EP4577367A1 - Device for coating a carrier substrate with a powdery material - Google Patents

Abstract

The invention relates to a device (100; 100*) for coating a carrier substrate (006) with a powdery material (004), having at least one first applicator (101; 101'), which comprises a first roller (102; 102') and a second roller (103; 103'), which form a first roller gap (104; 104') in the nip between their lateral surfaces, which first roller gap serves to form the film and through which powdery material (004) can be conveyed in order to form a first dry film (003) in the process, and having a roller (103'; 106) acting as a counter-pressure roller (103'; 106), which forms a second roller gap (107) with the second roller (103) or a further roller directly or indirectly downstream of the second roller (103) as viewed in the direction of material flow, wherein a substrate path leading through the second roller gap (107) is provided, on which a carrier substrate web (106) to be coated can be guided during operation and can be acted upon on a first side by the dry film (106) formed in the first roller gap (104). According to the invention, at least one traction device (141; 165) with a drive means (132; 133) is provided on each side of the frame for adjusting the roller gap (104; 107) between two neighbouring rollers (102; 103; 102'; 103') arranged to move relative to one another, by means of which the two rollers (102; 103; 102'; 103') can be clamped or moved towards one another in the adjusting direction and can be moved away from one another again or at least released again.

Description

Description

Device for coating a carrier substrate with a powdery material

The invention relates to a device for coating, in particular dry coating, a carrier substrate with a powdery material according to claim 1.

In WO 2020/150254 A1, a film is produced by calendering a powder mixture and wound onto a roll in order to be fed as such into a further process in which it can be laminated onto a collector. In one embodiment, the powder mixture is placed on a belt and guided into the nip of two rollers.

KR 102359521 B1 discloses a device for dry coating a current collector web with an active material layer, wherein a first and a second roller are provided on each side of the web, between which an active material layer is formed, and wherein the respective active material layer is applied to the current collector web in a nip between the two second rollers. A first and a second device for adjusting the roller spacing are provided, by means of which the distances between the first and second rollers can be adjusted. The first and second devices comprise a mechanical cylinder driven by a servo motor. Furthermore, a third device is provided for adjusting the roller gap formed between the second rollers. This allows the thickness of the electrode to be easily controlled via the gap width. In one embodiment, an air cylinder can also be provided between the second rollers, by means of which the distance is kept constant.

DE 102008 009 341 A1 concerns a grinding, mixing, dispersing, homogenizing or the like of liquid to pasty masses in a roller train with several rollers, each mounted on both front sides in bearing holders, whereby the mass is conveyed successively from a first roller to a last, a removal roller, and is removed there and there by a scraper. Two outer rollers of three rollers can be changed in their distance or their position to a middle roller by pivoting the bearing holders. The front-side bearing holders of at least one of the rollers are designed to be adjustable independently of one another transversely to the roller axis by respective eccentric bearings in such a way that a position offset from the other roller can be set by opposing deflection of the eccentrics.

The invention is based on the object of creating a device for coating, in particular dry coating, a carrier substrate with a powdery material.

The object is achieved according to the invention by the features of claim 1.

The advantages that can be achieved with the invention consist in particular in the fact that the device can reliably produce a coated carrier substrate with an active material layer that is as uniform and/or defined as possible.

In an embodiment of such a device for coating, in particular dry coating, a carrier substrate with a powdery material that is particularly suitable for the invention, it has at least one first application unit that comprises a first roller and a second roller that form a first gap in the nip between their lateral surfaces that serves to form a film, through which powdery material can be conveyed in order to form a first dry film, and a roller that acts as a counter-pressure roller that forms a second gap with the second roller or with a further roller of the first application unit that follows directly or indirectly downstream of the second roller, viewed in the direction of the material flow. through which a carrier substrate to be coated can be guided and exposed to the dry film formed in the first gap and transported in particular via the second roller and optionally the further roller to the second gap.

According to the invention, at least one pulling device with a drive means is provided on each side of the frame for setting the roller gap between two adjacent rollers arranged so as to be movable relative to one another, by means of which the two rollers can be moved or tensioned towards one another in the setting direction and can be moved away from one another again or at least relaxed again.

Preferably, the adjusting device comprising the drive means acts with its two acting ends on the first and the second roller in such a way that, in order to adjust the gap between the first and the second roller, it applies an adjusting force directed towards one another.

In a preferred embodiment, a cylinder-piston system that can be pressurized with pressurized fluid is provided as the drive means. In an advantageous embodiment, this is supplied or can be supplied with pressurized fluid via an actuating means fluidically connected to the cylinder-piston system from a pressurized fluid source connected to the actuating means on the input side, which provides and/or can provide pressurized fluid with a pressure of at least 100 bar or 10 MPa.

In an advantageous embodiment, means for emergency shutdown are provided, by which a depressurization of the pressure medium supply of the cylinder-piston system or a switchover to an operating mode causing shutdown is or can be effected.

Preferably, the first gap between the first and second roller is defined by the

Position-based adjustment device, i.e. based on a constant and/or defined gap width adjustable.

In an advantageous further development, the rollers forming the respective or relevant gap between them are each mounted on both sides in frame walls of mutually different sub-frames, wherein the adjusting devices each act on the frame walls of the two rollers forming the relevant gap between them.

In an advantageous embodiment, the roller acting as a counter-pressure roller is simultaneously designed as a laminating roller part of a second application unit located on the other side of the substrate path, which comprises a first roller of the second application unit, which forms a first roller gap of the second application unit with the laminating roller acting as a counter-pressure roller or with another roller of the second application unit located therebetween, through which powdery material can be conveyed in order to form a second dry film, which can be applied in the second roller gap via the laminating roller of the second application unit to the second side of the carrier substrate guided during operation via the transport path through the second gap.

Further advantageous embodiments and developments can be found individually or in combination in the claims and the following description.

Embodiments of the invention are illustrated in the drawings and are described in more detail below.

Show it:

Fig. 1 is a schematic representation of a product to be manufactured; Fig. 2 is a schematic diagram for the production and application of a dry film;

Fig. 3 shows an embodiment of a machine for producing a multi-layer product with a dry film applied to a carrier substrate with an application stage according to an embodiment of a first group of embodiments;

Fig. 4 is an enlarged view of the application stage of the first embodiment from Fig. 3;

Fig. 5 shows an alternative embodiment of an embodiment of the first group of embodiments;

Fig. 6 shows a further alternative embodiment of the embodiment of a first group of embodiments;

Fig. 7 shows a further alternative embodiment of the embodiment of a first group of embodiments;

Fig. 8 is a schematic diagram of an embodiment of a second group of embodiments;

Fig. 9 is a schematic diagram of a further embodiment of a second group of embodiments;

Fig. 10 shows an embodiment of a machine for producing a multilayer product with a dry film applied to a carrier substrate with an application stage according to an embodiment of the second group of embodiments; Fig. 11 is an enlarged view of the application stage from Fig. 10 with pairwise coupling of two rollers in a first embodiment;

Fig. 12 is an enlarged view of the application stage of Fig. 10 with pairwise coupling of two rollers in a second embodiment;

Fig. 13 a view from below with removal devices;

Fig. 14 is an oblique view of a product section with a slight lateral primer overhang;

Fig. 15 shows a further embodiment of a machine for producing a multi-layer product with a dry film applied to a carrier substrate with an application stage according to an embodiment of the second group of embodiments;

Fig. 16 shows a further embodiment of a machine for producing a multi-layer product with a dry film applied to a carrier substrate with an application stage according to an embodiment of the second group of embodiments;

Fig. 17 shows a further embodiment of a machine for producing a multi-layer product with a dry film applied to a carrier substrate with an application stage according to an embodiment of the second group of embodiments;

Fig. 18 is a perspective view of an embodiment of an applicator, in particular a double applicator, with a multi-part frame; Fig. 19 is a sectional view of an embodiment of an applicator according to Fig. 18, in particular a double applicator, with a multi-part frame;

Fig. 20 is a sectional view through a partial frame of a multi-part frame;

Fig. 21 is a schematic sectional view through a storage area of a sub-frame;

Fig. 22 is a sectional view through a partial frame with stop means for limiting the adjustment movement;

Fig. 23 a schematic diagram of two rollers with rotation axes inclined to each other;

Fig. 24 is a front view of a partial frame with a pivoting bearing;

Fig. 25 is a sectional view of an alternative embodiment of an applicator, in particular a double applicator, with a multi-part frame;

Fig. 26 is a schematic representation of an embodiment of a control circuit regulating the gap width of the film formation gap with an actuator formed by a multi-way valve a) in side view and b) in plan view of a part of the application unit;

Fig. 27 is a schematic representation of a multi-way valve;

Fig. 28 is a schematic representation of an embodiment of a control circuit regulating the gap width of the film forming gap with an actuating means formed by a pump a) in side view and b) in plan view of a part of the commissioned work;

Fig. 29 is a schematic representation of an applicator with a control circuit for controlling the gap width;

Fig. 30 is a schematic representation of an applicator with a control loop for control based on the layer thickness;

Fig. 31 is a schematic representation of an applicator with an alternative control loop for control based on the layer thickness;

Fig. 32 is a schematic representation of an applicator with a further alternative control circuit for control based on the layer thickness;

Fig. 33 is a schematic representation of an applicator with a control circuit for control based on the basis of the basis weight;

Fig. 34 is a schematic representation of an applicator with an alternative control circuit for control based on the basis of the basis weight.

The devices and machines described below are used to manufacture electrode units 001 of electrochemical storage devices, such as those used in particular in batteries or accumulators, such as lithium-sulfur, sodium-ion or in particular lithium-ion batteries, as well as in solid-state batteries.

A product 001; 002 to be manufactured by a machine mentioned below can, for example, be formed by an intermediate product 002 that is still to be cut, e.g. in web form, e.g. a product strand 002 designed as an electrode strand 002, or by arc-shaped end products 001 already cut in the machine, e.g. as electrode units 001, or electrodes 001 for short. product sections 001 formed.

To produce such products 001; 002 with a material layer 003; 003', in particular an active material layer 003; 003', applied to one or both sides of a carrier substrate 006, preferably a carrier substrate web 006, e.g. a current collector substrate 006 formed by, for example, a current collector foil 006, a device 100; 100* for coating, in short coating device 100; 100*, in particular for dry coating, of a carrier substrate 006, in particular in web form, e.g. the above-mentioned carrier substrate 006, with an above-mentioned material layer 003; 003', preferably a dry film 003; 003', in particular a powder composite film 003, which comprises at least one first application unit 101, by means of which powdery, preferably dry, material 004; 004', in particular a preferably solvent-free and/or dry powder mixture 004; 004', can initially be processed into a dry film 003, in particular by pressing and/or using a pressing force, and subsequently this dry film 003; 003' can be applied to a first side of the carrier substrate 006, in particular by pressing and/or using a pressing force. A dry film 003; 003' to be applied should, for example, have a thickness of 20 pm to 240 pm, preferably 40 pm to 100 pm, after application and pressing.

An above-mentioned powder mixture 004; 004', in particular in the form of a dry powder, comprises - in particular for the production of electrode units 001 for lithium ion batteries or accumulators - for example more than ninety percent by weight of an active material such as one or more of the lithium compounds lithium iron phosphate, lithium manganese oxide, nickel-rich lithium nickel manganese cobalt oxide, lithium nickel cobalt aluminum oxide, lithium cobalt oxide, lithium manganese nickel oxide and/or lithium titanate, a few, e.g. three percent by weight of a conductive additive, e.g. graphite or so-called CNTs, ie multi-walled carbon nanotubes, and a few, e.g. two percent by weight of a plastic that acts as a binding agent in the subsequent powder composite, e.g. polytetrafluoroethylene (PTFE).

The carrier substrate 006 simultaneously represents, for example, the current-conducting layer of the electrode unit 001 and is formed, for example, by an electrically conductive material in the form of a foil, fleece or fabric, e.g. a metal. It is formed, for example - in particular for the production of electrode units 001 for lithium-ion batteries or accumulators - from aluminum or copper and/or has, for example, a thickness d006 of 5 to 16 pm. In the case of the production of an anode, it is made in particular of copper with, for example, a thickness d006 of, for example, in the range of 5 to 13 pm and in the case of the production of a cathode, in particular of aluminum with, for example, a thickness d006 in the range of 7 to 16 pm.

In a preferred embodiment, the carrier substrate 006 has, at least in the surface area to be coated with the dry film 003; 003', a surface coating with a bond-supporting or bond-inducing agent 007; 007', e.g. a binder 007; 007', a primer 007; 007' or an adhesive 007; 007'. Such an agent 007; 007' can be formed by a thermoplastic or reactive binder or primer and can, for example, comprise a thermoplastic component and/or have a thickness d007 of only a few pm, e.g. at most 5 pm, in particular at most 3 pm.

A thickness d003; d003' of the active material layer 003; 003' of the product 001; 002, ie of the electrode unit 001 or of the electrode strand 002, is for example at most 240 pm, in particular at most 150 pm, preferably at most 100 pm and/or is for example at least 20 pm, in particular at least 30 pm, preferably at least 40 pm. The total thickness of the product 001; 002, for example coated on both sides, is - if necessary after passing through a calendering process following the application or coating of the carrier substrate 006 with the dry film 003, 003' inline or in a further machine - e.g. up to 500 pm, in particular up to 320 pm, preferably up to 220 pm and/or at least 50 pm, in particular at least 70 pm, preferably at least 90 pm. The density of the applied material 004, 004 is e.g. greater than 3000 kg/m ³ , preferably at least 3500 kg/m ³ . An intermediate product 002 which leaves the machine for pure coating, i.e. without subsequent calendering, and which is also referred to here as a preliminary product, can if necessary have a lower density, but e.g. B. of at least 2000 kg/m ³ , preferably of at least 2500 kg/m ² , in particular of at least 2900 kg/m ³ . In the case of coating on only one side, the total thickness of the finished product 001; 002, optionally further compacted by at least one calendering process, amounts to e.g. up to 255 pm, in particular up to 165 pm, preferably up to 65 pm and/or at least 30 pm, in particular at least 40 pm, preferably at least 50 pm.

If sufficient forces are available during the coating process or at the same time as the dry film 003, 003' is applied, or if such forces can be applied in the laminating gap, the above-mentioned values for the total thickness and/or density of the end product 001 or of the intermediate product 002, which only needs to be cut crosswise, can be represented without subsequent calendering after the coating process.

In order to ensure an effective manufacturing process, preferably web-shaped carrier material 006 is processed into an above-mentioned end or intermediate product, which has, for example, a width b006 of at least 300 mm, advantageously at least 500 mm, in particular at least 550 mm, or even 600 mm and more, in an advantageous embodiment even up to 1,200 mm. The carrier material 006 is not, for example, on the The entire width of the substrate is not coated with the dry film 003; 003', but only up to a free edge area in which the surface of the metallically conductive carrier material 006 remains free and accessible - e.g. for connecting cables. Such a width b003 of the coating amounts to at least 200 mm, advantageously at least 230 mm, or even 300 mm and more.

For the above-mentioned production of a dry film 003, a first roller 102, in particular a metering roller 102, and a second roller 103, in particular a laminating roller 103 of the first application unit 101 are provided in such a way that they form a first gap 104, in particular a first film-forming gap 104, in the nip between their outer surfaces, through which the powder mixture 004, for example fed into the nip by a device for feeding powdery material 700, in short powder feed device 700, can be fed to form the dry film 003 (see e.g. Fig. 2). A clear width of the first gap 104 at its narrowest point determines the - possibly compared to the thickness in the later product 001; 002 even greater - thickness of the dry film 003 even before its passage through an application point at which it is applied - in particular under pressure - to the carrier substrate 006.

The application point is preferably formed here directly by a nip of the second roller 103, which in this case acts as a laminating roller 103, with a roller 106; 103 acting as a counter-pressure roller 106; 103', or by a roller which interacts directly with the second roller or indirectly via one or more further rollers and acts as a laminating roller with a roller 106; 103 acting as a counter-pressure roller 106; 103' (not shown here). The second or further roller acting as a laminating roller 003 and the roller 106; 103 acting as a counter-pressure roller 106; 103 form a second gap 107, in particular an application gap 107, hereinafter referred to as "application gap" between their outer surfaces in the nip. B. also referred to as laminating gap 107, through which the carrier substrate 006 can be guided and, in particular on the side facing away from the counter-pressure roller 106; 103, with the film formed via the first film forming gap 104 formed, e.g. at least 40 pm thick, e.g. between 50 pm and 200 pm, in particular 60 to 120 pm thick dry film 003.

In a preferred embodiment, the application stage 100; 100* comprises a second application device 10T (see, for example, Fig. 3 to Fig. 13), by means of which a powder mixture 004', in particular solvent-free and/or dry, e.g. conveyed into the nip by a second device for supplying powdery material 700', in short powder supply device 700', can also be initially processed, in particular by pressing and/or using a pressing force, to form a second dry film 003'; 003 and then this second dry film 003'; 003 can be applied to the other, second side of the carrier substrate 006, in particular by pressing and/or using a pressing force. In principle, this can be the same powder mixture 004' or a different powder mixture 004' from the first powder mixture 004'.

Also in the second application unit 10T, a first roller 102', in particular metering roller 102', and a second roller 103', in particular laminating roller 103' are preferably provided such that they form a first gap 104', in particular second film-forming gap 104', in the nip between their outer surfaces, through which the powder mixture 004' can be conveyed to form the second dry film 003'.

Here too, the second roller 003' of the second applicator 10T can form a gap 107'; gap 107 with a roller 106'; 103 acting as a counter-pressure roller 106'; 103 in the nip between its outer surfaces, either directly or indirectly with the second roller 103' or via one or more other rollers and acting as a laminating roller (not shown here), through which the carrier substrate 006 can be guided and, in particular on the second side facing away from the second counter-pressure roller 106'; 103, can be subjected to the second dry film 003' formed via the second film-forming gap 104'; 104. In a first group of exemplary embodiments for the coating device 100 (see, for example, FIGS. 3 to 7), a second gap 107' is formed by a second application gap 107', e.g. a laminating gap 107', which is different from the first application or laminating gap 107', with a second roller 106', in particular a second counter-pressure roller 106' which acts as a counter-pressure roller 106 and is different from the first counter-pressure roller 106 and/or the laminating roller 103 of the first application unit 101, through which the carrier substrate 006 can be guided and, in particular on the second side facing away from the second counter-pressure roller 106', can be subjected to the second dry film 003' formed via the second film-forming gap 104'. In this embodiment, two independent application units 101; 10T for the two sides of the carrier substrate 106. It is therefore possible to set different conditions for the respective order independently of one another in the relevant laminating gap 107; 107'. For example, a different pressing or line force and/or temperature can be set.

For such an embodiment - e.g. with a view to a large wrap - in the respective application unit 101; 10T, the metering roller 102; 102', the laminating roller 103; 103' and the counter-pressure roller 106; 106' forming the laminating gap 107; 107' with the latter can be arranged relative to one another in a first embodiment such that the planes connecting the rotation axes R102; R103; R106; R102'; R103' of the respectively adjacent rollers 102; 103; 106; 102'; 103'; 106' intersect at an angle a which is, for example, between 40° and 130°, in particular between 70° and 110°, preferably between 80° and 100°. A large wrap can result in a better heat transfer from a counter-pressure roller 106; 106', which can be tempered if necessary, and/or an improved - e.g. flutter-free - running up and down (see e.g. Fig. 3 to Fig. 5).

For example, the respective counter-pressure roller 106; 106' can be arranged below the laminating roller 103; 103' in such a way that the plane connecting the rotation axes R103; R106; R103' of the two rollers 103; 103';106;106' is at most ± 30°, in particular, it deviates from the vertical by no more than ± 15°. The pressing force in the lamination gap and gravity act predominantly in the same direction.

In a second embodiment variant - advantageous, for example, with regard to the effective forces and load directions - the dosing roller 102; 102, the laminating roller 103; 103' and the counter-pressure roller 106; 106' which forms the laminating gap 107; 107' with the latter are arranged in relation to one another in the respective application unit 101; 101' in such a way that the planes connecting the rotation axes R102; R103; R106; R102'; R103' of the adjacent rollers 102; 103; 106; 102'; 103'; 106' intersect at most at an acute angle a, which is a maximum of 20°, in particular 0°, so that the rotation axes R102; R103; R106; R102'; R103' of the three rollers 102; 103; 106; 102'; 103'; 106' of the same application unit 101; 101' lie in the same plane. The arrangement is therefore very rigid, since the forces and counterforces are at least predominantly directed against one another. With such an arrangement of the three rollers 102; 103; 106; 102'; 103'; 106, e.g. also referred to as a "planar arrangement", the three rollers are arranged in a row one behind the other in such a way that their axes of rotation R102; R103; R106; R102'; R103' intersect at least one same straight line running perpendicular to the respective axes of rotation R102; R103; R106; R102'; R103'. They may be slightly inclined or tiltable towards each other, as explained below.

The two applicators 101; 10T with their laminating rollers 103; 103' are located on different sides of the substrate path and can be arranged one above the other in such a way that the two laminating gaps 107; 107' are located vertically directly above one another in one embodiment (see e.g. Fig. 6) or in another embodiment are offset horizontally, in particular by at least half and at most one and a half laminating roller diameters (see e.g. Fig. 7). In Fig. 7, for example, a substrate guide that can be transferred to other designs is indicated by a dashed line, through which a larger Wrap angle and thus a better heat transfer and/or a more stable run-up can be achieved. For this purpose, the substrate path is or will be deflected by an additional substrate guide element 121 such that the transport direction Ts when running onto the following roller 106; 106' runs at an incline of at least 45° to the transport direction Ts of the outgoing substrate 006.

In addition to the metering roller 102; 102', the second roller 103; 103' or a roller which interacts directly with the second roller or indirectly via one or more further rollers and acts as a laminating roller, in an advantageous development a further roller 118; 118' (see e.g. as an example for all versions of the first group in Fig. 5) can be provided which, in an operational, i.e. during production, circumferential section which guides the dry film 003; 003', between the metering gap 104; 104' and the laminating gap 107; 107' of the laminating roller 103; 103', in the manner of a calender roller 118; 118', is connected to a dry film 003; 003' which is fed or guided on the laminating roller 103; 103'. 003‘ is available.

For the above-mentioned designs, variants and forms, in a first configuration for the roller bearing, the laminating roller 103; 103' of the respective application unit 101; 10T with its axis of rotation R103; R103' can be operationally stationary, although its position can be adjusted if necessary, and the dosing roller 102; 102' and the counter-pressure roller 106; 106' can be mounted via respective actuators 109; 109';111; 11T so that they can each be adjusted in one direction with at least one movement component towards and/or away from the associated laminating roller 103; 103'. Here and in the following, the term actuator 109; 109';111;111' refers to the entirety of the direct or indirect positioning of a roller 102; 102';103;103';106;106' are to be understood as means which accomplish and/or enable the adjustment of the rollers 102; 102';103;103';106;106', which are also referred to below as adjustment means 109; 109';111; 11T and comprise at least one adjustment mechanism 112; 112';113;113' which guides the roller 102; 102';103;103';106;106' along an adjustment movement, as well as one or more drive means 132; 132';133;133'.

In a first embodiment, a position-based actuator 109; 109' or actuating means 109; 109' for position-based actuation is provided for the positioning of the respective dosing roller 102; 102' to the second roller 103; 103', i.e. an actuator 109; 109' or actuating means 109; 109', via which a defined position for the component to be positioned can be approached. A position-based actuator 109; 109' or position-based actuating means 109; 109' can be positioned, for example, with respect to a predetermined and/or defined position or can be operated or adjusted in a position-controlled or even position-regulated manner.

Such a position-based actuator 109; 109' can, for example, be realized in that a drive means 132; 133, e.g. a drive motor, can itself assume a defined and predeterminable position, as is possible for a position-adjustable servo drive or motor (see, for example, an embodiment of the drive means 132 set out below as a hydraulically operated cylinder-piston system 132 that can be controlled and/or regulated with respect to the piston position), or in that an adjustment path is limited at least towards the relevant side by stop means 119 that can be adjusted, e.g. via actuating and/or drive means 146, e.g. an adjustable stop 119, which defines the end position and against which the component to be adjusted with respect to the position can be pushed by means of a stopper, e.g. B. is set or can be set by a force-based or non-position-accurate drive means (see e.g. explanations for Fig. 19 or Fig. 22). The roller 102; 102' is mounted, for example, in or on an adjustment mechanism 112; 112';113;113', which is formed by a bearing mechanism 112; 112';113;113' that implements the adjustment path, e.g. with precise positioning. Such a mechanism is provided - particularly for small adjustment paths with large forces - e.g. advantageously by a bearing 113; 113' comprising an eccentric, e.g. a three-ring bearing 113; 113'. With regard to e.g. a position parallel to the adjustment direction and therefore more direct with regard to the adjustment path, a linear bearing 112; 112' running in the adjustment direction can also be advantageous instead. In this first, advantageous embodiment, a force-based actuator 111; 111 or actuating means 111; 111' for force-based actuation is provided for the actuation of the respective counter-pressure roller 103';106;106', i.e. an actuator 111; 111' or actuating means 111, via which actuation with a defined force to the abutment can be achieved. A force-based actuator 111; 111' or force-based actuating means 111; 111' is or are, for example, adjustable with respect to a predetermined and/or defined force or can be operated in a force-controlled or even force-regulated manner.

Such a force-based actuator 111; 111' - in particular provided at least on one side - can be realized, for example, in that a drive means 132, e.g. a drive motor 132, can itself apply a defined and predeterminable force, as is possible, for example, for a torque-adjustable or controllable, in particular torque-adjustable or controllable servo drive or motor, or in that the roller to be adjusted can be adjusted with an adjusting force to the relevant side by a drive means actuated by means of a pressure medium, e.g. by a pneumatically or hydraulically actuated cylinder-piston system 132; 133 against the other roller 103; 103', wherein the pressure of the drive means 132; 133 is preferably adjustable. The counter-pressure roller 106; 106' is here, for example, in or on an adjusting mechanism 112; 112'; 113; 113', which is formed by a bearing mechanism 112; 112' that implements the actuating force in a force-based manner, i.e. without additional mechanical limitation of the actuating path. As such, for example - at least on one side, but preferably on both sides - it can advantageously be formed by a bearing mechanism 112; 112' designed as a linear bearing 112; 112'.

In a second embodiment, however, the metering roller 102; 102' can be adjusted in a force-based manner and the counterpressure roller 106; 106 can be adjusted in a position-based manner. For this purpose, the above is to be transferred and applied in the respective correspondence. In a third embodiment, however, both rollers 102; 102';106; 106 can be adjusted based on force and in a fourth embodiment both rollers 102; 102';106; 106 can be adjusted based on position. For this purpose, the above is to be transferred and applied in the respective correspondence.

In a particularly advantageous fifth embodiment, a combined actuating mechanism 112; 113; 112'; 113' and/or a combined actuator 109; 109'; 111; 111' or combined actuating means 109; 109'; 111; 111' is provided for the actuation of at least the metering roller 102; 102' and/or at least for the actuation of the counter-pressure roller 106; 106', which optionally allows a position-based actuation of the respective roller 102; 102'; 106; 106' or a force-based actuation.

Such a combined actuator 109; 109'; 111 ; 111 ' is formed, for example, by an actuator 109, 111 ; 109', 11 T or actuating means 109, 111 ; 109', 11 T with an actuating mechanism 112; 112'; 113; 113', in whose actuating path a stop 119, which can be positioned, for example, via the drive and/or actuating means, can be optionally introduced to limit the position. Alternatively, an actuator 109, 111; 109', 111' can also be advantageous which, as the drive means 132, 133; 132', 133', has a motor 132; 132'; 133; that can be operated in a position-controlled or torque-controlled or torque-controlled manner. 133‘, in particular servo motor.

In a second configuration for the roller bearing, the counter-pressure roller 106; 106' of the respective application unit 101; 10T with its rotation axis R106; R106' can be operationally stationary, although adjustable if necessary, and the laminating rollers 103; 103' with each associated metering roller 102; 102' via respective common bearing mechanisms 112; 112' and/or actuators 111; 111' in pairs in one direction with at least one movement component towards and/or away from the associated counter-pressure roller 106; 106', and in addition to this the respective metering rollers 102; 102' via bearing mechanisms 112; 112';113;113' and/or actuators 109; 109';111; 11 T in one direction with at least one movement component can be mounted so that it can be adjusted towards and/or away from the respectively associated laminating roller 103; 103'.

In a first, advantageous embodiment, a position-based actuator 109; 109' in the above sense can be provided for setting the respective metering roller 102; 102', e.g. a bearing mechanism 112; 112'; 113; 113' formed on one or both sides by a three-ring bearing 113; 113' or by a linear bearing 112; 112'; 113; 113'. A force-based actuator 111; 111 can be provided in the above sense for setting the laminating rollers 103; 103' in pairs, each with an associated metering roller 102; 102'.

In a second embodiment, however, the metering roller 102; 102' can be adjusted in a force-based manner and the roller pair 103, 102; 103', 102 can be adjusted in a position-based manner. For this purpose, the above is to be transferred and applied in the respective correspondence.

In a third embodiment, however, the metering roller 102; 102' and the roller pair 103, 102; 103', 102 can be adjusted based on force and in a fourth embodiment the metering roller 102; 102' and the roller pair 103, 102; 103', 102 can be adjusted based on position. For this purpose, the above is to be transferred and applied in the respective correspondence.

In a particularly advantageous fifth embodiment, for the adjustment of at least the metering roller 102; 102' and/or at least for the adjustment of the roller pair 103, 102;

103', 102 in the above sense and/or in the above embodiment, a combined adjustment mechanism 112; 113; 112, 113 is provided, which allows optionally a position-based or force-based adjustment of the pair towards the counter-pressure roller 106; 106'; 103'; 103.

In a second group of embodiments for the coating device

100* (see e.g. shown in Fig. 8 to Fig. 12, Fig. 15 to Fig. 19, Fig. 25, Fig. 26 and Fig. 28) the second roller 003' of the second application unit 10T or a roller of the second application unit 101' which interacts directly with the second roller 103' or indirectly via one or more further rollers, together with the second or further roller 103 of the first application unit 101 acting as a laminating roller 103, form a common gap 107 acting as a two-sided laminating gap 107 in a nip between their lateral surfaces, the two laminating rollers 103; 103' forming the gap 107 between them acting as mutual counter-pressure rollers 103'; 103. The carrier substrate 006 can be guided through between the latter and, in particular on both sides, can be subjected to the dry films 003', 003' formed via the first and second film-forming gaps 104; 104'. Such an arrangement of two application units 101; 10T working together for simultaneous application on both sides is also referred to below as a double application unit 101; 10T.

In this case, the planes formed in the respective application unit 101; 10T by the rotation axes R102; R103; R102'; R103' of the metering roller 102; 102' and the laminating roller 103; 103' intersect, for example, at most at an acute angle a, which is, for example, a maximum of 20°, advantageously a maximum of 5°, in particular 0°, so that in the latter case the rotation axes R102; R103; R106; R102'; R103' of the rollers 102; 103; 106; 102'; 103'; 106' of the two application units 101; 10T interacting in a two-sided laminating gap 107 lie in the same plane or run parallel but vertically offset from one another.

In a first embodiment, the two planes run in a common horizontal plane or horizontally but vertically offset from each other (see e.g. Fig. 8).

In a second variant, which is advantageous, for example, with regard to a small wrap, the two planes run in a common plane inclined to the horizontal or in two planes inclined to the horizontal but vertically offset planes. The common plane or the two offset planes are inclined, for example, to the horizontal by an acute angle ß of 2° to 15°, in particular 3° to 10° (see, for example, Fig. 9). In such an arrangement of all, in particular all four rollers 102; 103; 106; 102';103' of a double application unit 101; 101' in one plane, e.g. also referred to as a "planar arrangement", the rollers 102; 103; 106; 102';103' are arranged one behind the other in a row such that their axes of rotation R102; R103; R106; R102' intersect at least one same straight line running perpendicular to the respective axes of rotation R102; R103; R106; R102'. They may be slightly inclined or tiltable towards each other, as explained below.

In addition to the respective metering roller 102; 102' and the second roller 103; 103', in an advantageous further development, a further roller 118; 118' in the above-mentioned type of calender roller 118; 118' can also be provided here (see, for example, the dashed lines in Fig. 8 and Fig. 9 as an example for all versions of the second group).

For the above-mentioned design variants and forms, in a first configuration for the roller bearing, a first of the two laminating rollers 103 or a further roller of a first of the two application units 101 acting as a laminating roller can be mounted with its rotation axis R103 in an operationally stationary manner, although possibly adjustable, while the second of the laminating rollers 103' or a further roller acting as a second laminating roller can be connected to the associated metering roller 102; 102' via a common bearing mechanism 112; 112' and/or a common actuator 109; 109';111; 11T in pairs in one direction with at least one movement component towards and/or away from the associated counter-pressure roller 106; 106', and in addition to this, the respective metering rollers 102; 102' can be connected via bearing mechanisms 112; 112';113;113' and/or actuators 109; 109';111; 11 T are mounted in a direction with at least one movement component towards and/or away from the respective associated laminating roller 103; 103' or further roller. In the case of one or several further rollers between the metering roller 102; 102' and the roller acting as a laminating roller, for example, can also be adjusted jointly in one direction with at least one movement component towards and/or away from the associated counter-pressure roller 106; 106' via the common bearing mechanism 112; 112' and/or the common actuator 109; 109';111;111'.

In a first, advantageous embodiment, a position-based actuator 109; 109' is provided in the above sense and/or in an above-mentioned embodiment for setting the respective dosing roller 102; 102'. For setting the second laminating roller 103' in pairs with associated dosing roller 102', a force-based actuator 111; 111 can be provided for force-based setting in the above sense and/or in an above-mentioned embodiment.

In a second embodiment, however, the metering roller 102; 102' can be adjusted in a force-based manner and the roller pair 103, 102; 103', 102 can be adjusted in a position-based manner. The above is also to be transferred and applied in the respective correspondence.

In a third embodiment, however, both rollers 102; 102'; 106; 106 can be adjusted based on force and in a fourth embodiment both rollers 102; 102'; 106; 106 can be adjusted based on position. For this purpose, the above is to be transferred and applied in the respective correspondence.

In an advantageous fifth embodiment, a combined actuating mechanism 112; 113; 112';113' is provided for the actuation of at least the metering roller 102; 102' and/or at least for the actuation of the roller pair 103, 102; 103', 102 in the above sense and/or in the above embodiment, which optionally allows a position-based actuation of the pair against the laminating roller 103'; 103 acting as counter-pressure roller 103'; 103 via a position-based actuator 109; 109' and a force-based actuation via a force-based actuator 111; 111'. In an advantageous sixth embodiment, described in more detail below in connection with Fig. 18 and Fig. 19 or Fig. 25 to Fig. 28, a position-based actuator 109; 109' in the above sense and/or in an above-mentioned embodiment is provided for setting the first gap 104; 104' or the respective dosing roller 102; 102', and a force-based actuator 111; 111 for force-based setting in the above sense is provided for setting the second gap 107 or setting the counter-pressure roller 103', wherein the two dosing rollers 102; 102' and the counter-pressure roller 103; 103' to be set can each be adjusted individually, ie without being coupled in pairs. In a particularly advantageous development of this embodiment, a position-based actuator 109; 109' is provided for setting at least the dosing roller 102; 102' and/or for setting the second gap 107 or setting the counter-pressure roller 103', a combined adjusting mechanism 112; 113; 112';113' in the above sense and/or in the above embodiment is provided.

For all versions of the two groups of embodiments with jointly adjustable rollers 103'; 102'; 103; 102, these can be mounted on both sides in supports 122'; 122, in particular in side parts of a base frame, which in turn are mounted in a frame that accommodates the application units 101; 10T via bearing mechanisms 112'; 112; 113'; 113 formed by linear bearings 112'; 112; 113'; 113.

Alternatively, the two jointly adjustable rollers 102; 103; 102'; 103' can be mounted on both sides in supports, in particular in side parts of a base frame, which in turn are mounted so as to be pivotable about a pivot axis parallel to the rotation axis of the first, stationary laminating roller 103; 103' (see e.g. Fig. 12).

As already mentioned, in a respective application unit 101; 10T between the second roller 103; 103' and the nip point to the counter-pressure roller 106; 103' at least one further roller acting as a laminating roller and connected to the counter-pressure roller 106; 103' can be arranged. A roller forming the laminating gap 107; 107' may be provided.

For all versions of the two groups of embodiments, in a particularly advantageous development, a removal device 114; 114', in particular a cleaning doctor blade 114; 114', is provided in the respective application unit 101; 101', which is surrounded by, for example, a material removal device 127; 127' and can be optionally placed on and off the outer surface of the first roller 102; 102' for cleaning purposes. This extends, for example, at least over the width of the roller outer surface effective for film formation.

Instead of this, or advantageously in addition to this, the material removal 127; 127' in the respective application unit 101; 101' comprises, viewed axially parallel to the second roller 103; 103' and spaced apart from one another, two removal devices 116; 116', in particular side edge doctor blades 116; 116', which can be adjusted axially parallel and positioned or positioned against the second roller 103; 103', by means of which a dry film 003; 003' conveyed over the second roller 103; 103' can be removed in the region of its side edges and, for example, deposited in a collecting device 117; 117'. This removal serves, for example, as so-called edge trimming to obtain a straight edge and/or a desired width b003; b003' of the dry film 003; 003. The collected quantity can, for example, be returned to the supply of the powder mixture 004; 004'. Such a removal device 116; 116' can also be used to remove an edge strip 008; 008', which can be used, for example, to determine the density of the material layer 003; 003'.

For cleaning purposes, a removal device 129; 129', in particular a cleaning blade 129; 129', which can be placed on and off the outer surface of the second roller 103; 103', can also be advantageously provided, which extends, for example, at least over the width of the roller outer surface effective for film formation, and optionally a suction or collecting device (not shown). For the supply or introduction of the powder mixture 004; 004' into the first gap 004; 004, an above-mentioned powder supply device 700; 700' for supplying a powdery material is provided, wherein in the region of the gusset above the gap 104; 104', i.e. in the space formed above the gap 104; 104' between the lateral surfaces of the two rollers 102; 103; 102';103', which in profile is in particular wedge-like or triangular, preferably a filling and/or supply space 126 with a width extending in the axial direction of the second roller 103; 103' is formed and/or provided.

In a particularly advantageous embodiment, in the application unit 101; 101' above the first gap 104; 104' there are provided two boundaries 124, in particular side plates 124, which are spaced apart from one another axially parallel to the first roller 102; 102' and can be adjusted, for example, in the axially parallel direction, which each seal off an area of the upper gusset formed between the jacket surfaces of the first and second rollers 102; 103; 102'; 103' towards both end faces of the application unit 101; 101' and in this way form an intermediate filling and/or storage space 126, preferably variable in width, for receiving the powder mixture 004; 004'. Depending on the desired width and/or position of the dry film 003; 003', the filling and/or storage space 126 can thereby be varied or variable on at least one, preferably on both sides in the position of its lateral boundary 124. As an alternative to a filling and/or storage space 126 directly delimited in the lower area by the lateral surfaces, a filling and/or storage space 126 in the form of a filling or storage funnel, e.g. comparable to an insertion aid mentioned below, could also be provided directly in or above the gusset - at least where not contradictory to other design features of the application unit 101; 10T or the powder feed 700; 700'.

For all above mentioned versions, variants, configurations, embodiments or

The bearing mechanism 112; 112';113;113' and/or the actuator 109; 109';111; 111 ' of the first roller 102; 102 is preferably designed such that a gap width b104 for the first gap 104; 104' is operationally adjustable to a variable clear width at the narrowest point of at least 15 pm, advantageously of at least 30 pm, in particular of at least 50 pm, and/or that the gap width b104 of the first gap 104; 104' is adjustable at least via the above-mentioned position-based drive means 132;

132' and/or via at least one-sided stop means 119 which limit an adjustment position in the direction of the nip point and whose position can be adjusted, i.e. for example an above-mentioned, in particular adjustable or positionable stop 119.

Alternatively or additionally, the bearing mechanism 112; 112'; 113; 113' and/or the actuator 109; 109'; 111; 111' are advantageously designed to set and/or apply a line force of, for example, at least 500 N/mm, advantageously at least 700 N/mm, preferably a line force of between 500 N/mm and 3000 N/mm, in the first gap 104; 104', at least in the region of its width contributing to film formation, between the rollers 102; 102'; 103; 103' forming the first gap 104; 104'.

As mentioned above, a combined actuating mechanism 112; 113; 112'; 113' can be provided for positioning the metering roller 102; 102' to the second roller 103; 103' - e.g. in an above embodiment and/or in the above sense - which optionally allows - e.g. in one operating mode - a position-based actuating mechanism via a position-based actuator 109; 109' and - e.g. in a second operating mode - a force-based actuating mechanism via a force-based actuator 111; 111'.

For all the above-mentioned designs, variants, configurations, embodiments or designs and, for example, independently of the above-mentioned implementation of the coating device 100; 100* with individual application units 101; 101' with respective counter-pressure rollers 106; 106 or with combined application units 101; 101' with mutually effective counter-pressure rollers 103'; 103, in a particularly advantageous Design of the dosing gap 104; 104' between the first and second rollers 102; 102';103;103' on the basis of a position-based actuator 109; 109' that is positionable in relation to a predetermined position or is position-controlled or position-regulated, e.g. positionable with respect to the gap width b104, controllable via e.g. a control chain Sb; Sd; S"d; SF or controllable via e.g. a control loop Rb; Rd; R"d; RF, i.e. adjustable, e.g. positionable, controllable or regulateable, to a constant and/or defined gap width b104; b104', wherein the position-based setting is based on a defined and constant relative position or gap width 104 of the two rollers 102; 103; 102';103' is directed in its working position, and/or the laminating gap 107; 107' between the second roller 103; 103' and the counter-pressure roller 106; 106';103'; 103 is adjustable in the above sense on the basis of a force-based, e.g. force-controlled or force-regulated, actuator 111; 111 ', e.g. with regard to the actuating force via, for example, a pressure regulating valve or, for example, a control path comprising such a pressure regulating valve, or, for example, controllable via, for example, a control path comprising such a pressure regulating valve, i.e. can be set, e.g. controllable or regulateable, to a constant and/or defined actuating or line force, wherein the force-based actuating is in particular based on a defined and/or constant actuating or line force between the two at the second gap 107; 107' involved rollers 106; 106';103'; 103 in their working position. Just to clarify, it should be noted that the line or positioning force effective between the two rollers 106; 106';103'; 103 involved in the second gap 107; 107' does not act directly, but rather via the material guided through the gap, in the case of the film formation gap 104; 104' e.g. via the powdery material 004; 004' and in the case of the laminating gap 107; 107' via the product strand 002 having the dry film 007 on one or both sides.

Without limiting the above-mentioned specific embodiments, in principle any of the two rollers involved in the respective gap 104; 104';107;107' 102; 102';103;103';106;106' can be adjusted by the corresponding actuator 109; 109';111;111' and/or mounted on corresponding adjusting mechanisms 112; 112';113;113' in the above sense. This also applies to designs in which one of the rollers 102; 102';103;103';106;106' involved in the relevant gap 104; 104';107;107' is mounted so as to be adjustable together with another roller 102; 102';103;103';106;106' not involved in this gap 104; 104';107;107'.

Likewise, for example, independently of the above implementation of the coating device 100; 100* with individual application units 101; 10T with respective counter-pressure rollers 106; 106 or with combined application units 101; 101 ' with mutually effective counter-pressure rollers 103'; 103, in an embodiment that is particularly advantageous with regard to optimal adjustability, the metering gap 104; 104' between the first and second rollers 102; 102';103;103' of the same application unit 101; 101 ' and/or the laminating gap 107; 107' between the second roller 103; 103' and the cooperating counter-pressure roller 106; 106; 103'; 103 - for example, not just position- or force-based, but - on the basis of a combined actuator 109; 109';111;111' optionally - in particular in the above sense - position-based adjustable, e.g. positionable with respect to the gap width b104, controllable via e.g. a control chain Sb; Sd; S"d; SF or controllable via e.g. a control loop Rb; Rd; R"d; RF, i.e. adjustable in e.g. one operating mode to a constant and/or defined relative position of the two rollers and/or a constant and/or defined gap width b104, e.g. positionable or controllable or controllable, or adjustable in e.g. another operating mode force-based, e.g. with respect to the actuating force via e.g. a pressure control valve or e.g. B. a control path comprising, for example, such a pressure control valve can be controlled or, for example, regulated via a control path comprising, for example, such a pressure control valve, designed, ie, in e.g. another operating mode, adjustable to a defined and/or constant setting or line force, e.g. controllable or adjustable. In particular, one of the rollers 102; 102';103;103';106;106' involved in the relevant gap 104; 104';107;107' can be adjusted either position-based or force-based in a combined adjusting mechanism 112; 113; 112; 113 mounted and/or the relevant gap 104; 104';107;107' can be optionally adjusted to a constant and/or defined gap width or to a constant and/or defined setting or line force in the above sense, in particular can be controlled or regulated in the above sense. Here too, without limiting the above-mentioned specific embodiments, any of the two rollers 102; 102';103;103';106;106' involved in the relevant gap 104; 104';107;107' can in principle be adjusted in this way by the corresponding combined actuator 109; 109';111;111' and/or can be mounted accordingly on corresponding combined adjusting mechanisms 112; 112';113;113' in the above sense. This also applies to designs in which one of the rollers 102; 102';103;103';106;106' involved in the respective gap 104; 104';107;107' is mounted in such a way that it can be adjusted together with another roller 102; 102';103;103';106;106' not involved in this gap 104; 104';107;107'.

In an advantageous embodiment, the combined actuator 109; 109'; 111; 11 T is formed by a force-based, in particular force-controllable or -regulatable, actuator 111; 11 T with an actuating mechanism 113; 113'; 112; 112', in whose actuating path a stop 119 can be optionally introduced to limit the position, for example via drive and/or actuating means 145; 146. A cylinder-piston system 133 that can be actuated with pressure medium, in particular hydraulically, is preferably provided as the drive means 133.

For positioning, the first roller 102; 102' can be mounted via a bearing mechanism 113; 113';112;112' and/or a position-based or force-based or optionally position- or force-based actuator 109; 109';111;111' in a direction with at least one movement component towards and/or away from the respectively associated second roller 103; 103'. In addition or instead, the counter-pressure roller 106; 106';103'; 103 can be mounted via a bearing mechanism 113; 113';112;112' and/or a position-based or force-based or optionally position- or force-based actuator 109; 109';111;111' in a direction with at least one movement component The movement component can be mounted so that it can be adjusted towards and/or away from the second or an intermediate further roller 103; 103'.

Alternatively, the first roller 103; 103' with the associated second roller 102; 102' can be mounted in pairs so as to be movable towards and/or away from the associated counter-pressure roller 106; 106' via a common bearing mechanism 112; 112'; 113; 113' and/or a common, e.g. position-based or force-based or optionally position- or force-based actuator 109; 109'; 111; 111', and in addition to this, the respective first roller 102; 102' can be mounted via a bearing mechanism 113; 113'; 112; 112' and/or a common, e.g. position-based or force-based or optionally position- or force-based actuator 109; 109'; 111; 111 ' is mounted in a direction with at least one movement component towards and/or away from the respectively associated second roller 103; 103'.

For all of the above-mentioned designs, variants, configurations, embodiments or embodiments, the first roller 102; 102' and the second roller 103; 103' forming the first gap 104; 104' with it are rotatably driven or driven mechanically independently of one another in opposite directions and at different circumferential speeds and/or by different drive means 148; 149, e.g. drive motors 148; 149, in particular at least speed-adjustable or controllable servo motors.

The first roller 102; 102' is operated at a lower speed, wherein the first roller 102; 102', in particular metering roller 102; 102', and the associated second roller 103; 103', in particular laminating roller 103; 103', are operable or operated, for example, in a ratio V102(102'): V103(103') of their peripheral speed of the first to the second roller 102, 102';103;103', which lies in a range between 1:5 and 3:5, in particular 1:4. The rollers 103; 106; 103; 103' forming the second gap 107; 107' together are preferably driven or can be driven mechanically independently of one another at the same peripheral speed by a common drive motor 148, in particular a servo motor, or preferably by different drive motors 148, in particular servo motors 148.

In an advantageous embodiment, the mechanically independent drive motors 148; 149 can be operated by a drive control via an electronic, in particular virtual, master axis.

Of particular advantage is a further development in which the first roller 102; 102' has, in the region of its outer surface contributing to film formation, a surface that is more material-repellent and/or has a less adhesively effective outer surface with regard to the powder mixture than the second roller 103; 103' in the region of its outer surface contributing to film formation.

At least the second roller 102; 102'; 103; 103' can have a polished and/or chrome-coated or ceramic-coated surface at least in the area of its outer surface that contributes to film formation. The first roller 102; 102' can have a structured or material-repellent surface at least in the area of its outer surface that contributes to film formation.

For all of the above-mentioned designs, variants, configurations, embodiments or embodiments, the first and/or second roller 102; 102'; 103; 103' can be tempered, in particular heated, preferably in such a way that its outer surface - e.g. at an ambient temperature of 25°C - can be heated to at least 80°C, advantageously to at least 100°C, preferably to at least 120°C.

Instead or preferably in addition to this, the counter-pressure roller 106; 106';103; 103 effective roller 106; 106' of the first group of embodiments can be tempered, in particular heated, preferably in such a way that its outer surface - e.g. at an ambient temperature of 25°C - can be heated to at least 80°C, advantageously to at least 100°C, preferably to at least 120°C.

The temperature control or heating can basically be carried out electrically, but in an advantageous embodiment it is realized by passing a temperature control or heating fluid through the roller 102; 102'; 103, 103'; 106; 106' to be temperature controlled. The temperature control fluid, e.g. appropriately tempered water, is fed to and removed from the roller 102; 102'; 103, 103'; 106; 106' to be temperature controlled via a temperature control fluid line 134 and e.g. a rotary union into the relevant roller 102; 102'; 103, 103'; 106; 106'.

For all of the above-mentioned designs, variants, configurations, embodiments or designs, the two application units 101; 10T, together with one or more substrate guide elements 121, possibly arranged directly in front of, after or in between, are mounted in a common or possibly multi-part frame 128, e.g. two front frame walls 131 of the same or possibly multi-part frame 128. In the case of a common frame 128 with one-piece frame walls 131, a particularly rigid arrangement of the application units 101; 10T can be provided in a laminating unit 100; 100* designed as an aggregate 100; 100*, e.g. a laminating aggregate 100; 100*.

In the event that a calendering unit 600; 600*, described below, also referred to as a calender 600; 600*, is provided in the substrate path - e.g. directly - downstream of the laminating unit 100; 100*, for example, the rollers 601; 60T; 602; 602* included in the calendering unit 600; 600* can, in an advantageous further development, also be arranged in this frame 603 or, in an advantageous variant, e.g. as a separate unit 600; 600*, e.g. calendering unit 600; 600*, in side walls of a separate frame 603 arranged directly on and/or above the frame 128 carrying the application units 101; 10T. be stored.

In an embodiment of the machine shown in Fig. 15 and Fig. 16, for example, which may be somewhat longer but in which the risk of vibration transmission between the units 100; 100*; 600; 600*, in particular at least the laminating unit 100; 100* and the calendering unit 600; 600*, is reduced, the laminating unit 100; 100* and the calendering unit 600 provided there are provided horizontally next to one another, preferably even in separate frames 128; 603, which are separated from one another, for example in terms of vibration. The calendering unit 600; 600* can also be omitted in a variant of Fig. 3, Fig. 10, Fig. 15 and/or Fig. 16 (not shown). An advantageous embodiment of such a machine without an additional calendering unit provided in the substrate path is e.g. B. shown in Fig. 17 and described in more detail below.

However, a calendering unit 600; 600* shown in Fig. 15 and Fig. 16, for example, or a calendering process downstream of the application of the dry film 003; 003* is not mandatory and can be omitted entirely in a different version of the machine for coating. In the latter case, calendering can then be omitted entirely or can be carried out or implemented in a separate process and/or a separate machine, e.g. a second machine. The second machine comprises, for example, a substrate unwinder on the input side, from which the web-shaped intermediate product 002 can be unwound and guided along a substrate path through at least one calendering unit 600 to a roll winder on the output side or via a cross-cutting device to a delivery.

Basically independent of, but advantageously in conjunction with one of the above-mentioned designs, variants, configurations, embodiments or configurations of the application units 101; 10T and/or coating devices 100; 100* and/or machine configurations, the frame 128 of the device for coating Device for coating 100; 100* in a particularly advantageous embodiment is designed in several parts (see e.g. Fig. 18, Fig. 19, Fig. 20, Fig. 21, Fig. 22, Fig. 24, Fig. 25, Fig. 26 and Fig. 28). In this case, at least two adjacent rollers 102; 102';103;103'; 106 of the application unit 101; 10T, in an advantageous embodiment at least the two rollers 103; 103'; 106 which form the laminating gap 107; 107' with one another and/or act as counter-pressure rollers 103; 103'; 106, are mounted on both sides in - in particular rigidly connected to one another - frame walls 131.1; 131.2; 131.3; 131.4 of two different sub-frames 128.1; 128.2; 128.3; 128.4, which can be changed in their relative position along an adjustment direction running perpendicular to the axis of rotation R102; R103; R102';R103';R106;R106' of at least one of the two adjacent rollers 102; 102';103;103'; 106 such that a distance between their jacket surfaces or axis of rotation R102; R103; R102';R103';R106;R106' and/or a distance between the jacket surfaces of two adjacent rollers 102; 102';103;103'; 106 - e.g. B. via a carrier substrate 006 that is loaded or coated on at least one side or via the powdered material 004; 004' - the effective adjusting force can be varied or adjusted. In a preferred variant, one of the two sub-frames 128.1; 128.2; 128.3; 128.4 can be arranged in a fixed location - e.g. on a base of the coating device 100; 100* or in or on a higher-level frame construction 145, e.g. a base plate 145, fixed to the frame - and the other of the at least two sub-frames 128.1; 128.2; 128.3; 128.4 via a bearing mechanism 112; 113 within at least one adjustment range along the relevant adjustment direction, and in another variant both one and the other of the adjacent sub-frames 128.1; 128.2; 128.3; 128.4 can be adjusted along the adjustment direction. The sub-frames 128.1; 128.2; 128.3; 128.4 each comprise in particular two frame walls 131.1; 131.2; 131.3; 131.4, which are rigidly, if possibly detachably, connected to one another via one or more cross connections, e.g. one or more cross members 136; 137. A sub-frame 128.1; 128.2; 128.3; 128.4 that can be adjusted in the above manner can thus be moved as a whole, together with the roller 102; 102';103;103'; 106 or rollers 102; 102';103;103'; 106 take place.

In an above-mentioned embodiment of an application unit 101 for only one-sided application, i.e. with a first roller 102, e.g. the metering roller 102, a second roller 103, e.g. the laminating roller 103, and a pure counter-pressure roller 106, in a first embodiment variant not shown, for example the first and second rollers 102; 103 can be mounted together in or on frame walls 131.1 of a first partial frame 128.1 and the counter-pressure roller 106 in or on frame walls 131.2 of a second partial frame 128.2. For this purpose, for example the first roller 102 in or on the first partial frame 128.1 is force-based via the above-mentioned adjusting means 109; 111, e.g. B. force-defined, force-controlled or force-regulated in the above sense, in its adjusting force and/or position-based, e.g. positionable in the above sense, position-controlled or position-regulated, adjustable in its distance from the second roller 103 (wherein the "and" variant in the and/or expression here stands for a combined actuator that can be adjusted either force- or position-based). In an alternative variant, e.g. the second roller 102; 103 and the counter-pressure roller 106 are mounted in or on frame walls 131.1 of a first sub-frame 128.1 and the first roller 102, e.g. dosing roller 102, on frame walls 131.3 of a separate sub-frame 128.3. For this purpose, for example the counter-pressure roller 106 is mounted in or on the first sub-frame 128.1 via the above-mentioned adjusting means 109; 111 force-based, e.g. force-defined, force-controlled or force-regulated and/or position-based, e.g. positionable, position-controlled or position-regulated, mounted so as to be adjustable at a distance from the second roller 103.

In a preferred variant of the above-mentioned design of an application unit 101 for only one-sided application, the first, the second and the counter-pressure roller 102; 103; 106 are mounted in or on frame walls 131.1; 131.2; 131.3 of a respective sub-frame 128.1; 128.2; 128.3. For example, one of the sub-frames 128.1; 128.2; 128.3, preferably the sub-frame 128.2 carrying the second roller 103, is arranged in a fixed space or frame and the other two sub-frames 128.1; 128.2; 128.3 are arranged relative to this mounted so as to be movable along the direction of adjustment. For example, in Fig. 18, for this embodiment, the right-hand sub-frame 128.4 with a frame wall 131.4 and the roller 102' can be omitted, with the roller 103' then being designed as a pure counter-pressure roller 106.

In a preferred embodiment of the application unit 101; 10T as a double application unit 101; 10T for simultaneous application on both sides, shown for example in Fig. 8 to 12 and Fig. 15, Fig. 16 and Fig. 17, in a first variant not shown, the two pairs of rollers consisting of the dosing and laminating rollers 102; 103; 102';103' can be mounted in pairs in a sub-frame 128.1; 128.2, the two sub-frames 128.1; 128.2 being positionally variable relative to one another in the above-mentioned manner such that a distance between the rotation axes R103; R103' of the two rollers 103; 102' forming the laminating gap 107 with one another is maintained. 103' and/or an adjusting force that is directly or indirectly effective between the casing surfaces can be varied. In this case, one of the sub-frames 128.1; 128.2 can be mounted in a spatially or frame-fixed manner and the other can be moved in the adjustment direction. The metering rollers 102; 102' are, for example, mounted in the respective sub-frame 128.1; 128.2 via the above-mentioned adjusting means 109; 111 in a force-based manner, e.g. force-defined, force-controlled or force-regulated and/or position-based manner, e.g. positionable, position-controlled or position-regulated, at a distance from the adjacent laminating roller 103. In an alternative variant, also not shown, this can adjust the laminating gap 107; 107' forming roller pairs 103, 103' in a first, common sub-frame 128.1 and the two metering rollers 102; 102' each in their own sub-frame 128.3; 128.4, wherein the first sub-frame 128.2 is e.g. spatially or frame-fixed and the other two sub-frames 128.3; 128.4 are movable relative to the first sub-frame 128.1 in such a way that a distance between the rotation axes R102; R103; R102';R103' between the first and second rollers 102; 103; 102';103' and/or an adjusting force acting directly or indirectly between the lateral surfaces can be varied in the above-mentioned manner. One of the laminating rollers 103; 103' via the above-mentioned actuating means 109; 111 force-based, e.g. force-defined, force-controlled or force-regulated, and/or position-based, e.g. positionable, position-controlled or position-regulated, adjustable at a distance from the other laminating roller 103.

However, in a preferred embodiment of the application unit 101; 10T as a double application unit 101; 10T for simultaneous application on both sides, all four or - in the case of, for example, further intermediate rollers, all - rollers 102; 103, 102'; 103' are mounted in frame walls 131.1; 131.2; 131.3; 131.4 of their own sub-frames 128.1; 128.2; 128.3; 128.4. For example, one of the sub-frames 128.1; 128.2; 128.3; 128.4, preferably a sub-frame 128.1 carrying a second or laminating roller 103, in particular the laminating roller 103 of the first applicator 101, is arranged in a fixed manner in the room or frame and the remaining sub-frames 128.2; 128.3; 128.4 are mounted so as to be adjustable along a direction preferably perpendicular to a rotation axis R103; 103' of a laminating roller 103; 103', in particular the laminating roller 103 mounted so as to be fixed in the room or frame, and/or in a straight line, in particular along a horizontally extending adjustment direction.

Preferably, at least the roller 103 of the first application unit 101 which is involved in the formation of the second gap 107; 107' and which follows upstream with respect to the material flow and/or is the first roller 102 of the first application unit 101 is mounted in or on a third sub-frame 128.3 which can be displaced along an adjustment direction which runs perpendicular to the rotation axis R102; R103; R102';R103';R106;R106' of at least the roller 103 of the first application unit 101 which is involved in the formation of the second gap 107. In the case of the double application unit 101; 10T, in an advantageous embodiment the roller 102 of the first application unit 101 which is involved in the formation of the second gap 107; 107' involved laminating roller 103' of the second application unit 10T following upstream with respect to the material flow, in particular the first roller 102 of the second application unit 10T is mounted in or on a fourth sub-frame 128.4 which is displaceable along an adjustment direction which runs perpendicular at least to the rotation axis R103 of the roller 103 mounted in or on the spatially or spatially most positioned sub-frame 128.1. For all of the above-mentioned designs with movable sub-frames 128.2; 128.3; 128.4, these are preferably movable on linear guides 112; 112', whereby separate guide sections 138, e.g. rail pieces 138, can be provided for each of the movable sub-frames 128.2; 128.3; 128.4, or continuous guides 138 or rails 138 for two or more displaceable adjacent sub-frames 128.2; 128.4. The sub-frames 128.2; 128.3; 128.4 can have support feet 139 on the base that correspond to the guide sections 138 or guides 138 and include, for example, sliding or rolling elements.

The rollers 102; 102'; 103; 103'; 106 can basically be mounted on a respective axis that is mounted in a rotationally fixed manner in the frame walls 131.1; 131.2; 131.3; 131.4 of the respective sub-frames 128.1; 128.2; 128.3; 128.4 via corresponding bearings 151 or advantageously - as can be seen in Figures 18 to 22 and 25, 26 and 28 - with front-side roller journals in bearings 151, in particular radial bearings 151, which in turn are arranged in or on the respective frame walls 131.1; 131.2; 131.3; 131.4.

In the preferred embodiment here, the sub-frames 128.1; 128.2; 128.3; 128.4, which are adjacent to one another and are arranged so as to be movable relative to one another, can be moved towards one another in the direction of adjustment, in particular tensioned, and can be moved away from one another again or at least relaxed again by at least one drive means 132; 132';133;133', in particular by at least one actuating device 141; 165 comprising a drive means 132; 132';133;133', and optionally by further means transmitting the actuating movement or force, per frame side, preferably by two or at least two actuating devices 141, in particular pulling devices 141, e.g. in the form of tensioning devices 141, per frame side. The traction devices 141 can be designed in such a way that they not only produce the above-mentioned traction force, but also, if necessary, an oppositely directed force and/or the partial frames 128.1; 128.2; 128.3; 128.4 moving away from each other. Force, e.g. a compressive force effective between the partial frames 128.1; 128.2; 128.3; 128.4, can be applied. The mutually facing sides of the adjacent partial frames 128.1; 128.2; 128.3; 128.4, which are arranged so as to be movable relative to one another, are designed to correspond to one another, for example, such that the adjacent rollers 102; 102';103;103'; 106 carried by the partial frames 128.1; 128.2; 128.3; 128.4 - e.g. with appropriately positioned stop means 119 - with their effective jacket surfaces in a relative position desired for operation with, if necessary, a desired gap width b104; b104' or a gap width b104; b104' that is set by the load. What has been explained here for the first gap 104; 104' is to be transferred accordingly to the setting of the second gap 107 or its gap width b107 in the case of a position-based adjustable second gap 107.

In an advantageous embodiment of such an applicator 101; 10T with a multi-part frame 128, at least one actuator 109; 109', which effects the setting, e.g. the variation of the position and/or the setting force between the first and second rollers 102; 103; 102'; 103' and comprises a drive means 132; 133, is designed to be position-based, e.g. positionable, position-controlled or position-regulated, or - in a particularly advantageous embodiment - can be operated optionally position-based, e.g. force-defined, force-controlled or force-regulated, or position-based, e.g. positionable, position-controlled or position-regulated.

In a first embodiment variant (see e.g. Fig. 18 to Fig. 22), for example, a drive means 133 which acts on the sub-frame 128.3; 128.4 carrying the first roller 102; 102' and on the sub-frame 128.1; 128.2 carrying the second roller 103; 103'; 106 and is operable or operated in a force-based manner, in particular a drive means 133 which can be operated or operated in a force-controlled or force-regulated manner, in particular a cylinder-piston system 133 which can be pressurized with pressurized fluid, in particular hydraulically, is provided, as well as at least one drive means 133 which is arranged between the sub-frame 128.3; 128.4 carrying the first roller 102; 102' and the sub-frame 128.1; 128.2 carrying the second roller 103; 103'; 106 supporting subframe 128.1; 128.2, a stop means 119 is provided which is effective and can be set or adjusted, for example, via actuating and/or drive means 146 and/or by a servomotor 155 - and whose stop effect can be controlled or regulated, for example - and which can be introduced into the adjustment path selectively and/or to a greater or lesser extent, for example, in a way that limits the travel. In principle, any stop means 119, preferably adjustable, can be provided as the stop means 119, by means of which an adjustment movement between the two relevant sub-frames 128.1; 128.2; 128.3; 128.4 can be limited and preferably adjustable with respect to the end position. These can be, for example, one or more stops 119 based on a respective screw thread, which can be brought into a desired position, in particular rotated, manually or via a remotely operated actuating and/or driving means 146 - possibly via a gear and/or by a servomotor 155. In a preferred embodiment here, stop means 119 based on a wedge gear, for example wedge-shaped strips designed in opposite directions, e.g. as stops 119, are provided as stop means 119, which interact in pairs with opposite sides and have a thickness that varies in opposite directions. For positioning, it is sufficient if, for example, one of the wedge-shaped strips is moved or can be moved against the other in the longitudinal direction of the pair of strips by a suitable actuating and/or driving means 146, e.g. a motor-driven actuator 146 designed, for example, by a screw drive, or a motor-driven rack. By means of such stop means 119, a very sensitive variation of the end position to be defined by the stop means 119 can be achieved with a large length of the interacting sides and a small gradient in the strength.

In an advantageous embodiment, at least one actuator 109; 109', which effects the variation and/or the setting force between the two rollers 103; 103';106;106' forming the second nip 107; 107' between them and comprises a drive means 132; 133, is designed to be force-based or - in a particularly advantageous embodiment - optionally force-based or position-based. For example, a drive means 133, in particular a cylinder-piston system 133 that can be pressurized with pressure fluid, preferably hydraulically, is provided as the drive means 133 on the two sub-frames 128.1; 128.2, which carry the rollers 103; 103';106;105' forming the second nip 107; 107' between them, directly or indirectly, and can be operated or driven in a force-based manner, in particular can be operated or driven in a force-controlled or force-regulated manner, as well as at least one cylinder-piston system 133 that can be pressurized with pressure fluid, preferably hydraulically, and at least one piston rod 134 between these two sub-frames 128.1; 128.2 effective lifting device 119 which can be adjusted via actuating and/or driving means 146. The lifting device 119 can be designed in a manner as described above or in a manner deviating from this, but at least adjustable in its lifting effect, e.g. controllable or adjustable.

The drive means 133 can act directly or indirectly on the two adjacent sub-frames 128.1; 128.2; 128.3; 128.4 or rollers 102; 103; 102';103' in that one active end of the drive means 132; 133, e.g. the piston or the piston rod 142 extending therefrom of a cylinder-piston system 132; 133 that can be acted upon with pressurized fluid, in particular hydraulically, for example force-controlled or position-controlled, on the one hand and/or one end of the cylinder 166 on the other hand, e.g. directly on the respective sub-frame 128.1; 128.2; 128.3; 128.4 or the respective rollers 102; 103; 102';103'. However, a connection can also be made indirectly, e.g. via further means that transmit the actuating movement and/or actuating force, e.g. a one- or multi-part transmission element that can be subjected to tension and/or compression, e.g. in the form of a tension and/or push rod, that extends or continues the piston 167 or the piston rod 142 on the one hand and/or possibly the cylinder 166 on the other. The respective connection of the actuating device 141 comprising the drive means 133 or directly of the drive means 133 itself, e.g. via pressure and/or tension plates 143; 144, determines an attack surface for the effect of the drive means 132; 133 in the present sense. The two active ends of the actuating device 141 or the drive means 133 encompassed by this is connected to the respective sub-frames 128.1; 128.2; 128.3; 128.4 in the direction of travel not only in a tensile but also in a pressure-resistant manner. This enables not only the movement towards one another but also an active movement away from one another.

In a preferred embodiment, at least one adjusting device 141; 165 comprising a drive means 132; 133 and causing a relative adjusting movement and/or pulling force between the two sub-frames 128.2; 128.3; 128.4, in particular an above-mentioned pulling device 141; 165, e.g. in the form of a tensioning device 141; 165, engages between two or each two sub-frames 128.1; 128.2; 128.3; 128.4 in such a way that it is attached to the sub-frames 128.1;

128.2; 128.3; 128.4 state that they move the two rollers 102; 103; 102';103' or the adjacent sub-frames 128.1; 128.2; 128.3; 128.4 into a relative position or setting relating to a predetermined gap width b104 _SO ii and/or setting force using a force directed towards one another between the sub-frames 128.1; 128.2; 128.3; 128.4 and - if necessary against a force directed opposite to the setting direction by the powdered material 004 or the coated carrier substrate 006 - keep this relative position or setting force constant except for a deviating specification regarding the relative position and/or setting force to be maintained. This means that it is possible, for example, to B. position- or force-based adjustable or controllable, drive means 132; 133 can introduce a tensile force between the sub-frames 128.1; 128.2; 128.3; 128.4, which moves the sub-frames 128.1; 128.2; 128.3; 128.4 or rollers 102; 103; 102';103' in the case of position-based adjustment to a desired gap width b104 _SO ii or in the case of force-based adjustment to a desired setting force - possibly against the opposing forces caused by the material 004 or the product strand 002 - or holds them at such a position. In contrast to the application of a pure thrust force to one of the two rollers 102; 103; 102';103' or partial frames 128.1; 128.2; 128.3; 128.4 from an outside has the advantage that the setting force only acts on the relevant roller gap 104; 104';107;107', and not - e.g. by a possibly co-caused pressing of the second roller 103 against a further roller 103'; 106 - additionally and uncontrolled applies a force to a further, e.g. second, gap 107; 107' which is adjacent in the adjustment direction. The at least one drive means 132; 133 or the adjusting device 141; 165 comprising the drive means 132; 133 acts with its or its two active sides or active ends on the adjacent rollers 102; 103; 102';103' or sub-frames 128.1; 128.2; 128.3; 128.4 in particular in such a way that, in order to set the relevant gap 104; 104'; 107 between the adjacent rollers 102; 103; 102';103', it acts on these or their sub-frames 128.1; 128.2; 128.3; 128.4 are subjected to an actuating force directed towards one another, ie a tensile force causing the movement and/or actuating force is introduced between the two sub-frames 128.1; 128.2; 128.3; 128.4, which brings about the above-mentioned advantage.

In the advantageous solution proposed here, one or more, for example, the above-mentioned adjusting devices 141 with a drive means 132; 133 act with their respective active ends, i.e. the ends of the drive means 132; 133 or the adjusting device 141 which can be varied by activation in terms of the distance from one another and/or the tensile force exerted between them, on the adjacent rollers 102; 103; 102'; 103' or sub-frames 128.1; 128.2; 128.3; 128.4 in such a way that - for a e.g. B. position-based or force-based adjustment - by means of this between the two adjacent rollers 102; 103; 102'; 103' or partial frames, a tensile force causing a relative movement between the rollers 102; 103; 102'; 103' or partial frames and/or adjustment force between the rollers 102; 103; 102'; 103' can be introduced, i.e. that the adjusting device 141 or the drive means 132; 133 pulls the two rollers 102; 103; 102'; 103' or partial frames 128.1; 128.2; 128.3; 128.4 towards one another for an adjustment - e.g. position-based or force-based.

In the embodiments according to Figures 18 to 22, a force-based operable or operated, in particular force-controlled or force-regulated operable or operated drive means 133 and/or a drive means 133 designed as a cylinder-piston system 133 that can be acted upon by pressurized fluid, in particular hydraulically. Such a cylinder-piston system 133 is preferably designed or configured such that a force of at least 20 kN, preferably at least 50 kN, can be applied by it in the relevant roller gap 104; 104';107;107'. Preferably, at least two such cylinder-piston systems 133 are provided on each frame side, which act between two adjacent sub-frames, whereby the above-mentioned force or line force can be applied by their entirety, for example.

The rollers 102; 102'; 103; 103'; 106 can basically be mounted on a respective axis that is non-rotatably mounted in the frame walls 131.1; 131.2; 131.3; 131.4 of the respective sub-frames 128.1; 128.2; 128.3, 128.4 via corresponding bearings 151, or advantageously - as shown for example in Figures Fig. 18 to Fig. 22 and Fig. 25, Fig. 26 and Fig. 28 - with front-side roller journals in bearings 151 designed as radial bearings 151, wherein the bearings 151 in turn are mounted in or on the respective frame walls 131.1; 131.2; 131.3; 131.4 are provided or arranged. In both cases, the rollers 102; 102'; 103; 103'; 106 or their roller necks or axes, viewed in the axial direction, are effectively supported radially on a width b151 of the bearing 151, which is determined by one or more rows of bearing elements supporting the roller necks or axes against the relevant sub-frame 128.1; 128.2; 128.3, 128.4. In the case of the radial bearing 151 that enables rotation, this can be one or more rows of rolling elements or sliding surfaces arranged in the circumferential direction. The effective support width b151 results from the distance between the two outer edges of the single bearing element row or the two outer bearing element rows.

In a particularly advantageous design - e.g. with regard to the lowest possible deformation - two or two of the adjacent and spaced-apart and/or partial frames 128.1; 128.2; 128.3; 128.4 whose adjusting force can be varied relative to one another, an adjusting device 141; 165 with its two effective ends, whose distance from one another can be varied, is attached to one of the two partial frames 128.1; 128.2; 128.3; 128.4 in such a way that the same roller, perpendicular to the rotation axis R102; R103, R102';R103', of at least one of the rollers 102; 103; 102';103';106; mounted on the two adjacent partial frames 128.1; 128.2; 128.3; 128.4 106', in particular running within the frame wall width, plane G at least the respective effective support width b151, viewed in the axial direction, of the rollers 102; 103; 102';103';106;106' mounted in the two sub-frames 128.1; 128.2; 128.3; 128.4 as well as an attack surface formed in the area of the acting with the respective sub-frame 128.1; 128.2; 128.3; 128.4, for example the cross-section of a pressure and/or tension plate 143; which is supported on the end of the adjusting device 141; 165 on the respective sub-frame 128.1; 128.2; 128.3; 128.4 or is fastened to it. 144, in particular a working cross-section, ie the effective piston or

Cylinder inner cross-sectional area, in the cylinder 166 of the drive means 133, which is formed, for example, by a cylinder-piston system 133. This ensures that the tensile stress acts in the alignment of the support and tilting in the bearing 151 caused by the tensile stress is avoided.

In a preferred embodiment, for all designs of the application units 101; 10T or double application units 101. 10T presented both in connection with the partial frames 128.1; 128.2; 128.3; 128.4 and in another design of a single or multi-part frame 128 - the rollers 102; 103; 102';103',106;106' are arranged relative to one another, at least in the operating position, such that their rotation axes R102; R103, R102';R103' intersect the same connecting line in at least one radial alignment. Such an embodiment should also be suitable for arrangements with one or more rollers 102; 103; 102';103',106;106' in the above sense of a "planar arrangement" in which the rollers 102; 103; 102';103',106;106' - at least along one side Support connecting lines - preferably in a middle area of the respective roller lengths.

For the force-based drive means 133 or actuators 133, the force applied by the drive means 133 is preferably adjustable, in particular controllable or adjustable. In the case of cylinder-piston systems 133 that can be operated with pressurized fluid, e.g. with compressed air or preferably with a pressurized fluid (e.g. oil under excess pressure), the pressure of the pressurized fluid provided by a pressure source is adjustable, in particular controllable or adjustable, at least in an adjustment range required for operation, e.g. via a pressure control valve or a pump that can be controlled or regulated with respect to the pressure to be provided on the output side.

In the case of the force-based set or controlled or regulated second roller gap 107; 107' and the position-based set or adjustable, controlled or regulated first roller gap 104; 104', at least the respective first roller 102; 102' or its sub-frame 131.3; 131.4 is not stationary in the direction of adjustment during production, but is movable or freely mounted at least within an adjustment range, e.g. of at least ±5 pm. This makes it possible to move the first roller 102; 102' in the event that the distance d104; d104' between the first and second rollers 102; 103; 102'; 103' fluctuates due to possibly slightly fluctuating material densities.

Basically independent of, but advantageously in conjunction with one of the above-mentioned designs, variants, configurations, embodiments or configurations of the application units 101; 10T and/or coating devices 100; 100* and/or machine configurations and/or frames 128, in a particularly advantageous embodiment at least the first and second rollers 102; 103; 102; 103' with their R102; R103, R102';R103' - generally or in at least one operating situation - are inclined to one another, i.e. are not stored or cannot be stored parallel (see e.g. principle from Fig. 23). However, these preferably run in two parallel planes.

If such a bearing is to be implemented generally and without the possibility of variation, the inclined arrangement can already be taken into account in the arrangement of the bearings 151 in a one-part or multi-part frame 128.1, 128.2, 128.3, 128.4.

Preferably, however, the axes of rotation R102; R103, R102'; R103' can be tilted against one another, i.e. they can be tilted from a parallel position to a position opposite one another or to different angles of inclination a. For example, one of the rollers 102; 102'; 103; 103', in particular the second roller 103, 103', is operationally fixed in space during the alignment of its R102; R102', R103; R103', although it can possibly be moved parallel in space without changing the inclination, and the other of the rollers 102; 102'; 103; 103', in particular the first roller 102; 102', has its axis of rotation R102; 102' relative to the alignment of the R102; R102', R103; R103' and/or mounted so as to be inclinable relative to the course of the rotation axis R102; R102', R103; R103' of the other roller 103; 103'; 102; 102', in particular the second roller 103; 103'. The pivoting preferably takes place about an actual or imaginary pivot axis which, for example, lies in a plane comprising the rotation axes R102; R102', R103; R103' of the two rollers 102; 103; 102'; 103' and/or preferably runs perpendicular to the rotation axes R102; R103; R102'; R103' of both the first and the second roller 102; 103; 102'; 103' and/or their rotation axes R102; R103; R102‘; R103‘ intersects.

Such inclination can in principle be realized directly via a special design of the bearing that accommodates the inclinable roller 102; 102';103;103' in the frame 128. For example, a bearing 151, e.g. a bearing 151 comprising an eccentric, can be provided on at least one, preferably on both sides, by means of which a radial position of the relevant rotation axis R102; R103, R102';R103' in the bearing 151 can be varied. Alternatively, a radially movable bearing can be provided on one or preferably on both sides of the frame 128, through the movement of which the relevant Bearing point can be varied radially.

Preferably, the first and the second roller 102; 103; 102; 103' of a same application unit 101; 10T, e.g. on the first and/or second application unit 101; 10T, corresponding e.g. to an embodiment of the multi-part frame 128 described above or below, are mounted in or on mutually different sub-frames 128.1; 128.2; 128.3; 128.4, wherein one of the two sub-frames 128.1; 128.2; 128.3; 128.4, preferably the sub-frame 128.3; 128.4 carrying the first roller 102; 102', as a whole, i.e. together with the associated frame walls 131.1, 131.2, 131.3, 131.4, one or more cross members 136; 137 and the roller 102; 103; 102'; 103' mounted therein, can be pivoted about a pivot axis S running perpendicular to its axis of rotation R102; R103, R102'; R103' and intersecting this at least over the maximum effective width of the roller 102; 103; 102'; 103' (see e.g. Fig. 18 to Fig. 20 and Fig. 22 to Fig. 25).

In an advantageous embodiment, the pivotable sub-frame 128.1; 128.2; 128.3; 128.4 is mounted on at least two bearing points 153 which are spaced apart from one another in the circumferential direction about the pivot axis S, wherein they lie at a radius Rs on a circular arc K which runs about the pivot axis S and/or determines the position of the pivot axis S (see, for example, Fig. 24). The bearing points 153 are formed, for example, by sliding or preferably rolling elements 153, e.g. rollers, which are arranged in two spaced-apart bearing blocks 147. The rollers can rotate about an axis parallel to the pivot axis S. The radius Rs of the circular arc K is, for example, greater than half, in particular than the entire maximum usable width of the sub-frame 128.1; 128.2; 128.3; 128.4 pivoted roller 102; 103; 102'; 103'. This allows a large adjustment range to be achieved for the smallest changes in inclination.

The bearing blocks 147 are, for example, perpendicular to the rotation axes R102; R103, R102';R103' of the roller 102; 103; 102';103' carried by the pivotable sub-frame 128.1; 128.2; 128.3; 128.4 are mounted on guides 138 and can be displaced on these together with the sub-frame 128.1; 128.2; 128.3; 128.4 mounted thereon in a direction perpendicular to the rotation axis R102; R103, R102';R103'.

In a preferred embodiment, the bearing points 153 for supporting the pivotable sub-frame 128.1; 128.2; 128.3; 128.4 interact with bearing surfaces 154 facing the bearing points 153, which are arranged in a lower region of the sub-frame 128.1; 128.2; 128.3; 128.4, in particular in the region of the lower end of the two relevant frame walls 131.1, 131.2, 131.3, 131.4 and/or - at least within an adjustment range for the pivoting movement in the circumferential direction of the circular arc K - have a surface supported on at least one bearing point 153 with a profile curved in the shape of a circular arc at least within an adjustment range. The radius of curvature preferably corresponds to the above-mentioned radius Rs.

In principle, pivoting can be effected manually, but preference is given to a drive means, in particular one that can be operated remotely, by means of which the relevant sub-frame 128.1; 128.2; 128.3; 128.4 can be pivoted.

When pivoting or the angle of inclination a, for example, this involves angles that are between 0.1° and 2.0°, in particular between 0.5° and 1.5°, preferably 1.0°. The adjustment range for pivoting can then be, for example, a range from 0° to at least 1°, advantageously from 0° to at least 1.5°, or even from 0° to 2.0° or possibly more.

The above description for the partial frame 128.1; 128.2; 128.3; 128.4 which can be pivoted about the pivot axis S is to be transferred to all of the versions presented for the divided frame 128; 128.1, 128.2, 128.3, 128.4 with the proviso that the partial frame 128.1; 128.3 of the first or second roller 102; 103, in particular the first roller 102 of a simple application unit 101, i.e. intended for one-sided application, or the sub-frame 128.1; 128.3; 128.2; 128.4 of the first or second roller 102; 103, in particular the first roller 102 of both application units 101; 10T of a double application unit 101; 10T is pivotable in the above-mentioned manner and is advantageously designed with the above-mentioned means.

Regardless of the pivoting of the roller 102; 103; 102'; 103' together with or without the sub-frame 128.1; 128.2; 128.3; 128.4, the pivot axis S preferably lies in a plane comprising the rotation axes R102; R103; R102'; R103' of the two adjacent rollers 102; 103; 102'; 103' and/or runs perpendicular at least to the rotation axis R102; R103; R102'; R103' of the pivotable roller 102; 103; 102'; 103', advantageously to the rotation axes R102; R103; R102'; R103' of both the first and the second roller 102; 103; 102'; 103' and/or intersects at least the rotation axis R102; R103; R102'; R103' of the pivotable roller 102; 103; 102'; 103', advantageously the rotation axes R102; R103; R102'; R103' of both the first and the second roller 102; 103; 102'; 103'. Advantageously, the pivot axis S of the pivotable roller 102; 102'; 103; 103' intersects the rotation axis R102; R103; R102'; R103' of the pivotable roller 102; 103; 102'; 103', advantageously the rotation axes R102; R103, R102'; R103' of both the first and the second roller 102; 103; 102'; 103', preferably in the middle area, i.e. for example at most 15% of the usable length from the center, or in particular at the height of the center of the maximum usable roller width. In the illustrated and preferred embodiment, the pivoting movement of the rotation axis R102; R103, R102'; R103' takes place in a plane running perpendicular to the pivot axis S, without the plane moving in the direction of the pivot axis during pivoting and/or without the pivot axis changing its position in space. This makes it possible to pivot independently for switching on and off and vice versa.

In an alternative embodiment of an actuator 109; 109' to the above embodiment, by which the rollers 102; 102';103;103' or roller gaps 104; 104';107;107' to be adjusted, in particular the relevant or respective first roller 102; 102', and/or the gap width b104; b104' between the first and second rollers 102; 103; 102';103' can be adjusted in a position-based manner, e.g. operated or operable in a position-controlled or position-regulated manner, the actuator 109; 109' which adjusts the first and second rollers 102; 103 to one another or their adjusting drive comprises one or more drive means 132 which are operated or operable in a position-controlled or position-regulated manner and which can assume a defined and/or predeterminable position, e.g. by itself or by appropriate control or regulation.

In a particularly advantageous embodiment shown here, the position-controlled or regulated drive means 132 of the travel- or position-based adjustable actuator 109 is controlled by a drive means which is adjustable in the position of its output means, e.g. B. a rotor or in particular piston 167, controlled and/or regulated or controllable and/or adjustable via a control or regulating variable and operated by pressurized fluid, in particular hydraulically, a drive means 132, in particular a hydraulically operated drive means 132 with respect to the position of the piston 167, in short the piston position, with regard to a control or regulating variable formed by the gap width b104 or by a variable correlating with and/or representing the gap width b104, is formed as an actuator (see e.g. Fig. 25 and Fig. 26). In this case - fundamentally regardless of whether an external variable such as e.g. B. a target gap width b104 _SO ii or another value correlated with and/or representing this, such as the piston position itself, is used - the piston 167 of the cylinder-piston system 132, viewed in the direction of adjustment, can be controlled and/or regulated in a defined manner with regard to its position via the target or reference value, and in particular in the position assumed by the variation - e.g. within the working range, independently of a force effect on the piston which varies during this time, e.g. its direction of movement - until, for example, a new variation is deliberately initiated on the input side by a new setpoint value. The piston 167 can, but does not have to, be controllable or adjustable with regard to its absolute position, but must be able to be positioned in a defined manner at least in its position by an associated control and/or regulating device 156 and held in this position by appropriate control or regulation. The cylinder-piston system 132 is designed in particular to be double-acting, ie the piston 167 can be pressurized with pressure fluid from both sides.

A quantity correlated with and/or representing the gap width b104 can in principle be any measurement quantity that describes the size of the adjustment movement, a bearing change of a measuring point or a distance that changes during adjustment, such as the piston position, a distance between roller-fixed measuring points or a moving point in the drive train.

In particular, the actuator 109 for the path- or position-based positioning of the gap 104 comprises as an actuator, i.e. as a drive means 132, a hydraulic cylinder-piston system 132, which can be operated or is operated, in particular is controlled or regulated, via an actuator formed by an actuating means 164; 164* with respect to a target or reference variable formed by the gap width b104 or a variable correlated therewith and/or representing it.

In this case, the hydraulically operated cylinder-piston system 132, which is controlled and/or regulated with respect to the piston position with regard to the target or reference variable, can basically be controlled or controllable as part of a control chain Sb with regard to a target gap width b104 _SO ii or with regard to a target gap width b104 _SO ii with regard to a predetermined or predeterminable gap width b104 or with regard to a variable representing the gap width b104. be adjustable (see e.g. Fig. 26 to Fig. 29).

Preferably, the actuating means 164; 164* as an actuating element together with the cylinder-piston system 132 as an actuator, with a sensor system 157 for detecting the gap width b104 or a variable correlated with and/or representing the gap width b104, with the actuating means 164; 164* and with control means 171, e.g. a controller 171 for short, are components of a control circuit Rb, by means of which the gap width b104 can be controlled as a reference variable to achieve and maintain a target width b104. The drive comprising the cylinder-piston system 132, the actuating means 164; 164* and the controller 171 forms in its entirety, for example, a hydraulic drive, in particular a servo-hydraulic actuator or drive, which is controlled or controllable here in particular with regard to a position or location. The term "control means 171" or "controller 171" is intended to include not only the controller circuit or logic itself but also any supply, amplifier stages, etc. that may be required for this purpose. The actuating means 164; 164* can be summarized together with the control means 171 acting on it under the term "control device 156" and can be shown as such in a partially simplified form in the figures.

In the case of control, a defined piston position specified to the drive means 132, for example via control means of a control chain Sb, or a defined variation of the assumed piston position can be made possible, for example, by providing an integrated position sensor in the cylinder-piston system 132 itself, by means of which the specification supplied via the control chain Sb can be implemented.

In the case of a hydraulically operated cylinder-piston system 132 which is controlled or regulated with respect to the piston position in relation to another, e.g. external, size, e.g. gap width b104, layer thickness d003 or basis weight FG, this is to be integrated into a corresponding control chain Sb; SF; Sd; S“d or into a corresponding Control loop Rt>;F;Rd; R“d is integrated with a corresponding external sensor or an external measuring system. The control chain Sb; SF; Sd; S“d or control loop Rb; RF; Rd; R“d relating to the external variable is then used to vary the specified target gap width b104 _SO ii or piston position accordingly.

The position-controlled or position-regulated drive means 132 is preferably formed by the above-mentioned hydraulically actuated or actuated cylinder-piston system 132 with at least one cylinder 166, in which a piston 167 movable in the cylinder 166 separates at least two chambers 168; 169 from one another in terms of fluid technology, regardless of whether the target gap width b104 _SO ii or a variable correlated with and/or representing this is used as the target or reference variable for positioning the piston 167. The piston 167 acts on a piston rod 142 which extends from the front of the cylinder 166 via a suitable seal and which can be formed in one piece or can be extended in a tension- and compression-resistant manner by one or more tension and/or compression rods.

In the preferred embodiment of a hydraulically operated drive means 132, in particular a cylinder-piston system 132, which is controlled and/or regulated with respect to a piston position with regard to an above-mentioned target or reference variable, the chambers 168; 169 separated from one another by the piston 169 can be supplied with more _or less pressurized fluid, in particular in a metered manner and/or to a defined extent, via a pressure medium line 158; 159 from an actuating means 164; 164*, regardless of whether the gap width b104 in the form of a target gap width b104 SO ii or a variable representing this and/or correlating with this and/or representing this is used as the target or reference variable for the positioning of the piston 167, so that the piston position or position can be adjusted depending on the inflow and outflow in the chambers 168; 169 in a defined manner in the cylinder 166, and with it the piston rod 142 protruding from the cylinder 166 or its - possibly extended - effective end, whereby, for example, the cylinder 166 is directly or indirectly connected to one of the first Gap 104 forming rollers 102; 103, e.g. on the first roller 102, and the piston rod 142 - if necessary via an extension - indirectly or directly engages the other roller 103; 102 of the adjacent roller pair 102, 103, e.g. on the second roller 103, or vice versa. The effective length or

Change in effective length of the drive means 132, in particular of the cylinder-piston system 132, as a result of a change in position of the piston 167 in the cylinder 166 and thus on the change in distance between the points of application of the drive means 132 or of the adjusting device 141 comprising it on the two rollers 102; 103 or their sub-frames 128.1; 128.2; 128.3; 128.4.

If required, i.e. in the event of a required adjustment, the respective chamber 168; 169 can optionally be supplied with additional pressure fluid via the actuating means 164; 164*, whereby pressure fluid is removed from the other chamber 169; 168 in accordance with the volume to be released or is discharged by displacement.

The actuating means 164 acting as an actuator can, in an advantageous first embodiment (see e.g. Fig. 26 and Fig. 27), be designed as an adjustable or switchable valve 164, in particular a multi-way valve 164, e.g. directional valve 164 for short, by means of which, depending on the selected switching state sO; s1; s2; s3, in a first switching state s1, e.g. a holding state s1, none of the chambers 168; 169 or in a second switching state s2, e.g. a first passage state s2, one or in a third switching state s3, e.g. second passage state s3, the other chamber 168; 169 is or can be supplied with additional pressure fluid from a connected pressure fluid source P, while preferably at the same time the other chamber 169; 168 is or can be relieved accordingly by discharge into a reservoir R. From the reservoir R - which is, for example, at ambient pressure level or at least at a pressure level lower than the working pressure level in the cylinder 166 - the pressure fluid source P, e.g. a pressure medium container with the pressure fluid, ie the pressure fluid under a hydraulic working fluid under excess pressure, for example a hydraulic oil. The first or holding switching state s1, which concerns holding the state reached, should also include an embodiment in which a self-flow, in particular a slight and/or possibly adjustable flow is made possible in both chambers 168; 169 in order to compensate for any losses caused by leaks and thus to maintain the piston position assumed and/or the existing pressure despite leaks. In this respect, both chambers 168; 169 in the holding switching state s1 are not fluidically connected to the pressure fluid source P at all or possibly to the same, in particular slight or throttled extent. Since the holding state s1 aims to maintain a balance between the two chambers 168; 198 in such a way that the piston 167 moves neither to one side nor to the other, this can also be referred to here as an equilibrium state. In particular, in the holding state s1 there is no or no significant pressure difference between the chambers 168; 169, so that the piston 167 rests in the assumed position.

In the second or third switching state s2; s3, a position of the piston 167, and thus the active end connected to the piston 167, can be varied to a defined extent in the cylinder 166 by a targeted and/or metered supply of the pressure fluid into one of the chambers 168; 169 - in particular with simultaneous discharge of the pressure fluid from the other chamber 169; 168. The active ends of the cylinder-piston system 132 - and thus, for example, the rollers 102; 103; 102'; 103' or partial frames 128.1; 128.2; 128.3; 128.4 actively connected to them - can thus be varied in a defined manner in terms of distance when viewed in the direction of adjustment.

In the case preferred here and explained above of an adjusting device 141 acting on or between the two adjacent rollers 102; 103; 102';103' or their sub-frames 128.1; 128.2; 128.3; 128.4 with the acting ends, the effective length of the cylinder is increased when metered into the chamber 169 located on the side of the piston rod 142. Piston system 132 is shortened and the two rollers 102; 103; 102';103' or partial frames 128.1; 128.2; 128.3; 128.4 are moved towards one another by means of a tensile force, and e.g. when metering into the chamber 169 facing away from the piston rod 142, the effective length is increased and the two rollers 102; 103; 102';103' or partial frames 128.1; 128.2; 128.3; 128.4 are moved away from one another by means of a compressive force.

For a case not shown here, in which an adjusting device for position- or path-based adjusting is designed and arranged in such a way that the adjusting takes place or can be effected by pressing one roller in the direction of the other roller, in the opposite way, when metering into the chamber 169 on the side of the piston rod 142, one of the rollers 102; 103; 102'; 103' or one of the sub-frames 128.1; 128.2; 128.3; 128.4 would be moved away from one another via a tensile force, and e.g. when metering into the chamber 169 facing away from the piston rod 142, one would be moved in the direction of the other roller 102; 103; 102'; 103' or one in the direction of the other of the sub-frames 128.1; 128.2; 128.3; 128.4.

As shown in Fig. 27, for example, the directional control valve 164, e.g. as a 4/4-way valve 164, can additionally have a fourth switching state s4, namely a switching state s4 in which both chambers 168; 169 are connected to the reservoir R via the return line and are thus, for example, depressurized. The directional control valve 164 is preferably designed such that the fourth switching state s4 simultaneously represents a basic switching state s4, to which the directional control valve 164 returns when the actuator 176 is inactive. In the case of such a fourth switching state s4, only symbolically indicated throttling devices, e.g. so-called pipe throttles, can be provided in the line paths coming from the chambers 168; 169, in particular in the line path leading through the valve 164. This means that when the cylinder-piston system 132 is depressurized, e.g. This can prevent a sudden relaxation, e.g. when the operation is stopped. Independently of this or advantageously in addition to the above, the directional or multi-way valve 164 in an advantageous embodiment can not only be switched to pass or block in a binary manner in at least one of its active switching states, but is designed for at least one, preferably both of the pass states s2; s3 in the manner of a proportional valve 164, in particular as a proportional directional valve 164, by means of which the fluid flow in the relevant switching state s2; s3 can be controlled or regulated with regard to the flow rate and/or with regard to the fluid pressure applied on the output side. In this advantageous embodiment, the directional valve 164 is preferably designed as a proportional directional valve 164, in the case of the above-mentioned fourth switching state s4 e.g. B. as a 4/4 proportional directional control valve 164, by means of which - in particular via the actuator 176 - in addition to an above-mentioned holding state S1, a second switching state s2, in particular first passage state s2, which can be varied in terms of its flow rate and/or output pressure, and/or a third switching state S3, in particular second passage state s3, which can be varied in terms of its flow rate and/or output pressure, can be set.

The directional control valve 164 or its actuator 176 can be adjusted by the actuator 176, which can be formed, for example, by a motor or preferably by a controllable electromagnet 176, regardless of whether it is designed as a directional control valve 164 with only binary passage states s2; s3 or as a proportional directional control valve 164 with at least one, preferably two passage states s2; s3 or passage states s2; s3 that can be varied in terms of the degree of opening, e.g. the flow and/or output pressure. The directional control valve 164 is preferably controlled or can be controlled via a controller 171 as part of a control circuit Rb; RF; Rd; R"d mentioned below, or if necessary, in the case of a path- or position-based setting of the gap 104 in question, via a relationship between the piston position and the gap width b104, it can be controlled by an appropriately configured control device and an inner control circuit relating to the piston position. Irrespective of the specific design of the above-mentioned valve 164, the cylinder-piston system 132 together with the directional control valve 164 and the controller 171 acting on the directional control valve 164 forms, for example, a so-called servo-hydraulic actuator 132, 164.

In order to be able to maintain a certain gap width b104 when pressing the powder 004; 004 into the film 007, an overpressure of, for example, at least 100 bar, preferably at least 150 bar, in particular of at least 200 bar (with 1 bar = 100 kPa) is provided by the compressed air source P pressure fluid. This also applies to the drive means 133 of the first embodiment, which is designed as a cylinder-piston system 133 and in which it works against a stop means 119. For displacement-based positioning, this ensures, for example, that a gap width b104 is kept constant despite possibly large material flows to be pressed in the film formation gap 104, and for force-based positioning, the possibility of high compaction and/or strong pressing with the carrier substrate 006 in the application gap 107.

In an alternative embodiment of the actuating means 164* acting as an actuator (see e.g. Fig. 28), this is designed as a pump 164* which is driven by a motor, in particular a servomotor - in particular a reversible one - and which can be controlled and/or regulated in particular with regard to a defined - in particular volume-related - delivery rate, and which pumps the pressurized fluid into one or the other chamber 168; 169 or out of the other chamber 169; 168. Depending on the design of the cylinder-piston system 132, additional elements such as expansion tanks and/or valves can be provided in the fluid circuit. The cylinder-piston system 132, together with the servomotor-driven pump 164* and possibly other components, for example the regulator 171 acting on the pump 164*, e.g. B. a so-called servo-hydraulic actuator 132, 164*.

The adjusting means 164 is used in the case of a controlled gap width b104. hydraulically operated drive means 132, for example, is directly actuated on the input side with a corresponding actuating command representing the desired gap width b104 _SO ii.

For all designs with a cylinder-piston system 132; 133 that can be pressurized with pressure medium, an emergency shutdown is advantageously provided, particularly because of the high pressures maintained and the protection against excessive adjusting forces, with a pressure sensor 177 that is provided in the line path that supplies the cylinder-piston system 132; 133 with pressurized fluid when one or the first roller is adjusted against the adjacent other or second roller 103; 103'; 102; 102', and with a switching logic implemented in control means and in signal communication with the pressure sensor 177, which, as a result of the pressure in the line path rising above a threshold value when one roller is adjusted against the adjacent other roller, depressurizes the pressure medium supply of the cylinder-piston system 132; 133, for example when using one of the above-mentioned Directional control valve 164 to the pressure-free switching state s4, or a switchover to an operating mode that causes a shutdown, for example when the above-mentioned directional control valve 164 is used in the switching state s2 that causes the shutdown. The pressure sensor 177 can be provided in the line connection 159 or - as shown - in the valve-internal output-side line path. The switching logic can be integrated, e.g. as a circuit or as a software routine, in the control means 171 that control the directional control valve 164.

In the preferred embodiment of a hydraulically operated drive means 132 regulated with respect to the gap width b104, the actuating means 164 or the actuator 176 serving to adjust the actuating means 164 - regardless of its design as a directional valve 164 or pump 164 - is supplied with an actuating command from a controller 171 on the input side, which compares a gap width b104 determined via the sensor system 157 with a desired or predetermined gap width b104 _SO ii, e.g. target gap width b104 _SO ii and, depending on the deviation, issues a corresponding control command to increase or decrease the gap width b104 _SO ii to the control means 164 or its actuator. For the gap widths b104; b104 _SO ii to be compared, the quantities representing the respective gap width b104; b104 _SO ii are also to be included here and in the following.

The controller 171 receives the determined gap width b104 directly or indirectly from the sensor system 157 that provides the gap width b104 or a measure of the gap width 104, if necessary via evaluation means 161 specifically set up for the sensor system 157 used. The sensor system 157 used and preferred here comprises two sensors 157.1; 157.2, e.g. capacitive sensors 157.1; 157.2, which are each directed on a line of the shortest distance between the two rollers 102; 103 onto the cylindrical roller surface of one of the two rollers 102; 103 or onto a cylindrical measuring surface that rotates rotationally symmetrically with the respective roller 102, 103 about its rotation axis R102; R103, e.g. a so-called measuring collar. The sensors 157.1; 157.2 each output a distance or a quantity representing the distance as a measured value, the sum of which relative to a reference value determined in a calibration measurement, e.g. with a gap width of zero or a small calibration thickness - e.g. after corresponding evaluation in the evaluation means 161 - provides the actual gap width b104 or the value of the quantity representing this.

In an advantageous embodiment, at least one of the above-mentioned hydraulically operated drive means 132 acts directly or indirectly between the first and the second roller 102, 103 on each frame side, but preferably two or possibly even more such drive means 132 per frame side,

It is particularly advantageous if a linear travel path is provided for the positioning of the respective movable rollers 102; 103; 102';103'; 106 or, in the above-mentioned case of a multi-part frame 128, the respective movable sub-frames 128.1; 128.3; 128.4 and/or - for example, despite the low thickness of the dry film 003; 003' or product strand 002 a travel path with a possible adjustment range of several, e.g. at least 2 mm, in particular or even at least 4 mm. The latter allows a sufficiently large stop for maintenance purposes or in the event of a malfunction.

Although the travel- or position-based actuator 109 is explained in connection with the first gap 104 preferred for this purpose, in the event that the second gap 107 is also to be set or adjustable in a travel- or position-based manner, the explanation is also to be applied accordingly to this.

Even if the actuator has been described only using the unprimed reference numerals, it is also to be transferred to a corresponding actuator 109' with primed reference numerals if a second first gap 1034' is present.

Basically, the design of the respective actuator 109; 109' engaging between the rollers 102; 103; 102'; 103' of a pair of rollers with the acting ends in the first design, i.e. with a force-based actuator 133 and stop means 119, and in the second embodiment, i.e. with one or more hydraulically operated drive means 132 controlled and/or regulated with respect to the piston position, is to be applied to an arrangement of the rollers 102, 103; 102; 103' in a one-piece frame 128 and/or to be applied to an engagement with respective bearings or bearing blocks which are adjustably mounted on the side walls of a one-piece or multi-piece frame 128 and which support the roller 102 to be adjusted. For example, a roller 102; 103; 106; 102'; 103' with their roller journals on both sides in a bearing or bearing block mounted on the frame 128, on a frame part or on a subframe so as to be linearly movable along an adjustment direction.

Preferably, such an arrangement of the actuator 109; 109' is also provided in the second embodiment of the actuator in connection with an above-mentioned multi-part frame 128 with several sub-frames 128.1; 128.2; 128.3; 128.4, wherein the above for the design of the sub-frames 128.1; 128.2; 128.3; 128.4 and/or for the configuration of the single or double application unit and/or for the pivotability of one of the rollers 102, 103, in particular the first roller 102, and/or the engagement in the plane G and/or for the formation of the force-based actuator 111; 11 T for the second roller gap 107 is to be applied accordingly, according to which for the setting of the second gap 107 between a roller 103'; 107 acting as a counter-pressure roller 103'; 107 and the first roller 102 or a further roller located therebetween, preferably in the manner described above for the first embodiment, a force-based or combined actuator 111 with at least one force-based operable or operated, in particular force-controlled or force-regulated operable or operated drive means 133, e.g. one or preferably several cylinder-piston systems 133, and optionally an adjustable stop 119 is provided.

In a preferred embodiment, the at least one drive means 132 or the adjusting device 165 comprising the drive means 132 also acts with its or their two active sides or active ends on the first and second rollers 102; 103; 102';103' or on their partial frames 128.1; 128.2; 128.3; 128.4, as explained above for the first embodiment, on the rollers 102; 103; 102';103' or partial frames 128.1; 128.2; 128.3; 128.4, in particular also in such a way that it is used to set the gap 104; 104' between the first and second rollers 102; 103; 102';103' apply an adjusting force directed towards one another to these or their sub-frames 128.2; 128.3; 128.4, i.e. introduce a tensile force between the sub-frames 128.1; 128.2; 128.3; 128.4, which has the above-mentioned advantage that the force resulting from position-based adjustment only acts on the relevant first roller gap 104; 104', and not additionally on the second gap 104; 104' - as can happen, for example, when an outer roller 102; 102' is applied with a force from the outside. In the solution proposed here, the respective drive means 132 or the adjusting device 165 comprising the drive means 132 each acts with one end directly or indirectly on one of the two rollers 102; 103; 102';103' or on their sub-frames 128.1; 128.2; 128.3; 128.4 and with the other effective end centrally or directly on the other of the rollers 102; 103; 102';103' or on their sub-frames 128.1; 128.2; 128.3; 128.4 and thus determine the relative position and/or the setting force applied between the rollers 102; 103; 102';103'.

The principle set out above of the adjusting devices 141 acting between the adjacent rollers 102; 103; 102'; 103', in particular pulling devices 141, e.g. in the form of tensioning devices 141, by means of which the rollers 102;

103; 102'; 103' for positioning or placing on top of each other in the positioning direction with a force directed towards each other, is - in particular for both the first and the second version of the actuator 141; 165 or drive means 132, 133 - of course to be read or applied to solutions in which the two rollers 102; 103; 102'; 103' to be pulled towards each other are not indirectly mounted in relatively movable sub-frames 128.1; 128.2; 128.3; 128.4, but elsewhere on a frame 128, base or sub-frame 128.1; 128.2; 128.3; 128.4. B. at least one of the two rollers 102; 103; 102'; 103' that are to be pulled towards each other can be mounted in or on the relevant frame 128, base or sub-frame 128.1; 128.2; 128.3; 128.4 so that it can move in the direction of adjustment. The adjustable roller 102; 103; 102'; 103' can advantageously be mounted in a linear bearing so that it can move in the direction of adjustment.

In an alternative, the hydraulically operated cylinder-piston system 132, which is controlled and/or regulated with respect to the piston position, can be controlled with respect to a predetermined or predeterminable layer thickness d003 or a quantity representing the layer thickness d003 as part of a control chain Sd or - e.g. by integration into a control circuit Rd with a sensor system 172 provided in the substrate path for determining the layer thickness d003 - can be regulated with respect to a predetermined or predeterminable layer thickness d003 or a quantity representing the layer thickness d003 (see e.g. Fig. 30 and Fig. 31). Such a sensor system 172 for determining the layer thickness d003 can, for example, at least one sensor 172.1 - e.g. capacitive or inductive, preferably a combination of inductive and capacitive - and/or is provided, for example, for determining the layer thickness d003 of the dry film 003 formed on the second roller or on a roller provided between the second and counter-pressure roller 103; 103'; 106 and/or is directed at a peripheral region of the roller 103 in question between the formation or absorption and the release of the dry film 003. In this case - as shown by way of example in Fig. 30, for example - the measured layer thickness d003 can be fed directly into the control device 156 and the hydraulically operated cylinder-piston system 132 can be varied in the event of a deviation via the adjusting means 164 on the basis of a comparison between a target thickness d003 _SO ii and the measured layer thickness d003. Or it can - as shown, for example, in Fig. 30. B. as shown by way of example in Fig. 31 - the measured layer thickness d003 in an external control loop R"d is first compared with the target thickness d003 _SO ii by a controller 174 and in the event of a deviation - e.g. based on a defined relationship, a varied value for the target gap width b104 _SO ii is first generated, which is fed to and/or used as a basis for the control loop Rb described above for controlling the gap width b104 as an internal control loop Rb for implementing the new target gap width b104 _SO ii.

In a further alternative to the control or regulation of the hydraulically operated cylinder-piston system 132, which is controlled and/or regulated with respect to the piston position, directed at the gap width b104, the hydraulically operated cylinder-piston system 132, which is controlled and/or regulated with respect to the piston position with respect to the above-mentioned target or reference variable, can be regulated with respect to a predetermined or predeterminable basis weight FG or a variable representing the basis weight FG, e.g. by integration into a control loop RFG, with a sensor system 413.1; 413.2 provided in the substrate path for determining the basis weight FG with respect to a predetermined or predeterminable basis weight FG or a variable representing the basis weight FG (see e.g. Fig. 33 and Fig. 34). The following also applies here for the design with or without the underlying inner control loop Rb for regulating the gap width b104. the above and is to be applied accordingly.

Even if in the above and in the associated figures the design with hydraulically operated drive means 132 is specifically explained and shown only for a pair of first and second rollers 102; 103 in conjunction with a roller 103'; 107 acting as a counter-pressure roller 103'; 107, this is of course to be applied accordingly to the second pair with a first and second roller 102'; 103' in the case of a double application unit 101; 101'.

The above-mentioned control chains Sb; Sd; S"d; SF or control circuits Rb; Rd; R"d; RF are to be applied to the first embodiment of the actuator 109; 109' with the proviso that the control chain Sb; Sd; S"d; SF or the control circuit Rb; Rd; R"d; RF in question acts on the actuating means 146, in particular on the actuator motor 155 included in the actuating means 146 for actuating the stop means 119, in particular the stop 119, instead of on the hydraulically operated cylinder-piston system 132 controlled and/or regulated with respect to the piston position. These variants are identified in Figures Fig. 29 to Fig. 31 and Fig. 33 by the reference symbol 146 in brackets for the actuating means 146.

In a preferred embodiment, for all versions of the application units 101; 10T or double application units 101; 10T - both for those presented in connection with the partial frames 128.1; 128.2; 128.3; 128.4 and for those otherwise designed with a single or multi-part frame - the rollers 102; 103; 102';103',106;106' provided in the application unit or double application unit 101; 10T; 101; 10T are arranged relative to one another, at least in the operating position, in such a way that their axes of rotation R102; R103, R102';R103'; R106 are in at least one radial alignment along the axes of rotation R102; R103; R102';R103'; R106 intersect the same connecting line, which runs horizontally in particular. In the case of one or more inclined rollers 102; 103; 102'; 102, 103';106;106', this connecting line coincides, for example, with the respective Pivot axis S. Without inclined roller 102; 103; 102';103',106;106', the rotation axes R102; R103, R102';R103'; R106 are advantageously parallel - as already explained in an embodiment variant described above - and even lie in the same plane, which here runs horizontally in particular.

For all of the above-mentioned designs, variants, configurations, embodiments or designs, the actuator 109; 109';111; 11 T and/or the bearing mechanism 112; 112';113;113' comprised thereby of at least the rollers 103; 103';106;106' forming the second gap 107; 107' are preferably designed to operationally form a gap width of at least 15 pm, advantageously of at least 30 pm, in particular of at least 50 pm, at the narrowest point and/or, in particular at least within the limits defining the maximum adjustment path, to form a gap between the two rollers 103; 103';106;106' via a product strand 002; 002' to be formed and/or by at least one adjusting mechanism 112; 112' and/or at least one actuator 109; 109', and/or to set and/or apply a line force of e.g. at least 500 N/mm, advantageously at least 700 N/mm, preferably a line force of between 500 N/mm and 3000 N/mm, in the second gap 107; 107', at least in the region of its width contributing to film formation and/or film application, between the rollers 103; 103';106;106' forming the second gap 107; 107' and/or to enable a desired line force to be kept constant even with fluctuating dry film thickness by - e.g. automatic or controlled - tracking of at least one of the two rollers 103; 106; 106; 103'. In contrast to tracking controlled via a control loop, automatic tracking is, for example, tracking which is carried out by the drive means - preferably force-based adjustable, in particular force-controlled or force-adjustable - or its application of force itself and without readjustment via an additional control loop. For all of the above-mentioned designs, variants, configurations, embodiments or designs, in a particularly advantageous further development, an extraction system 123; 123' is provided above the respective application unit 101; 10T or the application units 101; 101', through which any escaping gases or vapors that may arise can be extracted.

The rollers 102; 102'; 103; 103'; 106; 106' of the above-mentioned application units 101; 10T are preferably designed with a width in the range of 400 mm to 800 mm, in particular 500 mm to 700 mm, which can be used for film formation and/or application.

Basically independent of, but particularly advantageous in conjunction with one of the above-mentioned designs, variants, configurations, embodiments or designs of the coating device 100; 100* and/or one of the equipment and/or configurations for the machine explained in more detail below, a subsequent procedure for forming the dry film, in particular for a subsequent application to a carrier substrate 006 in e.g. an above-mentioned application unit 101; 101, in particular in conjunction with an above-mentioned multi-part design and/or the design of the actuators 109; 109'; 111; 11T, is of very particular advantage.

In this case - as already described above - in order to form or produce the dry film 003; 003' from a powdery material 004, for example as set out above, with the first roller 102; 102' and the second roller 103; 103', which forms a roller gap 104; 104' between their lateral surfaces with the first roller 102; 102', powdery material 004; 004' is fed to the roller gap 104; 104' via the region of the gusset above the roller gap 104; 104' and this is conveyed through the roller gap 104; 104' in order to form a dry film 003; 003' that is to be conveyed further on the lateral surface of the second roller 103; 103' when it passes through the roller gap 104; 104'. The first roller 102; 102' is thereby provided with a first peripheral speed V(102;102') in the area of its outer surface and the second roller 103; 103' can be driven or is driven at a second peripheral speed V103; 103' in the area of its outer surface. A basis weight FG, ie a mass related to a unit area of the dry film 003; 003', e.g. in milligrams per square centimeter (mg/cm ² ), of the dry film 003; 003' formed by the roller gap 104; 104' is determined by deliberately causing a variation of a ratio

V(102;102‘) : V(103;103‘) between the peripheral speed V(102; 102‘) of the first roller 102; 102‘ in the region of its outer surface and the peripheral speed V(103;103‘) of the second roller 103; 103‘ in the region of its outer surface is changed, i.e., for example, deliberately set.

The ratio V(102;102') : V(103;103') is varied, for example, within a range of 1:3 to 1:6, advantageously at least within a range of 1:4 to 1:5. The variation of the ratio V(102;102') : V(103;103') can be brought about here by varying the differential speed and vice versa, so that the above-mentioned variation of the ratio V(102;102') : V(103;103') can equally be regarded as varying the differential speed and vice versa.

It is particularly advantageous to provide a control circuit, e.g. a so-called closed loop, whereby during operation, depending on a determined measured value for a dimension representing the basis weight FG, the basis weight FG or a dimension representing the basis weight FG is controlled to a target value FG _S0 H or to a value in a permitted range by varying the ratio between the peripheral speeds V(102; 102';103;103') (see e.g. Fig. 32).

The variation of the ratio between the peripheral speeds V(102; 102';103;103') is advantageously carried out with a fixed but adjustable gap width b104. This can, for example, be adjustable in a position-based manner and/or in a size specified above. Preferably, the ratio between the peripheral speeds V(102; 102';103;103') is varied by varying the peripheral speed V(102; 102') of the first roller 102; 102', while the second roller 103; 103' continues to operate, for example, at the present, in particular stationary, machine speed.

A variation in the peripheral speed V(102; 102') of the first roller 102; 102 takes place, for example, by applying a control and/or regulating means 173 that controls and/or regulates the rotary drive, in particular the drive means 148, of the first roller 102 with an actuating signal that causes a variation in the relative speed, wherein in the preferred case of a first roller 102 driven by a single motor, the actuator is a drive controller 173 that controls and/or regulates the drive motor 147 and the reference variable is, for example, a changed value for a gear factor. In the case of a drive of the first roller 102 that is mechanically coupled via a gear, the control and/or regulating means 173 can be an actuator of a gear stage that can be adjusted with regard to the gear ratio and the actuating signal can be, for example, an actuating signal for adjusting the gear ratio.

The variation occurs, for example, along a, in particular linear, decreasing relationship between a differential speed on the lateral surfaces or a quantity characterizing the differential speed on the one hand and the basis weight or the measure representing the basis weight on the other. In this case, for example, at least in the applied adjustment range, a particularly negative gradient is advantageous in which, for example, a variation in the differential speed by 1% results in a change in the basis weight in the range of, for example, 1.0 to 1.5 mg/cm ² , in particular 1.1 to 1.3 mg/cm ² . The measure for a current basis weight can be determined by a measurement at a point downstream of the roller gap 104; 104' in the transport path of the dry film 003; 003' on the dry film 003; 003' that has not yet been applied, e.g. on the second roller 103; 103', or on the dry film 003; 003' that has already been applied to a carrier substrate 006, e.g. on the product strand 002. This can be done, for example, in conjunction with or based on the above-mentioned density measurement method, whereby a value for the basis weight is also obtained, or preferably via a measuring device 413 or sensor system 413.1, 413.2 mentioned below, for example, and preferably an ultrasound-based measurement that, for example, obtains a measure for the basis weight FG by comparison with results from a reference measurement or reference measurements.

With such a procedure, small fluctuations in the basis weight can be corrected without having to adjust rollers 102, 102'; 103; 103'; 106; 106 or sub-frames 128.1; 128.2; 128.3; 128.4.

The procedure is to be applied to setting or controlling a volume-related density by varying the ratio between the peripheral velocities V(102; 102'; 103; 103') of the corresponding ones.

The drive or drive motor 147 of the first roller, together with the control and/or regulating means 173 and the measuring device 413 or the sensors 413.1, 413.2, forms a control circuit R'FG for regulating the ratio between the peripheral speeds V(102; 102'; 103; 103') as a function of a basis weight FG determined - in particular inline (see e.g. Fig. 34).

As an alternative to the described control of the ratio between the circumferential speeds V(102; 102';103;103') depending on a determined basis weight FG, the input side can also use the by the above-mentioned sensor system 172 are used. In this case, the drive or drive motor 147 of the first roller 102 together with the control and/or regulating means 173 and the sensor system 172 for determining the layer thickness d003 forms a control circuit R'd for regulating the relationship between the peripheral speeds V(102; 102';103;103') as a function of a layer thickness d003 of the dry film 003 formed, determined in particular inline (see e.g. Fig. 32).

A machine for producing, in particular in an inline process, a multi-layer product (see e.g. Fig. 3, Fig. 10, Fig. 15, Fig. 16 or Fig. 17), which has an above-mentioned dry film 003; 003' formed from a powder mixture on at least one side of a carrier substrate 006, preferably comprises a substrate feed 200, through which the carrier material 006 can be fed to the machine on the input side, a first substrate path section 300, via which the carrier substrate 006 is fed to an application stage 100; 100* for applying the dry film 003; 003' on at least one side of the carrier substrate 006 and a second substrate path section 400, via which the carrier material 006 provided with the dry film 003 on at least one side can be fed to a product holder 500, by means of which the product can be combined to form product packages, e.g. into rolls or stacks.

In a particularly preferred embodiment, the application stage 100; 100* is designed in one of the above-mentioned designs, embodiments, configurations, embodiments or variants for the device 100; 100* described above. In this case, all designs, embodiments, configurations, embodiments of the first group of embodiments can be used instead of the application stage 100 shown as an example in Fig. 3, and all of the second group can be used instead of the application stage 100* shown as an example in Fig. 10, Fig. 15 or Fig. 16. In the embodiments of the machine shown in Fig. 15 and Fig. 16, variants can also be used for designs, embodiments, configurations, embodiments or variants of the first group for the application stage 100, ie with separate application devices 101 ; 101 to be used.

In an advantageous embodiment, the substrate feed 200 is formed by a substrate unwinder 200, in particular a roll changer 200, preferably by a roll changer 200 comprising several roll positions and/or qualified for non-stop roll changing. It can advantageously comprise a substrate guide element 202 designed as a motor-driven roller 202, in particular a pull roller 202, and/or a substrate guide element 203 in the form of a dancer roller 203 - e.g. spring-loaded on a lever or a guide transversely to the substrate path or deflected with a force.

The carrier substrate web 006 is unwound at the substrate unwinder 200 and fed to the substrate path leading through the machine at the unwinding location on the input side.

In the case of a pulling roller 202 included in the substrate unwinder and structurally associated therewith (see, for example, in Fig. 3 or Fig. 10), this can be included in a pulling mechanism 207, in particular a feed mechanism 207, which, for example, in addition to the pulling roller 202, has a drive means that drives the pulling roller 202 - in particular independently of other pulling rollers - and whose speed can be regulated and/or controlled, in particular a drive motor, e.g. in the form of a servo motor, and/or pressure rollers that can be placed on the pulling roller 202 to increase the friction. In this case, the roller 202 or the drive means - depending on the web tension conditions and/or web tension requirements present before and after the roller 202 - can also be operated or operated as a generator or to inhibit the advance of the carrier substrate web 006, for example in order to achieve a to establish or maintain a certain and/or desired web tension.

For example, a substrate guide element 208; 307 can be designed in the substrate path as a measuring roller 208, e.g. a web tension measuring roller 208; 307 (exemplary for all embodiments, e.g. shown in Fig. 16), still structurally associated with the substrate path in the roll unwinder 200 or already associated with the first substrate path section 300, by means of which, for example, the web tension or at least a variable representing the web tension can be determined in order to use this, for example, to regulate the web tension, e.g. via the conveying speed of individual units 100; 100*; 600 or one or more web guide elements 202; 308; 401; 502, in particular those that are positively driven by a motor.

The substrate feed 200 designed as a roll changer 200 advantageously comprises a roll drive that is mechanically independent of the rest of the machine and/or driven by a single motor and/or a lifting device to support a roll loading and/or roll unloading process.

In an advantageous embodiment, a device for lateral web edge control 204 (shown as an example for all embodiments, e.g. in Fig. 15), in particular a sensor system that detects a web edge and an actuator that causes a lateral offset of the carrier substrate, e.g. a pair of turning bars that can be pivoted about an axis running perpendicular to the transport direction Ts, can be provided in the substrate path section attributable to the substrate feed 200 and/or in the adjoining first substrate path 300. In a particularly advantageous embodiment, the web edge control 204 is combined with a bonding device 206, e.g. a bonding table 206.

Instead or additionally, in an advantageous embodiment, in the substrate path section of the substrate feed 200 and/or in the first substrate path 300, a Spreading device, in particular a single or multi-element web guide element with a convex outer surface, is provided.

In an advantageous development, a one- or multi-part pretreatment station 302, in particular a cleaning and/or deionization station 302, is provided in the first substrate path 300, by means of which the carrier substrate 006 is or can be freed from surface contamination, e.g. dust or cutting residues, and/or electrical charge carriers on one or both sides in a contactless or contacting process.

In the first substrate path 300, in particular downstream of any cleaning that may be provided, a measuring station 303 is advantageously provided, in particular with a sound- or radiation-based measuring device 303, by means of which the material thickness of the carrier material 006 can be checked for its thickness and/or homogeneity in the thickness and/or for contamination and, for example, in the event of impermissible deviations from a target specification, an optical and/or acoustic warning signal and/or an error signal is transmitted to a machine control system and/or a control station.

For all versions of the machine, in an advantageous embodiment, a substrate guide element 208; 307 can be designed as a measuring roller 307 (shown as an example for all versions in Fig. 15 and Fig. 16) in a substrate path section structurally assigned to the roll unwinder 200 and/or in an adjoining substrate path section of the first substrate path 300, by means of which, for example, the web tension can be determined in order to use this, for example, to regulate the web tension, e.g. via the conveying speed of individual units 100; 100*; 600 or one or more web guide elements 202; 308; 401; 502, in particular those that are positively driven by a motor. Only one of the two measuring rollers 208; 307 or, advantageously, both measuring rollers 208; 307 can be provided, in the latter case e.g. B. the downstream measuring roller 307 is used to determine and/or regulate the substrate path section upstream of the web tension in the first or only application point as described below.

In an advantageous development, a pretreatment station 304 designed as an application station 304 is provided in the first substrate path 300, for example, through which the carrier material 006 can be exposed to a binder and/or a primer on one or both sides. In this case, a dryer (not shown), e.g. a hot air or radiation dryer, can preferably be provided directly downstream of the application station 304.

In a particularly preferred embodiment, considered in principle on its own, but advantageous in conjunction with one or more of the other embodiments of the machine, a thermal pretreatment station 306, in particular a tempering station 306, e.g. an infrared radiation source 306, is provided in the substrate path immediately before the application stage 100; 100*, i.e., for example, downstream of the last substrate guide element 301; 307 interacting with the carrier substrate web 006, by means of which the carrier material 006 can be heated above ambient temperature, in particular to above 60°C, preferably to at least 80°C. This can, for example, be of particular advantage for activating a connection-supporting or connection-inducing agent 007; 007' provided or applied to the carrier substrate 006. Basically independent of this, but advantageously in conjunction with such a temperature control station 306, a sensor 311 for determining the temperature of the carrier substrate web 006, e.g. temperature sensor 311, in particular a contactless and/or radiation-based temperature sensor 311 can be provided. The sensor 311, e.g. as a temperature sensor 311, can be part of a control circuit for controlling the temperature of the carrier substrate web 006 with the temperature control station 306 that may be provided.

Instead of a pulling roller 202 or attributable to the pulling mechanism 207 or possibly in addition to this, a pulling roller 308 or a pulling mechanism 309 can be provided in the substrate path section 300 adjoining the substrate unwinder 200 and/or leading to the location of the first or only dry film application, i.e. to the first or only laminating gap 107; 107'. In the case of only one pulling roller 202; 308 or only one pulling mechanism 207; 309 in the substrate path between the unwinding from the roll 201 and the entry into the first or only laminating gap 107; 107', such a pulling roller 202; 308 or such a pulling mechanism 207; 309 can basically be structurally associated with the substrate unwinder 200, a device located between the substrate unwinder 200, in particular from the unwinding, and application stage 100; 100*, in particular the first or only application point, or structurally just as well be assigned or associated with the application stage 100; 100* on the input side. What is important here is that such a pull roller 202; 308 or such a pull mechanism 207; 309 is arranged upstream of the first application point, ie the first or only laminating gap 107; 107', in the substrate path, in order to build up or maintain a certain and/or desired web tension, for example in the subsequent substrate path section or in a part of the substrate path section formed by a subsequent substrate path section. The pull mechanism here has - in accordance with the pull mechanism 207 already described above - e.g. next to the pull roller 308 a drive means which drives the pull roller 308 - in particular independently of other pull rollers - and whose speed can be regulated and/or controlled, e.g. B. in the form of a servo drive motor, and/or pressure rollers that can be set on the pull roller 308 to increase the friction. The roller 308 or the drive means - depending on the web tension conditions and/or web tension requirements present before and after the roller 308 - can also be operated or operated as a generator or to inhibit the advance of the carrier substrate web 006 in order to build up or maintain a certain and/or desired web tension, for example in the subsequent substrate path section extending, for example, to a next clamping or web pulling point, or in a part of the substrate path section formed by a subsequent substrate path section. In an advantageous embodiment, an above-mentioned calender 600 or an above-mentioned calendering unit 600 with two rollers 601; 602, in particular calendering rollers 601; 602, which form a gap, e.g. a calendering gap, is provided in the second substrate path 400, in particular in the substrate path immediately after the application stage 100; 100*. This has the advantage, for example, that in the event that the desired density is not produced during the dry film application, an end product 001 or merely an intermediate product 002 that still needs to be cut can still be produced with the desired density in the active material layer 003; 003'.

In an alternative embodiment, already mentioned above but not shown in the figure here, the advantage of which lies, for example, in the independence of the processes and their optimization and thus in the quality and/or lower susceptibility to failure, a first above-mentioned machine is provided - e.g. in a plant or a system with several machines - for coating a carrier substrate 006, in particular an above-mentioned carrier substrate web 006, with a dry film 003; 003', which is formed from a powdery material 004; 004', which preferably comprises a coating device 100; 100* in one of the above-mentioned advantageous embodiments in the substrate path, and a separate, second machine for compacting the dry film 003; 003' by means of at least one calendering unit 600; 600* provided in the substrate path of the second machine. Although these machines can in principle be provided at different locations, they are preferably - e.g. B. in the same plant building - in a plant or machine arrangement for producing a multi-layer product 001 with a dry film applied to a carrier substrate, in particular for producing an electrode strand 002 or electrode units 001. In this case, a product strand 002, referred to here as a preliminary product, which has not yet been further compressed, is combined, for example, on the output side of the machine for coating in the product holder 500 designed in particular as a product winder 500 to form a roll 501 of preliminary product, and this Roll 501 is subsequently or at a later point in time fed to the second machine on the input side, in particular to a roll unwinder provided on the input side of this machine. The product strand 002 from the preliminary product is unwound there, guided through a calendering unit 600; 600' arranged in the substrate path, and wound up on the output side as a fully compacted product strand 001 to form a product roll 501 or laid out after a cross-cutting process provided downstream of the calendering unit 600.

Regardless of whether the above-mentioned calendering process takes place inline in the same machine in which the dry film 003; 003' is applied to the carrier substrate 006, or whether calendering takes place separately from the application in a different machine, e.g. a second machine having a calendering unit 600; 600*, the calendering unit 600; 600* comprises two rollers 601; 601*; 602; 602*, e.g. calender rollers 601; 601*; 602; 602*, of which e.g. at least one, preferably both, is or are heatable, in particular heatable in such a way that their outer surface - e.g. B. at an ambient temperature of 25°C - to at least 80°C, advantageously to at least 100°C, preferably to at least 120 and/or between which a pressure with a preferably adjustable line force of at least 500 N/mm, advantageously at least 700 N/mm, in particular at least 1000 N/mm, preferably up to at least 2000 N/mm, or in particular a line force lying between 500 N/mm and 3000 N/mm can be applied. The product strand 002, which is coated on at least one side, can be passed through the calendering gap for the purpose of further compaction of the dry film 003; 003' using pressure and/or a temperature higher than the ambient temperature. The calender rolls 601; 601*; 602; 602* have e.g. B. a diameter of at least 400 mm, in particular at least 500 mm, preferably at least 550 mm, and/or for example a usable width of e.g. at least 400 mm, in particular at least 500 mm, preferably at least 550 mm. For the manufacture of the mentioned products 001; 002, a concentricity of each roller 601; 601*; 602; 602* with a maximum deviation of ± 2 m, preferably of ± 1 mm from special advantage.

Basically independent of, but advantageous in conjunction with one or more of the other design variants of the machine, in a particularly advantageous embodiment in the second substrate path 400 after the application stage 100; 100*, in the case of a possibly provided calendering unit 600 downstream of this, a cooling device 402, e.g. with one or more partially wrapped tempered cooling rollers 402.1;

402.2, through which a product strand 002 passed through can be cooled, e.g. by at least 20°C, in particular by at least 50°C.

Basically independent of, but advantageously in conjunction with one or more of the other embodiments of the machine, in an advantageous further development in the second substrate path 400 is an inspection device 403; 403.1; 403.2, in particular based on an optical and/or acoustic measurement, e.g. with a sensor 403.1 directed to one side and a sensor 403.2 directed to the other side

403.2, by means of which the product surface can be checked for errors or defects, e.g. for completeness in the area and/or thickness of the applied dry film 003; 003'. The inspection device 403; 403.1; 403.2 can in this case - as shown in Fig. 15, for example - be provided in the substrate path downstream of the calendering unit 600 or - as shown in Fig. 16, for example - in the substrate path downstream of the application stage 100; 100' but upstream of the calendering unit 600. In the former case, errors caused by the calendering can be detected, but in the second case, errors caused in the application stage 100; 100' can be detected as early as possible. The inspection device 403 can preferably be in the form of sensors 403.1; 403.2 each side must include a camera, e.g. a line scan camera, by which the respective surface is recorded or optically scanned and evaluated for faulty or missing areas via a downstream evaluation device. Basically independent of, but also advantageously together with other design variants of the machine, but in particular in conjunction with an inspection device 403; 403.1; 403.2 provided on the substrate path, a device for marking defects 412 is provided in an advantageous further development, which can be formed for example by a printing device, e.g. an inkjet print head, or an insertion device, whereby the latter can, for example, insert or apply a material marking agent, e.g. a so-called marking flag or marking label, onto the carrier substrate web 006.

For all versions of the machine, in an advantageous embodiment, at least one substrate guide element 409 can be designed as a measuring roller 409 in the second substrate path 400, by means of which, for example, the web tension can be determined in order to use this, for example, to regulate the web tension, e.g. via the relative conveying speed of individual units 100; 100*; 600 or one or more web guide elements 202; 308; 401; 502, in particular those that are positively driven by a motor. Preferably, at least in the application stage 100; 100*, in particular downstream of the location of the last or only order and upstream of a possibly provided calendering unit 600, in particular upstream of a possibly taking place calendering, but particularly preferably both in the mentioned and in the substrate path section downstream of the calendering unit 600 provided in an advantageous embodiment, at least one substrate guide element 409 is designed as a measuring roller 409. Instead of this or in addition to this, a substrate guide element 507 structurally associated with the product winder 500 can be designed as a measuring roller 507 downstream of the calendering unit 600 in the substrate path.

In order to ensure an optimal substrate flow through the application stage 100; 100*, in an advantageous embodiment in the second substrate path 400, preferably immediately behind the application stage 100; 100*, but before a possibly provided Calendering unit 600, a substrate guide element 401 designed as a motor-driven pull roller 401 is provided. This can be comprised of a pull mechanism 411 which, for example, in addition to the pull roller 401 itself, has a drive means that drives the pull roller 401 - in particular independently of other pull rollers - and whose speed can be regulated and/or controlled, e.g. in the form of a servo drive motor, and/or pressure rollers that can be set on the pull roller 401 to increase the friction. In this case, the roller 401 or the drive means - depending on the web tension conditions and/or web tension requirements present upstream and downstream of the roller 401 - can in principle also be operated or operated as a generator or to inhibit the advance of the carrier substrate web 006, but is here operated or operable as a motor to build up and/or maintain a web tension on the upstream substrate path section, i.e. conveying the carrier substrate web 006 in the transport direction Ts or with an advance compared to, for example, the speed at an upstream pull roller 202; 301 and/or the peripheral speed of the last or only laminating roller 107; 107' or the pair of laminating rollers 107; 107'.

Alternatively or additionally to this, in a preferred embodiment, a web tension compensation and/or control device 406 (e.g. shown in Fig. 15 as an example for all embodiments) is provided in the second substrate path 400 downstream of the application stage 100, 100*, possibly between the application stage 100; 100* and a calendering unit 600 provided in an advantageous embodiment), with e.g. a dancer roller 407 - e.g. spring-loaded on a lever or a guide transversely to the substrate path or deflected by a force - by means of which, for example, fluctuations in the web tension can be compensated and/or the conveying speed of an upstream or downstream unit 100; 100*; 600 or one or more web guide elements 202; 308; 401; 502 - in particular via the deflection of the dancer roller 407. A machine shown as an example in Fig. 17, which is designed, for example, without a calendering unit 600 arranged downstream of the application stage 100, 100* in the substrate path, can - with the exception of the calendering unit 600 - optionally be provided with several or all of the devices and/or substrate guide elements 202; 203; 208; 307; 308; 401; 404; 409; 502; 503 shown in Fig. 15 or Fig. 16. For example, in the first substrate path section 300, an above-mentioned dancer roller 203 and/or at least one above-mentioned pull roller 308 and/or at least one above-mentioned web tension measuring roller 307 and/or an above-mentioned tempering station 306 is provided, and in the second substrate path section 400, an above-mentioned web tension measuring roller 409 and/or a cooling device 402, in particular with at least one cooling roller 402.1; 402.2, at least one above-mentioned pull roller 401 and/or at least one above-mentioned inspection device 403 for detecting errors and/or defects and/or a measuring station 408 for determining the product strand thickness and/or a device for marking defects 412 and/or at least one dancer roller 503 can be provided. Furthermore, in the second substrate path section 400, a - in Fig. 17 e.g. For example, a cleaning station 414 for removing loose particles and residues from the surface - which can also be advantageously provided as an example for the other embodiments - and/or a measuring device 413 for determining the basis weight FG - which can also be advantageously provided as an example in Fig. 18, for example.

The measuring device 413 for determining the basis weight FG is preferably based on an ultrasound-based measuring system 413.1, 413.2 or sensors 413.1, 413.2. Preferably, an ultrasound transmitter 413.1 is provided on the substrate path on a first strand side, through which the product strand 002 can be exposed to ultrasound waves, and on the same or preferably the other side of the substrate path, a receiver 413.2 is provided, through which reflected ultrasound waves can be detected in the case of the same side and transmitted ultrasound waves can be detected in the case of the other side. In both cases, a correlation with the basis weight and/or this representing a size and - with appropriate calibration - a value for the basis weight can be determined. In an advantageous embodiment, the sensor system 413.1; 413.2 is designed to determine a value for the basis weight across the width, i.e. across the substrate path, in the width direction over a length which, for example, corresponds to at least half the substrate strand width and, for example, is symmetrical to the center of the substrate path, continuously or at several points. For example, viewed across the transport direction - e.g. over a width which corresponds to at least half the strand width of the product strand 002 - a plurality of individual ultrasonic transmitters 413.1 and/or receivers 413.2 are provided next to one another, or an extended ultrasonic transmitter 413.1 and/or receiver 413.2 - designed with an appropriate width. In an advantageous development, a deflection roller around which the product strand 002 is at least slightly wrapped is provided in the substrate path before and after the measuring point acted upon by the ultrasonic transmitter 413.1. In order to obtain defined conditions, the distance in the substrate path between the measuring point and the respective deflection roller corresponds, for example, to at most twice the strand width, preferably at most the strand width.

The measuring device 413 or the measuring system 413.1; 413.2 it comprises can, as explained above, deliver the measured value determined for the basis weight as part of the above-mentioned control loop R'FG for controlling the basis weight FG by varying the ratio of the peripheral speeds V(102; 102'; 103; 103') or of the above-mentioned control loop Rpc for controlling the basis weight FG by varying the gap width.

For all the designs and variants of the machine mentioned here, an embodiment is particularly advantageous in which in the substrate path downstream of the application stage 100; 100* - in the case of a calendering unit 600; 600 provided in the substrate path downstream of a single or last calendering unit 600; 600 - before combining to form the product container 501 in the product holder, a Measuring station 408 is provided for determining the product strand thickness, in particular the total thickness (e.g. shown in Fig. 15, Fig. 16 and Fig. 17 as an example for all designs).

Instead of or in addition to the above-mentioned cooling device 402 in the second substrate path section 400, such or further cooling devices 402; 504 can also be provided in the substrate path section attributable to the product holder 500 or on its frame. Such a cooling device 504 can be formed, for example, by a substrate guide element 504 designed as a cooling roller 504. Alternatively, such a cooling device 504 - attributable to the second substrate path section 400 or structurally to the product holder 500 - can also be formed by one or more tempered cooling rollers 504.1; 504.2 partially wrapped one after the other.

In a further development, a sensor 508 for determining the temperature of the product 002, in particular of the product strand 002, can be arranged in the substrate path downstream of the calendering unit 600, which may be provided, for example downstream of the cooling device 504, which may be provided, but at the latest before the delivery, e.g. before winding in the product winder 500. The sensor 508, e.g. as a temperature sensor 508, is in particular designed as a contactless and/or radiation-based temperature sensor 311, and/or can be part of a control circuit for controlling the temperature with the cooling device 504, which may be provided.

In an advantageous embodiment, the product holder 500 is designed as a product winder 500, in particular in the form of a roll changer 500.

Preferably, the product winder 500 is qualified for a non-stop roll change and/or comprises an above-mentioned substrate guide element 502 designed as a motor-driven pull roller 502 and/or a substrate guide element 503 in the form of a - e.g. on a lever or a guide transversely to the substrate path - spring-loaded or by a force deflected - dancer roller 503.

In order to ensure optimal substrate travel between the calendering unit 600, if provided, and the winding on the product winder 500, in an advantageous embodiment, a substrate guide element 401; 502 designed as a motor-driven pull roller 401; 502 can be provided in the second substrate path 400 or in a substrate path section attributable to the product winder 500. This can be comprised of a pull mechanism 411; 506, which, for example, in addition to the pull roller 401; 502, has a drive means, e.g. in the form of a servo drive motor, which drives the pull roller 401; 502 - in particular independently of other pull rollers - and whose speed can be regulated and/or controlled, and/or pressure rollers which can be set on the pull roller 401; 502 to increase the friction.

In a particularly advantageous embodiment of a machine comprising, for example, a calendering unit 600, which is particularly advantageous for stable and trouble-free inline continuous operation, there is a first substrate path section located between the unwinding point from the substrate roll 201 in the substrate unwinder 200 and the entry into the only or first laminating gap 107; 107' of the application stage 100; 100*, as well as a second substrate path section located between the exit point of the carrier substrate web, which is then provided with the dry film 003; 003' on at least one side, from the only or last downstream laminating gap 107; 107' of the application stage 100; 100* and - for the embodiment with calendering unit 600; 600* - the entry into the calendering gap between the two calendering rollers 601; 602, at least one positively driven pull roller 202; 308; 401; 502 and/or at least one measuring roller 208; 307; 409 is provided for determining a web tension. In an advantageous further development for the design with calendering unit 600; 600*, a tension roller 202; 308; 401; 502 is also provided in a region between the point of exit of the carrier substrate web 006, which is provided with the dry film 003; 003' on at least one side, from the calendering gap and the point of winding onto the A positively driven pulling roller 502 and/or a measuring roller 409; 507 for determining a web tension is provided in the third substrate path section located on the product roll 501 in the product winder 500.

Preferably, a web tension control device (not shown here) is provided, which is connected on the input side to the measuring roller 208; 307; 409 provided in the first and the second above-mentioned substrate path section and on the output side to a drive control which controls the roller drives of the pull roller 202; 308; 401 provided in the first and the second above-mentioned substrate path section, and which in particular has data processing and/or electronic switching means which are set up to build up and/or maintain a predetermined web tension and/or a web tension difference predetermined for the two substrate path sections in each of the two substrate path sections by appropriately controlling the drive control of the drive of one or more of the pull rollers 202; 308; 401. In a further development, the web tension control device can additionally be connected on the input side to the measuring roller 409; 409 provided in the third above-mentioned substrate path section. 507 and on the output side with a drive control of the drive of the respective pull roller 502 or of a pull roller 502 provided in the third above-mentioned substrate path section and, for example, can also be controlled by this with regard to a predetermined web tension and/or a predetermined web tension difference to the upstream substrate path section.

In general, and in particular for a design of the machine without a calendering unit downstream of the application stage 100; 100*, the above-mentioned information on the pull rollers 202; 308; 401; 502 and measuring rollers 208; 307; 409, on the signal connections and on the web tension control device is applicable to a design with at least one measuring and/or at least one pull roller 208; 307; 202; 308 in the first substrate path section between the unwinding and the point of the first application through the Application stage 100; 100* and at least one measuring and/or at least one pulling roller 409; 507; 401; 502 in a substrate path section between leaving the only or last point of the dry film application through the application stage 100; 100* and winding up in the roll winder 500.

By means of an above-mentioned dancer roller 203; 407; 503 and a control circuit comprising this - and for example integrated into an above-mentioned web tension control device - fluctuations in the web tension can be compensated for or regulated and/or a conveying speed of an upstream or downstream unit 100; 100*; 600 or one or more particularly motor-driven web guide elements 202; 308; 401; 502, such as the drive of an upstream substrate unwinder 200 or downstream substrate winder 500 or an upstream or downstream pull roller 202; 308; 401; 502, can be regulated, in particular via the deflection of the dancer roller 407. It is - e.g. B. on a guide or on a lever - spring-loaded transversely to the substrate path, in particular against the direction of action of the web tension of the substrate web 006 (or the product strand 002) looping around the roller with a force pneumatically or elastically pretensioned.

An above-mentioned pulling roller 203; 308; 401; 502 comprises, for example, a drive motor, in particular a servo motor, whose speed can be regulated and/or controlled, and/or works together with one or more pressure elements, e.g. pressure rollers, for example to improve the conveying behavior and/or is, depending on the position in the substrate path, operable as a motor - for example to generate or maintain an upstream web tension or - for example to generate or maintain a downstream web tension - as a generator, i.e. with a braking effect, and/or is included in a control circuit that regulates the web tension - and is integrated, for example, in an above-mentioned web tension control device - e.g. as an actuator. As an alternative to the design of the machine with a product holder 500 designed as a roll winder 500, in a particularly advantageous design, a cross-cutting device can be provided in the second substrate path 400 or at the entrance to the product holder 500, by means of which a product strand 002 produced in the machine can already be cut crosswise into product sections 001. The product holder 500 is designed, for example, as a stack delivery device, in particular as a multiple stack delivery device that lays out several stacks one behind the other.

In a machine and/or device 100; 100* described above, for example, a web-shaped carrier substrate 006 is continuously and preferably provided on both sides with a dry film 003; 003' of a width smaller than the carrier substrate width, so that an uncoated edge of the carrier substrate remains on both sides.

List of reference symbols

001 product, end product, product section, electrode unit, electrode

002 Product, intermediate product, product strand, electrode strand

003 Active material layer, material layer, dry film, powder composite film (especially solvent-free)

003‘ Active material layer, material layer, dry film, powder composite film (especially solvent-free)

004 Material, powdery, powder mixture (especially dry)

004‘ Material, powdery, powder mixture (especially dry)

005 -

006 Carrier substrate, carrier substrate sheet, current collector substrate, current collector foil, sheet-like

007 Bonding agent, primer, binder, adhesive 007‘ Bonding agent, primer, binder, adhesive 008 Part, material strip, edge strip

100 Coating device, coating device, application stage, aggregate, laminating aggregate, laminating unit

100* Coating device, coating device, application stage, aggregate, laminating aggregate, laminating unit

101 Commissioned work, first

10T applicator, second

102 Roller, first, dosing roller

102‘ roller, first, dosing roller

103 Roller, second, laminating roller, counter pressure roller

103‘ roller, second, laminating roller, counter pressure roller

104 gap, first, film forming gap, metering gap, roller gap, nip

104' gap, first, film forming gap, metering gap, roll gap, nip - Roller, counter-pressure roller ' Roller, counter-pressure roller Gap, second, application gap, laminating gap ' Gap, second, application gap, laminating gap - Actuator, actuating means, position-based ' Actuator, actuating means, position-based - Actuator, actuating means, force-based ' Actuator, actuating means, force-based Actuating mechanism, bearing mechanism, linear bearing' Actuating mechanism, bearing mechanism, linear bearing Actuating mechanism, bearing mechanism, three-ring bearing' Actuating mechanism, bearing mechanism, three-ring bearing Removal device, squeegee, cleaning squeegee' Removal device, squeegee, cleaning squeegee - Removal device, squeegee, side edge squeegee' Removal device, squeegee, side edge squeegee Collecting device, collecting tray ' Collecting device, collecting tray Roller, further, calender roller ' Roller, further, calender roller Stop means, wedge stop - Substrate guide element, guide roller, deflection roller Carrier, side parts (base frame) ' Carrier, side parts (base frame) Extraction ' Extraction limit, side plate - filling and/or supply area Material removal ' Material removal Frame (application stage) .1 Partial frame, first .2 Partial frame, second .3 Partial frame, further or third .4 Partial frame, fourth Removal device, squeegee, cleaning squeegee ' Removal device, squeegee, cleaning squeegee - Frame wall .1 Frame wall .2 Frame wall .3 Frame wall .4 Frame wall Drive means, path or position based, motor, position controllable and/or adjustable' Drive means, path or position based, motor, position controllable and/or adjustable, Drive means, force based, cylinder-piston system, motor, torque controllable and/or adjustable ' Drive means, force based, cylinder-piston system, motor, torque controllable and/or adjustable Tempering fluid line - crossbeam, base plate Traverse, cross member

guide section, rail section, guide, rail

Support base

Adjusting device, pulling device, tensioning device

Piston rods

Pressure and/or tension plate

Pressure and/or tension plate

Frame construction, base plate

Actuating and/or driving means, actuator

Bearing block

Drive means, rotary, drive motor, speed-adjustable or controllable,

Servo motor

Drive means, rotary, drive motor, speed-adjustable or controllable,

Servo motor

Bearings, radial bearings

Bearing, rolling element, sliding element,

Storage area

Actuator, electric, hydraulic

Control and/or regulating device, control device

Sensors (gap width)

Sensor

Sensor

Pressure medium line

Pressure medium line

Valve

Evaluation tools Part, roll neck (102)

Roll pins (103)

Actuator, multi-way valve (switchable), pump (reversible)

Adjusting device, pulling device, tensioning device

Cylinder

Pistons

Chamber

Chamber

Controller

Sensors, measuring device (layer thickness)

Sensor

Control and/or regulating means, drive controllers

Controller

Actuator, electromagnet

Pressure sensor

Substrate feed, substrate unwinder, roll changer

Roll, substrate roll

Substrate guide element, roller, pull roller, positively driven

Substrate guide element, dancer roller

Web edge control

Gluing device, gluing table

Traction mechanism, intake mechanism

Substrate guide element, measuring roller, web tension measuring roller

Substrate path section, conveyor section, first, upstream, feed side Substrate guide element, roller, guide roller, deflection roller

Pretreatment station, cleaning station, deionization station

Measuring station (carrier substrate thickness)

Pretreatment station, application station

Pretreatment station, thermal, tempering station, infrared radiation source

Substrate guide element, measuring roller, web tension measuring roller

Substrate guide element, roller, pull roller, positively driven

Traction mechanism

Sensor, temperature sensor

Substrate path section, conveyor section, second, downstream, discharge side

Substrate guide element, roller, pull roller, positively driven

Cooling device * Cooling device (alternative or additional)

Inspection facility

Substrate guide element, roller, guide roller, deflection roller

Web tension compensation and/or control device

Dancer roller

Measuring station (product strand thickness)

Substrate guide element, measuring roller, web tension measuring roller

Traction mechanism

Defect marking

Product intake, product winder, roll changer

Product container, roll, product roll 502 Substrate guide element, pull roller, positively driven

503 Dancer roller

504 Cooling device, substrate guide element, roller, cooling roller

504.1 Cooling roller

504.2 Cooling roller

505 -

506 Traction mechanism

507 Substrate guide element, measuring roller, web tension measuring roller

508 Sensor, temperature sensor

600 Calendering unit, unit, calendering unit

600* Calendering unit (alternative or additional), unit, calendering unit

601 Roll, calender roll, first, heated

601* Roll, calender roll, first (alternative or additional)

602 Roll, calender roll, second, heated

602* Roll, calender roll, second (alternative or additional)

603 Frame (calendering unit)

700 Device for feeding powdered material, powder feeding device

700' Device for feeding powdery material, powder feeding device b Width b151 Support width d Thickness, layer thickness b003 Width (003; 003') b006 Width (006) b008 Width (008) d003 Thickness, layer thickness (003) d003' Thickness, layer thickness (003') d006 Strength (006) d008 Strength, layer thickness (008)

G Level

K circular arc a angle, angle of inclination

P Pressure fluid source

R Reservoir

Rs radius (swivel movement) s1 switching state, holding switching state s2 switching state, passing state s3 switching state, passing state s4 switching state, basic switching state

R102 Rotation axis

R102‘ rotation axis

R103 Rotation axis

R103‘ rotation axis

R106 Rotation axis

R106‘ rotation axis

S swivel axis

Ts transport direction (product strand 002, carrier substrate 006)

Claims

Expectations 1. Device (100; 100*) for coating a carrier substrate (006) with a powdery material (004) with at least one first application unit (101; 10T) which comprises a first roller (102; 102') and a second roller (103; 103') which form a first roller gap (104; 104') in the nip between their lateral surfaces, which serves to form a film, through which powdery material (004) can be conveyed in order to form a first dry film (003), and with a roller (103'; 106) which acts as a counter-pressure roller (103'; 106) and which forms a second roller gap (107) with the second roller (103) or with a further roller which follows the second roller (103) directly or indirectly downstream of the second roller (103) in the direction of the material flow, wherein a a substrate path is provided which leads to the second roller gap (107), on which a carrier substrate web (106) to be coated can be guided during operation and can be acted upon on a first side by the dry film (106) formed in the first roller gap (104), characterized in that for setting the roller gap (104; 107) between two adjacent rollers (102; 103; 102'; 103') arranged so as to be movable relative to one another, at least one pulling device (141; 165) with a drive means (132; 133) is provided on each side of the frame, by means of which the two rollers (102; 103; 102'; 103') can be moved towards one another or tensioned in the setting direction, and can be moved away from one another again or at least relaxed again. 2. Device according to claim 1, characterized in that the adjusting device (141; 165) comprising the drive means (132; 133) acts with its two active ends on the first and the second roller (102; 103; 102';103') in such a way that, in order to adjust the gap (104; 104') between the first and second rollers (102; 103; 102';103'), it applies an adjusting force directed towards one another. 3. Device according to claim 1 or 2, characterized in that the drive means (132; 133) is designed as a cylinder-piston system (132; 133) which can be acted upon by pressurized fluid. 4. Device according to claim 3, characterized in that the cylinder-piston system (132; 133) is or can be supplied with pressure fluid via an actuating means (164; 164*) fluidically connected to the cylinder-piston system (132; 133) from a pressure fluid source (P) connected to the actuating means (164; 164*) on the input side, which provides and/or can provide pressure fluid with a pressure of at least 100 bar or 10 MPa. 5. Device according to claim 3 or 4, characterized in that means for emergency shutdown are provided, which comprise a pressure sensor (177) which is provided in the first line path which supplies the cylinder-piston system (132; 133) with pressure fluid when the one or first roller (102; 103; 102'; 103') is set against the adjacent other or second roller (102; 103; 102'; 103'), a switching logic implemented in control means and in signal connection with the pressure sensor, which, as a result of a pressure in the first line path rising above a threshold value when the one roller (102; 103; 102'; 103') is set against the adjacent other roller (102; 103; 102'; 103'), causes the pressure medium supply of the cylinder-piston system to be depressurized (132; 133) or a switchover to an operating mode causing a shutdown. 6. Device according to claim 1, 2, 3, 4 or 5, characterized in that the first gap (104) between the first and second rollers (102; 103; 102'; 103') can be adjusted by the adjusting device (141; 165) in a position-based manner, i.e. to a constant and/or defined gap width (b1904). 7. Device according to claim 6, characterized in that the adjusting device (141; 165) for the position-based setting of the first gap (104; 104') comprises a force-based operated or operable actuator (111; 11T) with a cylinder-piston system (133) that can be acted upon with pressurized fluid as drive means (133) and an actuating mechanism (112; 112';113;113'), in the actuating path of which a positionable stop (119) can be introduced for position limitation. 8. Device according to claim 6, characterized in that the adjusting device (141; 165) for the position-based setting of the first gap (104; 104') comprises as drive means (132) a drive means (132) which can be regulated with respect to a position of its output-side output means and/or a hydraulic drive (132, 164, 171) which can be regulated or regulated with respect to a position or position and which has a cylinder-piston system (132) which can be pressurized with pressure fluid. 9. Device according to claim 6 or 8, characterized in that the adjusting device (141) for adjusting and/or keeping constant the gap width (b104) of the first gap (104) has a double-acting hydraulic cylinder-piston system (132) which is controllable or regulated via a directional control valve (164). 10. Device according to claim 9, characterized in that the directional control valve (164) as an actuator together with the cylinder-piston system (132) as an actuator, with a sensor system (157) for detecting a gap width (b104) or a variable correlating with and/or representing the gap width (b104) and with a controller (171) controlling the actuator on the basis of a result provided by the sensor system (157) are components of a control loop (Rb), by means of which the gap width (b104) can be or is regulated to assume and/or maintain a target gap width (b104 _SO ii) or a target variable correspondingly correlated therewith and/or representing this. 11. Device according to claim 1, 2, 3, 4, 5, 6, 7, 8, 9 or 10, characterized in that that the rollers (102; 103; 106) forming the gap (104; 107) between themselves are each mounted on both sides in frame walls (131.1; 131.2; 131.3; 131.4) of mutually different sub-frames (128.1; 128.2; 128.3; 128.4) and that the adjusting devices (141; 165) each act on the frame walls (131.1; 131.2, 131.3; 131.4) of the two rollers (102; 103; 106) forming the relevant gap (104, 107) between themselves. 12. Device according to claim 11, characterized in that the sub-frame (128.1) carrying the second or further roller (103) of the first application unit (101) is mounted in a spatially or frame-fixed manner and the sub-frames (128.3; 128.2) carrying the first roller (102) and the counter-pressure roller (106) are adjustably mounted at a distance from the second or further roller (103) which is arranged in a spatially or frame-fixed manner. 13. Device according to claim 11 or 12, characterized in that the adjustably mounted sub-frames (128.3; 128.2) are movably mounted on linear guides (112; 112'). 14. Device according to claim 1, 2, 3, 4, 5, 6, 7, 8, 9, 10, 11, 12 or 13, characterized in that the roller (103') acting as a counter-pressure roller (103') is simultaneously designed as a laminating roller (103') part of a second application unit (10T) located on the other side of the substrate path, which comprises a first roller (102') of the second application unit (10T) which, with the laminating roller (103') acting as a counter-pressure roller (103') or with a further roller of the second application unit (10T) located therebetween, forms a first roller gap (104; 104') of the second application unit (10T), through which powdery material (004') can be conveyed in order to form a second dry film (003), which in the second roller gap (107) over the laminating roller (103') of the second application unit (10T) onto the second side of the carrier substrate (106) which is guided during operation via the transport path through the second gap (107) can be applied. 15. Device according to claim 14, characterized in that between the two rollers (102'; 103') forming the first gap (104') of the second applicator (101'), at least one actuating device (141; 165) operable and/or designed as a pulling device (141; 165) with a drive means (132; 133) acts indirectly or directly on both sides, by means of which the two rollers (102; 103; 106) involved in the gap (104; 107) in question can be moved towards one another and/or can be subjected to a force directed towards one another. 16. Device according to claim 15, characterized in that the first gap (104') between the first and second rollers (102; 103; 102'; 103') of the second applicator (101') can be adjusted by the adjusting device (141; 165) in a position-based manner, i.e. to a constant and/or defined gap width (b1904). 17. Device according to claim 16, characterized by the adjusting device (141; 165) according to claim 7 or claim 8. 18. Device according to claim 15, 16 or 17, characterized in that the rollers (102'; 103') forming the first gap (104') of the second application unit (101') between themselves are each mounted on both sides in frame walls (131.1; 131.2, 131.3; 131.4) of two mutually different sub-frames (128.2; 128.4) and that the adjusting devices (141; 165) each act on the frame walls (131.2; 131.4) of the two rollers (102'; 103') forming the relevant gap (104') between themselves. 19. Device according to claim 18, characterized in that the sub-frame (128.4) carrying the first roller (102') of the second applicator (10T) is mounted at a distance from the second roller (103') of the second applicator (103') that can be varied. 20. Device according to claim 1, 2, 3, 4, 5, 6, 7, 8, 9, 10, 11, 12, 13, 14, 15, 16, 17, 18 or 19, characterized in that a linear adjustment path is provided for the adjustment in the adjustment direction and/or a bearing mechanism (112; 112'; 113; 113') formed by linear bearings (112; 112'; 113; 113') is provided. 21. Device according to claim 1, 2, 3, 4, 5, 6, 7, 8, 9, 10, 11, 12, 13, 14, 15, 16, 17, 18, 19 or 20, characterized in that the second gap (107; 107') between the counter-pressure roller (106; 106'; 103'; 103) and the second or the intermediate further roller (103; 103') of the first application unit (101; 101 ') can be adjusted by the adjusting devices (141; 165) acting between these two rollers (103; 103'; 106) on the basis of a force-based actuator (111; 11 T), i.e. can be adjusted to a constant and/or defined adjusting or line force. 22. Device according to claim 21, characterized in that the adjusting device (141; 165) for the force-based adjustment of the second gap (107') comprises a cylinder-piston system (133) adjustable in terms of pressure as drive means (133). 23. Device according to claim 1, 2, 3, 4, 5, 6, 7, 8, 9, 10, 11, 12, 13, 14, 15, 16, 17, 18, 19, 20, 21 or 22, characterized in that the first roller (102; 102') of a same application unit (101; 101') or a sub-frame (128.1; 128.2; 128.3; 128.4) carrying the first roller (102; 102') is arranged or can be pivoted relative to the second roller (103; 103') about a pivot axis (S) which is perpendicular to the axis of rotation (R102; R103; R102; R103') of the first and/or the second roller (102; 103; 102'; 103') and/or intersects the rotation axis (R102; R103; R102; R103') of the first roller (102; 103; 102'; 103') and/or the second roller (102; 103; 102'; 103').