EP2582457A1

EP2582457A1 - Roller press having torque balance

Info

Publication number: EP2582457A1
Application number: EP11719234.4A
Authority: EP
Inventors: Meinhard Frangenberg
Original assignee: KHD Humboldt Wedag AG
Current assignee: KHD Humboldt Wedag AG
Priority date: 2010-06-18
Filing date: 2011-05-06
Publication date: 2013-04-24
Anticipated expiration: 2031-05-06
Also published as: DE102010024231A1; US9108377B2; BR112012030316A2; RU2013102117A; RU2560561C2; DE102010024231B4; US20130087054A1; DK2582457T3; WO2011157483A1; AU2011267295B2; AU2011267295A1; CN102947003A; CN102947003B; EP2582457B1

Abstract

The invention relates to a roller press (100) for the pressure treatment or compaction of granular material, having at least two rolls (110, 120) formed as freely rotating rolls, in each case rotatably mounted in a machine frame (171) by a shaft (111, 112, 121, 122), driven in opposite directions and separated from one another by a roll gap (115), wherein the shafts (111, 112, 121, 122) of the rolls (110, 120) are accommodated in bearing housings (130, 140, 100, 160) movably mounted in the machine frame (171) and wherein in each case two bearing housings (130, 140, 150, 160) arranged on one side of the rolls (110, 120) and belonging to different rolls (110, 120) are connected to each other via at least one pressure cylinder (210, 210', 220, 220', 230, 230', 240, 240'). According to the invention, the connection between the bearing housings (130, 140, 150, 160) in each case has at least one torque balance (250, 250', 260, 260'). In this way, the structure of a roller press having roller centering is simplified as compared with the prior art and can be produced more cost-effectively.

Description

Roller press with moment scale

The invention relates to a roller press for pressure treatment or

Kompaktierung granular Guts comprising at least two rotatably mounted respectively via a shaft in a machine frame and driven in opposite directions and separated by a nip, designed as Loswalzen rolls, the waves of the rollers accommodated in the machine frame movably arranged bearing housings and wherein each two on one side of the Roll arranged bearing housing of different rolls are connected to each other via at least one pressure cylinder and a method for centering a nip of a roller press.

To center the nip in roller presses for pressure treatment or compacting granular Guts the rollers of the roller press are usually held by large hydraulic drives in their desired position, so on the one hand, the pressure in the nip between the rollers is maintained and on the other hand, by the centering parallelism the limitation of the nip maintained by the surface of the rollers. With this centering, the hydraulic drives operate with high force both to maintain the parallelism of the nip and to maintain the pressure in the nip. For this purpose, a first roller is fixedly mounted as a fixed roller in the machine frame in bearings in the simplest case, which in turn are secured by bearing housings in a machine frame to consoles. In contrast, a second roller is stored as a Loswalze in camps, the in between two consoles of the machine frame bewegl I arranged Lagergehäu-sen are arranged. The hydraulic ikantriebe for relative positioning of the Loswalze against the hard roller and to maintain the pressure in the nip exert high forces on the machine frame as an abutment, for which it is necessary to design the machine frame accordingly stable.

In roller presses with rollers with a weight of up to 50 t a correspondingly large dimensions of the machine frame is necessary so that the logistics of the machine frame and its handling in a necessary and regular change of the rollers is complicated and only with correspondingly large-sized cranes and removal aids possible ,

In order to reduce the dimensions of the necessary dimensioning of the machine frame, DE1 02005006090A1 proposes to form both rollers of the roller press as a loose roller, these two loose rollers being connected to one another via the bearings and the bearing housings and via hydraulic drives. The rollers, the bearings, the bearing housings and the hydraulic drives form a closed force system, which relieves the machine frame and thus can be dimensioned to a lesser extent. This arrangement has proven itself in practice. Since in this roller press the closed power system is designed to be displaceable relative to the machine frame, it is necessary to center the closed power system during operation, so that the nip does not migrate during operation of the roller press. This centering is achieved by the use of a correspondingly dimensioned hydraulics. It is necessary to control the hydraulics by control circuits, which are against the forces of the moving system Rollers, hydraulics and bearings such as bearing housings centered on the nip.

In further development of this roller press is proposed in DE1 02007059072 to use a hydraulic double cylinder, which is attached to the machine frame. In this hydraulic double cylinder, two adjacent hydraulic chambers operate and are supported against each other. Despite the forces acting on the hydraulic system, the force of the hydraulic cylinder acting on the nip is not transmitted to the machine frame. However, in order to center the nip, it is necessary to provide the hydraulic pressures necessary to generate the pressure in the nip by multi-quadrant operation.

The object of the invention is therefore to develop the roller presses so that while maintaining the self-contained and largely separate from the machine frame power system, the centering is made easier and less expensive to manufacture.

The object of the invention underlying task is solved in that the connection of the bearing housing in each case has at least one torque balance. Further advantageous embodiments of the invention are specified in the subclaims. The process object of the invention is achieved by the use of the torque balance according to claim 1 0.

A torque balance is understood to mean a rocker-like or pendulum-like suspension, on which pairs counteracting, first and second hydraulic cylinders engage opposite arms of the torque balance. These counteracting hydraulic cylinders in each case alone cause the tilting of the torque balance in the direction of the related Hydraulikzyl Indian. This change in position of the torque balance on the opposite side of the first hydraulic cylinder has the effect that the opposite second Hydraulikzyl inder is more heavily loaded and therefore the control circuit of the now more heavily loaded second hydraulic cylinder builds up a higher pressure and counteracts the first Hydraulikzyl indians until the torque scale is again positioned in its equilibrium position. The first and the second hydraulic cylinder have in the roller press according to the invention a rotatably configured clutch, so that the first and the second hydraulic cylinder can also attack at an angle to the arms of the torque balance. By this rotatable coupling, it is possible that the rollers of the roller press can not assume mutually parallel positions, which is always the case when a larger grain outside the center of the nip passes through the nip or when the nip is loaded unevenly with ground material , The effect of the torque balance is that a rolling centering is enforced via a simple, movably mounted, mechanical element, provided that the hydraulic cylinders working to generate the pressure in the nip work against each other. Due to the torque balance, it is also possible, if necessary, to compensate the force of two unbalanced and mutually working hydraulic cylinders. In this case, hydraulic controls for operating the various cylinders in Mehrquadrantenbetrieb not necessary because the compensation is done mechanically.

The torque scale can be constructed asymmetrically or symmetrically. The symmetry of the symmetry mirrors the symmetry of the

Torque scale, especially the unequal length of the boom of the Torque scale the different size and rated load capacity of the opposite lying hydraulic cylinder again. However, a symmetrical configuration of the torque balance, which is arranged approximately centrally between the bearing housings, is preferred. At the same length boom of the torque scale grip in this Fal l two identical hydraulic cylinder or at least two hydraulic cylinders with the same nominal capacity and the same characteristic.

The torque balance is preferably rotatably mounted about a vertical axis of rotation which lies in a plane which is spanned by the center line of the nip and the vertical. Due to the vertical axis of rotation, the torque scale rotates in a horizontal plane and thus allows a skewing of the rollers to each other, the torque balance on this misalignment has a balancing effect, so that the rollers experience a misalignment of a force that causes after return of the roller press in equilibrium position, the rollers of the roller press are again parallel to each other.

In a preferred embodiment of the invention, the torque balance on a rocker with two arms, via which the two bearing housing of the roller press are connected to each other, and the torque scale has a rotatably mounted pendulum, via which the rocker is pivotally mounted with the two arms about the axis of rotation , Due to the pendulum, the rocker of the torque balance with the two arms rotates about a pivot point outside the power line between the two hydraulic cylinders, which on the opposite arms of the

Pull moment scale. This ensures that only a small part of the force of the hydraulic cylinder is transmitted to the axis of rotation, because the torque scale tilts when uneven force of both counteracting Hydraulikzyl indians to one side or the other, so that the force of the hydraulic cylinder, which have a different direction due to the misalignment, is always geradl inig each other and not transmitted to the machine frame.

Although the force system of rollers, shafts, bearings, bearing housings, hydraulic cylinders and torque balance is closed and therefore does not transmit the force to generate the pressure in the nip or only on the extent of a small directional component on the machine frame, the axis of rotation is still firmly connected to the machine frame. Although the torque scale is supported on the axis of rotation, but the high forces of the hydraulic cylinders, which in each case in pairs and oppositely arranged liegend attack on the torque scale, are redirected by the torque scale, so that the force or at least the largest proportion always in the direction of Hydraulic cylinder acts.

The hydraulic cylinders are loaded in the roller press according to the invention only to train. As a result, the torque balance has the effect that the distance between the hydraulic cylinders is minimized to each other and thus aligns the torque balance. This enhances the centering effect on the nip.

In a preferred embodiment of the invention, two bearings of two different rollers are formed on one side of the roller press as a fixed bearing and two bearings on the opposite side of the roller press are designed as a floating bearing. The floating bearings allow an axial movement of the shaft in the bearing, so that the change in length of the roller is ausgegl by temperature ausgeg and also the distance of the bearing to each other in an inclined position of the rollers. Regardless of the degrees of freedom that make the floating bearings available, the bearing housings all bearings mounted on a slide in the machine frame. Thus, the bearings can move in a direction perpendicular to the center line of the nip and the floating bearings provide a degree of freedom in the axial direction, ie parallel to the center line of the nip available.

The invention will be explained in more detail with reference to the following figures.

It shows:

1 is a sketched view of a roller press according to the invention in the state of equilibrium from above with partially hidden machine frame parts,

FIG. 2 shows the same arrangement as in FIG. 2 but in the deflected state,

Figure 3 is a perspective view of selected elements of a roller press according to the invention.

FIG. 1 shows a roller press 1 00 according to the invention in a view from above (parts of a machine frame are hidden for a better illustration of the individual parts). In this roller press 1 00, a first roller 1 1 0 by means of the shafts 1 1 1 and 1 1 2 rotatably mounted in the roller press 1 00. To form a nip to be centered 1 1 5, a second, adjacent roll 1 20, which in turn is rotatably supported by shafts 1 21 and 1 22 in the roller press, arranged in the roller press 1 00. In operation, the roller press 1 00, the two rollers 1 1 0 and 1 20 are driven in opposite directions, so that the on the nip 1 1 5 abandoned from above ground material is drawn into the nip 1 1 5. The bearings of the rollers 110 and 120 in the roller press 100 is done via fixed bearings, which are arranged in the fixed bearing housings 130 and 140 and via floating bearings, which are arranged in the floating bearing housings 150 and 160, in the roller press 100 the bearing housings 130 and 140 in the axial Direction of the rollers 110 and 120 are opposite. These bearing housings 130, 140, 150 and 160 are in turn arranged on slide rails 170 and 180, on which the bearing housings 130, 140, 150 and 160 together with the bearings received therein and in turn received waves 111, 112, 121 and 122 in the machine frame 171st , which is here only interrupted and partially illustrated, horizontal compensating movements perpendicular to the axis of the rollers 110 and 120 can perform. To a lesser extent, the bearing housings 130, 140, 150 and 160 can also perform rotational movements about a vertical axis of the bearing housings 130, 140, 150 and 160.

Fixed bearing housing 130 and 140 and floating bearing housing 150 and 160 form each on one axial side of the rollers 110 and 120 together with the visible in this view, each upper torque scale 250 respectively torque scale 260, not visible in this view, lower torque scales 250 'and 260' and the respectively associated, loaded on train, overhead hydraulic cylinders 210, 220, 230 and 240 and not visible, underlying hydraulic cylinders 210 ', 220', 230 'and 240' a closed force system. In this force system, the respective upper torque scales 250 and 260 and the lower torque balances 250 ', 260', which are not visible in this view, are fastened in a rotationally movable manner via rotary hangers 310 and 320 on the machine frame 171.

During operation of the roller press 100, it happens that the rollers 110 and / or 120 must perform compensatory movements for the passage of particles which may not be comminuted, for example metal pieces which have undesirably entered the material to be ground or for the passage of non-uniformly distributed material to be ground to the length of the nip 1 1 5. During this balancing movement, the roller press is temporarily in an imbalance condition. This state is shown in the following figure, Figure 2.

FIG. 2 shows the roller press 1 00 in an instant of an exaggerated compensating movement. Both roller 1 1 0 and roller 1 20 have performed a slight rotational movement about a vertical axis, whereby the nip 1 1 5 has a trapezoidal profile, with a larger opening in Figure 2 on the lower side of the nip 1 1 5. This compensating movement is only possible me if the bearing housings 1 30, 140, 1 50 and 1 60 on the slide rail 1 70 and 1 80 can dodge in the horizontal direction and if the floating bearings in the floating bearing housings 1 50 and 1 60 an axial movement of the shafts 1 1 2 and 1 22 allow.

Due to the inclination of the rollers 1 1 0 and 1 20, the bearing together with the bearing housings 1 30, 140, 1 50 and 160 are inevitably moved out of its equilibrium position. Since the bearing housings 1 30 and 140 and 1 50 and 1 60 in pairs via the torque scales 250 and 260 are connected, and since the torque scales 250 and 260 by Drehangeln 310 and 320 via the pendulum 290 and 300 about a vertical axis rotatable in the machine frame 1 71st are stored, the force is transmitted by the compensating movement of a roller 1 10, 120 to the respective other roller 1 20, 1 1 0. The upper torque scale 260 shown in FIG. 2 is rotated in a clockwise direction, while in the state of the roller press 1 00 shown here, the lower torque balance 250 is slight twisted counterclockwise. In this state, the roller press 1 00, the distance between the paired bearing housing 1 30 and 140 and / or bearing housing 1 50 and 1 60 is greater than in the equilibrium state, which is shown in Figure 1. Due to the tensile force of the two hydraulic cylinders 21 0 and 220 and / or the hydraulic cylinder 230 and 240, the roller press 1 00 is inclined to return to the equilibrium state shown in Figure 1, wherein the trapezoidal nip shown in Figure 2 again rectangular profile and is aligned in the machine frame 1 71 centered. The Drehangeln 31 0 and 320 need to center the nip 1 1 5 does not absorb the forces of train loaded hydraulic cylinders 21 0, 220, 230 and 240, however causes the drehbewegl Ie suspension of the torque scale 250 and / or 260, that an aligned , Equilibrium position of the rollers 1 10 and 1 20 only in a horizontal position mögl I is, whereby the nip 1 1 5 is centered.

An advantage of the use of the torque balance is a simplification of the hydraulic iksteuerung, which can take place in each case in an extreme case without compensation with each other, because the torque balance is capable of minor differences in the control curve of the hydraulic ik systems offset each other. Furthermore, can be dispensed with the use of multi-chamber Hydraulikzyl indi. The roll press 1 00 presented here is robust, offers automatic centering and can be equipped with a lightweight machine frame thanks to the closed power system.

Finally, FIG. 3 shows a perspective view of a roller press 1 00 according to the invention, in which selected elements for masking the invention are hidden. I'm the per- can be seen from the perspective view that a roller 1 20 is received via a shaft 1 22 in a floating bearing housing 160. At this point, the shaft protrudes 1 22 out of the floating bearing housing 1 60 and there is the drive side of the shaft 122. This floating bearing housing 1 60 is like the floating bearing housing 150 of the second, here hidden roller 1 1 0 added within a frame of several elements, in this embodiment, the roller press 1 00 of four loaded on train hydraulic ikzylindern 230, 230 ', 240 and 240', from which the floating bearing housing 1 50 and 1 60 encompassing blocks 1 55 and 1 65 and the torque scales 260 and 260 ', wherein this frame forms a closed force system, which is designed to absorb the force resulting from the pressure in the nip 1 1 5. In addition to the inclusion in the frame of various elements l here exposed blind bearing housing 1 50 and 1 60 on a slide rail 1 80, which is not part of the above-described frame of several elements, but part of a machine frame 1 71 not begotten here. The slide 1 80 thus takes only the weight of the rollers 1 1 0 and 1 20 together with their waves 1 1 1, 1 1 2, 1 21 and 1 22 and the floating bearing housing 1 50, 1 60. The torque scales 260 and 260 'consist of two powerful rockers 280, 280' in which the hydraulic cylinders 230, 230 ', 240 and 240' engage. Between the two rockers 280, 280 ', a pendulum 300, 300' is added, via which the

Torque scale 260, 260 'can rotate about a pin as Drehangel 320. This pin is fixedly mounted on a part of the machine frame 1 71 and takes in comparison to the tensile force of the hydraulic cylinders 230, 230 ', 240 and 240' on slightly dimensioned forces. LIST OF REFERENCE NUMBERS

Roller press 220 hydraulic cylinders

Roller 220 'hydraulic cylinder

Shaft 230 hydraulic cylinder

Shaft 230 'hydraulic cylinder

Nip 240 hydraulic cylinder

Roller 240 'hydraulic cylinder

Wave 250 torque scale

Shaft 250 'torque scale

Fixed bearing housing 260 Moment scale

Fixed bearing housing 270 Rocker

Floating bearing housing 270 'rocker

Block 280 seesaw

Floating bearing housing 280 'rocker

Block 290 pendulum

Slide rail 290 'pendulum

Machine frame 300 pendulum

Slide rail 300 'pendulum

Hydraulic cylinder 310 rotary hanger

Hydraulic cylinder 320 rotary hanger

Claims

PATEN TA NSPR CHE

1. Roll press (100) for pressure treatment or compaction of granular material comprising:

at least two rollers (110, 120) rotatably mounted in each case via a shaft (111, 112, 121, 122) in a machine frame (171) and driven in opposite directions and separated by a nip (115) and designed as loose rollers;

wherein the shafts (111, 112, 121, 122) of the rollers (110, 120) are received in bearing housings (130, 140, 150, 160) movably arranged in the machine frame (171) and

wherein in each case two bearing housings (130, 140, 150, 160) of different rollers (110, 120) arranged on one side of the rollers (110, 120) are connected via at least one pressure cylinder (210, 210 ', 220, 220', 230, 230 '). , 240, 240 ') are interconnected,

characterized in that

the connection of the bearing housings (130, 140, 150, 160) in each case has at least one moment scale (250, 250 ', 260, 260').

2. Roller press according to claim 1,

characterized in that

the at least one torque scale (250, 250 ', 260, 260') is arranged approximately centrally between the bearing housings (1 30, 140, 1 50, 160).

3. Roller press according to claim 1 or 2,

characterized in that

in that each of the at least one moment scales (250, 250 ', 260, 260') is rotatably mounted about a vertical axis of rotation (31 0, 320) lying in a plane passing through the center line of the nip (1 1 5) and the Vertical is stretched.

4. roller press, according to claim 3,

characterized in that

each of the at least one torque scale (250, 250 ', 260, 260') has a rocker (270, 270 ', 280, 280'), via which the two bearing housings (1 30, 140, 1 50, 160) are interconnected , and a rotatably mounted pendulum (290, 290 ', 300, 300'), via which the rocker (270, 270 ', 280, 280') about the rotational axis (31 0, 320) is pivotally mounted.

5. Roller press, according to one of claims 3 to 4,

characterized in that the axis of rotation (31 0, 320) is fixedly connected to the machine frame (1 71).

6. Roller press according to one of claims 1 to 5,

characterized in that

the pressing cylinder pressing cylinder (21 0, 21 0 ', 220, 220', 230, 230 ', 240, 240') in pairs and opposite each other on the torque scale (250, 260) attack.

7. Roller press according to one of claims 1 to 6,

characterized in that the pressure cylinders (21 0, 220, 230, 240) are loaded to train.

8. Roller press according to one of claims 1 to 7

characterized in that the bearing housings (1 30, 14, 1 50, 1 60), the pressure cylinder (21 0, 21 0 ', 220, 220', 230, 230 ', 240, 240') and the torque scale (250, 250 ', 260, 260') form a self-contained force system.

9. Roller press according to one of claims 1 to 8

characterized in that

that at least one of the bearings of at least one roller (1 1 0, 1 20) is a movable bearing, which provides a degree of freedom in the axial direction of the shafts (1 1 1, 1 1 2, 1 21, 1 22) available. Method for centering the nip (115) of a roller press (100) for pressure treatment or compaction of granular material, which

has at least two rollers (110, 120) rotatably mounted in each case via a shaft in a machine frame (171) and driven in opposite directions and separated from one another by a nip (115) as loose rollers;

wherein in each case two bearing housings (130, 140, 150, 160) of different rollers (110, 120) arranged on one side of the rollers are connected via at least one pressure cylinder (210, 210 ', 220, 220', 230, 230 ', 240, 240'). ) are interconnected

marked by

the use of at least one torque scale (250, 250 ', 260, 260') between the bearing housings (130, 140, 150, 160).