SE511274C2 - Headbox - Google Patents

Abstract

Stock inlet to deliver the pulp flow to the fourdrinier of a papermaking machine, giving a rapid setting to the alignment of the stock inlet box to adjust the point where the pulp flow strikes the fourdriniers. The stock inlet, for a papermaking machine, has two horizontal base plates (49), in release mountings at each frame section (13), to support the lifting arms (18) with leading (38) and trailing (80) mountings. A leading setting support (87) is at both sides of the double fourdrinier under the stock inlet, with a free horizontal surface (89) positioned downstream of the leading mounting (38). At least one moving setting unit (61) is on both sides. A free and horizontal press surface (92), at each lifting arm (18), is vertically over the surface (89) of the leading adjustment support (87). The gap between the surfaces (89,92) allows the setting unit to raise the stock inlet box from the frame section (13) after the base plate (49) has been released from it, to form a space between the frame section (13) and the released base plate (49), for the insertion of a selected number of spacer plates (62). A second and trailing adjustment support (88) is at both sides, fixed to the frame sections (13), and a third adjustment support (74) is secured to the base plate (49) at the center. The trailing and center supports (88,74) each have free vertical surfaces (90,91), while two free vertical press surfaces (94) are away from each horizontally. They form a space for the insertion of the setting unit (61), to move the stock inlet box to and from the pulp outlet gap, after the base plate (49) has been released, and to act on the lifter arms through the facing surfaces. The horizontal press surface (92) and the vertical press surfaces (94) each have a leading projection (27) and a downwards projection (28). A grip (46) acts on the trailing setting unit (41), to rotate the stock inlet box on the leading mounting (38), and also has a parallel shaft (47) between the trailing setting units to synchronize their rotation to give a unified movement. A frame structure (16) supports the stock inlet box. It links the lifter arms (18), with a longitudinal support section at right angles to the machine direction to connect the lifter arms (18) to the stock inlet box. It has a rotating/sliding unit (48), with a support shoulder (53) anchored to the base plate (49) with the sliding unit (53), in contact with a sliding plate (51). A holder (55) takes the leading mounting (38) of the lifter arms (18). The base plate (49) has leading and trailing counter supports (58,59) to give fixed positions for the locking system with a number of setting screws (70), for the lifter arms (18) to be locked (34) in the required position with the counter supports (58,59). The setting screws (70), including the two horizontal setting screws, are coaxial in succession between the counter supports (58,59) and the support shoulder (53). The horizontal screws are threaded into the support shoulder (53), and at least one vertical setting screw (70) is mounted to the trailing counter support (59) for a swing movement, and extends to the lifter arm lock (34) with a stop ring (72) and a number of nuts (73), for a clamping and locking action. The base plate (49) is anchored to the frame section (13) by a release bolt (50). A number of openings in the sliding unit (54) take mounting bolts (69) for a release fitting at the base plate (49) and the sliding plate (51), for them to act together.

Description

10 15 20 25 30 35 511 274 2 gradually thickens into a continuous fiber network work. In order to obtain a correct sheet structure at shift beam thickness, web feed speed or type of stock, it is therefore essential that the stock the spraying takes place on one for the current production carefully determined, since the drainage and thus the tion is strongly influenced by where and how the stock rays strike ned pà viran, i.e. with which angle of impact, at which distance from the stock outlet and at what speed the stock beam hits the forming wire.

In order to be able to make desirable changes to the impact point, length and angle of impact of the stock beam must the inlet drawer and its target outlet can be set.

The thickness of the stock beam is regulated by means of actuators, which set the geometry of the lip opening. When installing tion of the headbox, after replacement, service, etc., must the headbox is set in a position and with a focus in in relation to the forming zone so that the three meters will be the right ones.

The inlet drawers of the tissue machines do not differ the basic principles from other drawers without the drawer type depend on the speed range. Even at a low speed, ie. over 300 m / min, today used closed sprayers, which provide more stable profile and better formation. The speed into the syringe is selected so that you get a good fiber distribution and appropriate intensity of turbulence in the stock without unnecessary pressure loss. However, this requires that the syringe be used the flow for which it is dimensioned, because a lower flow than this results in a poorer fiber distribution and a poorer basis weight profile. If the syringe needs to be replaced thoroughly that a new optimal flow requires this, must the stock beam can be adjusted in a quick and easy way to a new position valid for the new syringe. 10 l5 20 25 30 35 511 '1274 Double wire machines, in which a drainage takes place between double wires, have been known since the 70s. Essentially this type of wire machine includes a chest roller and a forming rollers, which rollers together with said wires forms an inlet pinch, whereby the two wires then runs together below close to 180 ° of the forming roller circumference, forming outer and inner wires. As inlet drawers for double-wire machines only syringes are used, which must be built so that they can be inserted into the nip between the wires, as the free force beam should not exceed one maximum length of about 250 mm, preferably about 100 mm.

This is important for the beam, which can have a speed at 1800-2000 m / min., should not have time to break up on the ground of turbulence before impact on the forming wire. Mäldstrà- even after deaeration, the unwanted pressure set air bubbles, which increase the risk of emergence said turbulence, especially at higher engine speeds. due to the fact that the air bubbles in the stock beam quickly expand, when they come out of the syringe, which breaks and deforms said beam. The lips are approximately equal in length, which in part facilitates of the stock outlet, when the position of the inlet drawer must adjusted or reset. Nevertheless, the said setting a very complicated and time-consuming work due to the lack of space in said inlet nip, why the syringe must first be coarsely adjusted, before one fine adjustment of the lip opening using actuators can become relevant.

The syringe is placed next to the forming roller just before the inlet pinch with its angle of impact and alignment carefully set. Because a very large part of the drainage happens in the inlet pinch, what happens there is very important for the formation of the paper.

The best formation is obtained, if about 30-40% of the beam is below the tangent to the forming roller in 10 15 20 25 30 35 511 274 4 the direction of the beam, so that part of the target beam hits The forming roll, This results in a pressure surge in the the point of impact, which, however, tends to be regulated by lifting the beam so that its lower surface only touches the forming waltz. The more of the target beam that lies under the key to the forming roller the more the pressure shock increases due to that more of the beam hits said forming roll. You get therefore try to find the best position for the target beams and thus for the stock sprayer at different web speeds, concentrations and paper grades with different requirements what constitutes an acceptable formation. Setting device in addition to the syringe must also be so stable that the relation of the stock beam to the forming zone does not change.

There are several different constructions of the market today double-wire machines, which differ from each other by with regard to, for example, the placement of the syringe, ningen pä nypet, m.m.

Depending on what the wet area looks like, the target jets can be directed downwards, horizontally or upwards. Viran stitches contain air that must be removed. An upright beam gives it best venting and least risk of liquid splashes, however at the same time the disadvantage of a more difficult drainage ning. If instead the stock beam hits the forming wire in an oblique downward pinch, while the wires run upwards over the forming roll, the dewatering takes place mainly ligen downwards. All three options are used successfully.

The focus of the stock beam towards a desired point of impact must reset or adjusted during, for example, trimming after regrinding the roller, after changing the roller or byte, etc. In the case of a wire exchange, for example, the inlet the drawer is moved, which, with the awkward adjusting devices available today takes too long time required. The syringe must also be available for inspection and cleaning, why it must be able to lO 15 20 25 30 35 511 274 be made easily accessible so that it can be opened. A simple adjusting device, with which all of the above configurations can be easily set and where an and faster reset after, for example, rolling or wire exchange can be performed, would mean a large profit.

The machine manufacturers today also build syringes can inject two or three jets of stock simultaneously into the nip between two wires, the individual beams from the syringe is held apart by means of air wedges all the way to the point of impact, why the length of the stock rays, ie. setting the distance between the syringe and the the flea market, becomes even more important.

At the high speeds that apply to modern soft- paper machines, hydrodynamics becomes very important. The set e.g. very high demands that the syringe can deliver a power beam with so well attenuated turbulence that the beam holds together until it reaches the pinch between viruses. In this pinch is then the direction of the beam and impact point critical. Due to the cramped space between the inlet nip and the syringe, the setting of a new angle of impact with a maintained beam length being very complicated. In the link systems used today these small changes are a big problem, then so small calibrations can not be performed with ease but large risk of the syringe during this adjustment come into contact with and damage the other equipment.

As mentioned above, a very large part of the dewatering takes place in the inlet nip, so it is of the utmost importance to the watering here is set correctly. This initial dewatering is directly dependent on the angle of impact of the mold jet mot viran. A good formation is obtained, if the fibers can be kept dispersed in the free stock layer until complete fixed in the emerging fiber network without 10 15 20 25 30 35 511 274 6 before forming fibrous flocks. This process is affected by the kind of stock currently in use. Stocked with different origin such as deciduous or coniferous threads, additives, tur m.m. has different forming properties, why different it must be possible to set angles of impact and stock beam lengths in after the current properties and this then quickly and cost-effective, as all downtime in production tion is extremely costly. Excessively slow drainage leads to a decrease in the turbulence in the stock layer and the risk of fibrous flocks forming increases. One too rapid dewatering, for example due to an excessive strong angle of impact, leads to the fiber network being fixed too early. The fiber bed then becomes too dense and fibers can be easily pulled in and caught in the meshes of the wire. This both damages the paper and clogs the wire. Mäldstrålens it must therefore be possible to set the angle of impact with one very high precision, which is impossible with the awkward available constructions available today. These constructions simply can not perform small changes in a fast, stable and easy way.

By generating turbulence in the stock layer below themselves the drainage process, which for the most part takes place immediately after the impact on the wire and during breathing of the wires through the inlet nip, one achieves that any fiber flocks are broken and that the emergence of new ones, which leads to the formation of the paper tion is improved. The angle of impact of the beam, i.e. how big part of the stock jet which strikes the forming roll with the following variation of turbulence and stock pressure, has therefore the dominant effect on successful drainage and thus also on the formation. Additional factors such as affected by the angle of impact are water splashes and to transport away the backwater.

The mentioned setting of inlet drawers has so far been performed by means of several different setting devices, which 10 15 20 25 30 35 511 274 however, they all have in common that they cost significantly sums. In Canadian Patent Specification CA-1,098,748 describes a setting device comprising a link systems consisting of a number of link arms, which are operated of several actuators in a complicated way. Mentioned linkage systems also carry the full weight of the entire headbox the construction, hence the constituent construction elements becomes very bulky and expensive. Actuators in the form of small and light hydraulic or pneumatic piston cylinders can not be used, as a possible pressure drop on due to the rotatable suspension would immediately result in a changed angle of impact of the stock beams with a deterioration in formation as a result. Because everyone movements in the described suspension device are constituted of rotational movements, it is further not possible to change the point of impact without simultaneously changing both the sontella as the vertical position. Also, one can not predetermined length of the stock beam is maintained. At the heavy and awkward constructions in question here, it is also completely impossible to use alone link arms and actuators obtain definite and precise movements. One must therefore through repeated and time-consuming try to operate the headbox back and forth, before a reasonably acceptable position can be obtained.

It is further known from the explanatory note SE-447 139 a headbox, which is carried by the front and rear frame structures, in which horizontal sliding guides are arranged. The headbox can be moved in one horizontal direction using a first actuator.

An additional actuator is arranged at the headbox rear part, with which also a rotation around one at it guide shaft arranged in front of the frame structure can be made.

Thus, the headbox can be moved in a horizontal direction, which affects, for example, the beam length, and rotated about said front articulated shaft, thereby the angle and point of impact can be varied. 10 l5 20 25 30 35 511 274 s However, the headbox can not be moved vertically, why even this setting device is clearly limited in its adjustability in relation to a fixed inlet nyp.

The German explanatory memorandum DE 43 28 997 describes finally a setting device, with which an attempt is made to cope with said complex setting of both one a certain desired direction and a certain specific meeting point, at the same time as a predetermined target beam length is maintained hálles. The entire weight of both the headbox and the set the actuator is supported by the described actuator as well as its storage means. It is easy to see that such setting device, which must be dimensioned to handle very large loads, about 40 tons, requires one extremely powerful and costly construction. After- which the center of gravity of the structure will vary according to where the headbox is located, each input element must elements, for example bearings, actuators, etc., are dimensioned for a number of variable and variable load cases, where of the entire adjusting device, including the inlet lock dan, in the extreme case almost entirely worn by alone one of the respective elements, see figure 3 in the one described here the writing. The constituent elements therefore become strong oversized compared to if the loads are distributed more evenly between several sub-elements, which is why problems with the position of the stock beam arises, as the actuators cannot provide the accuracy and flexibility required race. The setting device shown comprises at least three pairs of permanently mounted jacks, which are more expensive construction, partly due to the large loads exposed test for excessive wear. Because the construction is suspended in a system of actuators, all of which are free to move in relation to each other, in addition, difficulties in curbing the insurmountable the vibrations in a satisfactory manner. lO l5 20 25 30 35 511 274 A main object of the present invention is to at least for the most part eliminate the above problems, and provide an improved device for setting the position of an inlet drawer so that its stock beam in a fast, easy and reliable way can be set in an optimal position with respect to the point of impact, length and angle of impact of the stock beam in relation to a forming zone at the inlet pinch to a double wire machine.

Another object of the invention is to provide one device for adjusting the position of an inlet drawer so that a paper web with a good formation can be produced, regardless of the type of mold or at what speed or flow that is considered optimal for the current the headbox construction or the wire configuration.

A further object of the invention is to provide come a device for setting a headbox so that any vibration or instability at the headbox eliminated or at least significantly reduced.

A further object of the invention is to provide come a device for setting a headbox according to the current paper quality, pulp quality as well as the machine speed, so that its alignment and stand can be adjusted with respect to height, length and slope in a considerably simpler and more flexible way one third of the normal cost.

The device according to the invention is characterized in that the adjusting device further comprises two horizontal base plates, which are releasably arranged at each tripod part and supporting the lifting arms; 511 274 10 10 15 20 25 30 35 a first, front actuator support at each machine side, which has a free, horizontal surface and is located downstream said front storage means; at least one movable actuator at each machine side; a free horizontal pressing surface, which is formed in each lifting arm vertically above the front actuator support Surface; that said pressing surface and surface of the front actuator the support between them delimits a space for receiving the actuator, which upon activation has its resistors force-transmitting press surfaces in engagement with said press surface of the lifting arm and the surface of the actuator support for lifting of the headbox from the frame parts after the said base plate detached from the frame part to form a space between the frame part and the one detached from it bottom plates; and a supply of spacer plates for placement in said intermediate lane space between the base plate and the frame part in a certain number corresponding to the necessary setting of the headbox in height after deactivation of the actuator.

An essential advantage of the invention is that they are included the dimensions of the structural parts can in some cases be race, for example, the plate thickness of various bearing elements are reduced from 100 mm to 50 mm. The construction according to the invention, therefore, not only re, about one third of the normal cost, without, since the weight of said construction becomes lower, too management is simplified with the subsequent streamlining of inlet drawer setting.

The invention is explained in more detail below with reference to to the drawings.

Figure 1 is a schematic side view of parts of a wet section of a paper machine seen from the driver's side, including 10 l5 20 25 30 35 11 511 274 a double-wire machine with a headbox, which is equipped with an adjusting device according to the invention.

Figure 2 is a schematic side view of parts of the installation the device according to figure 1 seen from the driver's side and showing a lifting arm rotatably arranged partly to a rear actuators, partly to a turning and sled member, a number movable actuators and a locking device.

Figure 3 is a schematic view of parts of the headbox and its adjusting device according to Figure 1 as seen upstream of the double-wire machine and with sections at the side cut off.

Figure 4 is a detail cross-section through the driver's side rotation and sled means according to Figure 3.

Figure 5 is a top view of parts of the adjusting device according to figure 1 seen straight from above, showing the driver's side rotating and sliding means and a locking device which fixes this.

Figure 6 is a detail view of the driver's rear actuator according to figure 1.

Figure 7 is a detail view of the driver's lifting arm seen from driver side.

Figure 8 is a top view of the lifting arm according to Figure 7 seen from above.

Figure 9 is a side view of a base plate of the rotary and the slide member according to Figure 5, showing a sliding plate and front and rear abutments for two substantially horizontal acting set screws. 10 15 20 25 30 35 511 274 12 Figure 10 is a top view of the bottom shown in Figure 9. the plates seen from above.

Figures 11, 12 and 13 are detailed views of a support ear of the turning and sledging means according to figure 4 seen from the driver the side, the inlet pinch and straight from above.

Figure 14 is a top view of a spacer plate included in the adjusting device according to figure 1.

Figure 15 is a side view of the spacer plate of Figure 14 seen from the inlet pinch.

Figure 1 shows diagrammatically in side view parts of a device 1 for setting a headbox 2 at a paper machine 3 seen from the driver's side 4. The headbox 2 has a housing 75 with a nozzle chamber and a stock outlet with an outlet nozzle 77 in the form of a lip opening for ejection of a single or multilayer jet of grist. The headbox 2, as in the embodiment shown is a syringe, is located next to an inlet pinch 5 to a double wire machine 6, in which a dewatering takes place between an outer wire 7 and an inner wire 8. said double wire machine 6 comprises a breast roll 9 and a forming roll 10, which rollers 9, 10 together with the wires 7, 8 forms said inlet pinch 5, whereby the two wires 7, 8 run together around a large part of the forming roller 10 perimeters.

The adjusting device 1 comprises a frame construction 11, which connects to the paper machine 3 other machine racks 12 on a stable and, so far so is technically possible, vibration-free way. Tripod In addition, the structure 11 is so constructed that the inlet drawer 2 is easily accessible for tuning, adjustment and service. The frame construction 11 comprises according to it shown embodiment, see Figures 1 and 3, two racks 10 15 20 25 30 35 13 511 274 parts 13, 14 arranged at the driver side 4 of the paper machine 3 and drive side 15, between which frame parts 13, 14 double the wires 7, 8 of the wire machine run in under the headbox 2.

If another stretch of wire is considered more advantageous, one can such are of course arranged within the scope of the present invention. Such an alternative route may then be obtained by arranging one or more guide rollers (not shown) for said wires 7, 8 in the vicinity of said inloppslada 2.

As can be seen from Figures 2, 3 and 4, the positioning device 1 a body carrying the inlet drawer 2 construction 16, which comprises a lifting device 17, which has two lifting arms 18, 19, which are suitably arranged on each side of the headbox 2. The frame structure 16 also includes a substantially perpendicular to the machine direction provided elongate support member 20, which connects said lifting arms 18, 19 to the headbox 2. At In the embodiment shown, the support member 20 consists of two stable box beams 21, 22, which extend between the insides of said lifting arms 18, 19 and to these single sides of the headbox 2, the attachment of respective box beam 21, 22 to said lifting arms 18, 19 consists of a screw connection 23 (see figure 2). This attachment may, however, consist of any other suitable dressing, such as welded or riveted joints, if desired.

In the following description, when corresponding construction elements appear on both the driver's side 4 and drive side 15 of the paper machine 3, driver side 4 only construction elements to be treated, because the difference between said elements is only that they are mirror-inverted in relationship to each other.

With the terms "forward" and "backward", respectively "front" and "rear", "downstream" and "upstream", etc. referred to 10 15 20 25 30 35 511 274 14 movements, directions or positions in relation to machine direction or inlet pinch 5.

As shown in Figures 7 and 8, each includes lifting arm 18, 19 an elongate body 24, the appearance and cross-sectional shape is adapted to other construction elements, with whom it is to cooperate, and to the loads, for which it will be exposed to. The elongated body 24 has a front end 25 and a rear end 26. Further each lifting arm 18, 19 comprises a stirrup member 29, which is arranged in the front half of the lifting arm 18, 19 and attached to its vertical outside facing the drawer 2. Bracket- the member 29 comprises three rectangular and vertical plate elements 30, 31, 32, of which a first plate element Is arranged at a distance from and substantially parallel with the lifting arm 18, 19, while the other two plate elements 31, 32, which have substantially the same dimensions, are attach to the lifting arm 18, 19, from the headbox 2 inverted, vertical exterior to form one in vertical direction through cavity 33 together with the first the plate element 30. A locking element 34, the purpose of which is more detailed described below, is further attached partly to the yoke member 29 top, partly to the outside of the lifting arm 18, 19, which locking element 34 comprises a rearwardly open elongate groove 35 substantially parallel and coaxial with the continuous the cavity 33. Two circular through-openings 36, 37 are further arranged coaxially with each other, of which it one opening 36 is provided in the first plate member 30 and the second opening 37 in the lifting arm 18, 19. The openings 36, 37 are arranged to receive a front storage means 38, for example comprising a hinge pin or hinge shaft, including therefore suitable bushings. Furthermore, one appropriate number of heels 39, which are intended for said screw bandage 23 to the elongate support member 20, received in the middle section of the lifting arm 18, 19, at the one shown in figure 7 the embodiment consisting of three holes in a row along the lifting arm 18, 19 upper edge and lower edge, respectively. As early as lO 15 20 25 30 35 15 511 274 welded joints or rivet joints can be mentioned instead selected if desired, which also applies to all others fix bandages. An additional heel 40 is included therein rear portion 26 of the lift arms 18, 19. Adjustment the arrangement includes rear mechanical actuators 41, 42, which are connected to the lifting arms 18, 19 at said hole 40. In the embodiment shown, the actuators are constituted 41, 42 of mechanical screw jacks. Each screw jack 41, 42 are rotatably mounted at their lower and upper ends at the lifting arm 18, 19 and the frame part 13, 14 respectively. partially suitable storage means 79, 80. Each screw jack 41, 42 comprises a rotatable spindle or a substantially vertically displaceable rack, which encloses of a protective helical bellows 43 and a protective tube 44 at their upper and lower portions (see Figure 6), which parties are outside a suitably wide the center part of the rack arranged transmission box 45.

The transmission drawer 45 holds in the usual manner missionary means for the conversion of an applied torsional motion to an axial movement. At least on the driver's side 4 a gripper 46 from said transmission box 45, by means of which gripper 46 an operator by means of a suitable tool can operate the rear actuators 41, 42 in an ascending or descending direction so that the race carriage 2 is thereby rotated around the front storage the means 38 of the lifting arms 18, 19. A parallel shaft 47, which connects the transmission means to each other, extends between the rear actuators 41, 42 so that a synchronized and uniform rotational movement can be obtained on the driver's side 4 and the driver's side 15.

As can be seen from Figures 4 and 5, a rotary and carriage means 48 arranged on each machine side 4, 15, which rests on a base plate 49, which is releasably mounted at the frame part 13, 14 by means of a plurality of bolts 50. the plate 49 carries a sliding plate 51, at which one suitable measuring scale 52, such as a steel ruler, is mounted at its 10 15 20 25 30 35 511 274 16 facing the driver side 4 and the drive side 15, respectively, and parallel to the machine direction. Each turning and sled- means 48 comprises a support ear 53, which consists of a horizontal sliding member 54 (see Figures 11-13) resting on the sliding plate 51 of the bottom plate 49, and a vertical holder part 55 with its vertical plane parallel to the machine direction and attached eccentrically to the horizontal slide member 54 top. The vertical holder part 55 has an opening 56 for receiving the front storage means of the lifting arm 18, 19 38 and is arranged to be inserted into the cavity 33, which is present between the stirrup member 29 and the lifting arm 18, 19 so that ring member 38, can be inserted through the yoke member 29, the holder part 55 and the lifting arm 18, 19 for forming a swivel joint. The horizontal slider 54 has one with it said measuring scale 52 cooperating hands 57, whereby any displacement in the machine direction of the support ear 53 and thus the inlet drawer 2 can be read.

As shown in Figure 5, each base plate 49 carries one anterior abutment 58 and a rear abutment 59, which abutments are firmly anchored, e.g. by welding, at the bottom 49. Between the base plate 49 and the frame part 13, 14 one or more spacer plates 62 are placed, the total of which construction height is selected for setting the turning and sled member 48 in a position which gives the headbox 2 the desired height the situation.

Support ear 53 horizontal horizontal part 54 and vertical holder part 55 are firmly connected to each other into one L-shaped unit. Figure 11 shows the opening 56 in the support ear 53 holding part 55 which receives the lifting arm 18, 19 front storage means 38. Directly below the vertical holding the part 55 is located in the sliding part 54 a central cavity 63, to which two coaxial, threaded holes 64, 65 are connected for receiving each set screw 66, 67, which are included in a locking device 60. The heel space 63, as well as the holes 64, 65, are oriented in the machine direction. Furthermore, the sliding part is 54 10 15 20 25 30 35 1,511,274 provided with two slit-shaped recesses 68, which are arranged one after the other in the machine direction, next to the vertical holder part 55. The support ear 53 is fixed to the bottom plate 49 by means of fixing screws 69 (see figure 4), which extends through the recesses 68 and screwed into threaded holes 81, 82 in the slide plate 51 and bottom plates 49.

The locking device 60 is intended to ensure that the inlet The position and orientation of the drawer 2 are completely fixed after each setting made. It comprises said horizon adjusting screws 66, 67 (see Figures 2 and 5), which are arranged in line with each other. Adjusting screw 66 works between the support ear 53 and the anvil 58, while the adjusting screw 67 acts between the support ear 53 and the abutment 59. The steel screw warns 66, 67 are screwed into the threaded holes of the support ear 53 64, 65 so that the heads of the adjusting screws 66, 67 abut the front bracket 58 and the rear bracket 59, respectively at said fixation. With the reference numbers 83, 84 are referred to as locknuts which, in the operative position, prevent turning the adjusting screws 66, 67. The locking device 60 also includes a substantially vertical steel screw 70 with skull 85 received in a recess 71 in the anvil 59 rear end and rotatably mounted on the bracket 59 by means of a shaft journal 86. The vertical adjusting screw 70 extends up to the locking member 34 at the lifting arm 18, 19 jumper means 29. It comprises a stop ring 72 (see figure 2), and a plurality of nuts 73, which are arranged so that the stop ring 72 can be clamped against the locking element 34 underside, whereby the lifting arm 18, 19 can thus be locked fixed in its set position. In the embodiment shown but the adjusting device 1 comprises a movable one actuators 61 and three actuator supports 87, 88, 74 at each machine side 4, 15, namely a first, front actuator support 87, which is fixed to the frame part 13, 14, a second, rear actuator support 88, which is fixed to the station part 13, 14, and a third, middle actuator support 10 15 20 25 30 35 511 274 18 74, which is supported by the base plate 49 and is fixed to this. If desired, there may be more than one removable actuators 61 at each machine side 4, 15. Each lifting arm 18, 19 are provided with three pressing surfaces 92, 93, 94 (see figure 7), which are located at a predetermined distance from and in the middle for each actuator support 87, 88, 74. At the shown In the embodiment, each lifting arm 18, 19 is formed with one horizontal, forwardly projecting projection 27 at it front end 25 and a vertical, downwardly projecting protrusion 28. At the horizontal protrusion 27 it is located said pressing surface 92, which has a horizontal stretch and facing downwards, while the other two pressing surfaces 93, 94 are trained at the vertical projection 28 and have bare extent. The third, middle actuator support 74 extends across the machine direction and is firmly connected it, e.g. by welding, with the base plate 49 and the rear end of the bracket 59 and with a reinforcing element 76, which is welded to the base plate 49 at its from the driver side 4 and the drive side 15, respectively rear corner (see Figures 9 and 10).

The first, front actuator support 87 is provided at the front end portion of the frame portion 13, 14 and has one horizontal surface 89, which is located vertically below and on predetermined distance from the horizontal projection 27 horizontal pressing surface 92 to provide sufficient space for placing the movable actuator 61 therebetween lan. The second, rear actuator support 88 is provided at the rear end portion of the frame portion 13, 14 and has one vertical surface 90, which is located upstream of and on predetermined distance from the vertical projection 28 rear, vertical pressing surface 93 to provide sufficient space for placing the movable actuator 61 in between. The second, middle actuator support 74 is thus located between the front and rear actuators supports 87, 88 and has a vertical surface 91 which is located downstream of and at a predetermined distance from the 10 15 20 25 30 35 19 511 274 the front, vertical pressing surface 94 of the blast 28 to provide sufficient space for placement of the movable the actuator 61 in between. The actuator 61 has one press element 95, which projects from its power structure body so that the actuator 61 with its opposing forces transmitting press surfaces with controlled force act against the pressing surfaces 92, 93, 94, the actuator 61 abutting the current, fixed actuator support 87, 88 or 74.

By the term "movable actuator" is meant herein invention that the actuator 61 is not fixedly connected to any structural part of the headbox 2 or its setting device 1, but is in free contact with the opposite surfaces 89, 92; 90, 93; respectively 91, 94 so that the actuator 61 is manually inserted and removed the space bounded by said opposite surfaces 89, 92; 90, 93; respectively 91, 94.

The movements of the inlet drawer 2 outlet nozzle 77 are kept within those at the inlet nip 5 of the double wire machine 6 the maximum permissible limits by the lifting arms 18, 19 vertical rotational movements are limited downwards by each frame part 13, 14 and upwards of one for each lifting arm 18, 19 arranged, suitably in the vicinity of each rear height-adjustable mechanical actuators 41, 42 device 78 (see Figures 1 and 2).

The function of the setting device 1 is as follows.

Depending on the angle of impact, the point of impact and which stock beam length sought must be displaced the inlet drawer 2 takes place in at least one of several directions, including a substantially vertical movement upwards or downwards, a substantially horizontal moving forward or backward as well as a movement by rotating the headbox 2 around the storage means 38. Most often, a combination or a repetition of at least two of the mentioned movements are performed in one successively, before the desired parameters 10 15 20 25 30 35 511 274 20 for the stock ray can be achieved. If, for example, you want one slightly steeper angle of impact for the stock jet, but with a maintained hit point in the nip 5 of the double wire machine 6, at the same time as a slightly increased stock beam length, must partly a movement of the headbox 2 in a horizontal direction backwards, partly a movement of the headbox 2 i a vertical direction upwards, partly a rotation of the inlet the drawer 2 around its storage means 38 is made in a suitable manner order. A setting of the headbox 2 can for example, start by moving it backwards in the direction from the nip 5 a certain piece, whereby an increased space for the movements of the outlet nozzle 77 in or at the pinch 5 of the double wire machine 6 is created. In doing so, each is unloaded support both mounting screws 69 to the base plate 49 and the horizontal adjusting screws 66, 67 to thereby enable a horizontal sliding between said support sliding part 54 of the ears 53 and the sliding plate 51 of the bottom plate 49.

The movable actuator 61 at each machine side 4, 15 placed at the middle actuator support 74, as year arranged at the rear portion of the base plate 49, and with its direction of force action against the vertical of the lifting arm 18, 19 projection 28, after which the two actuators 61 are thus activated that the two lifting arms 18, 19 together with the two the rotating and striking means 48 are displaced horizontally backwards away from the nip 5. At this displacement, seen from driver side 4, turn the two mechanical screw jacks 41, 42 clockwise around partly their lower storage members 79, which are arranged at the respective machine frame parts 13, 14, partly their upper storage means 80, which are arranged at each lifting arm 18, 19 rear end portion 26. The parallel shaft 47, which cooperates with and extends between the two screw forces 41, 42, thereby ensuring that the synchronized the movements on the driver side 4 and the drive side 15 are synchronized with each other. Before and / or after the one below described lifting of the headbox 2 can be operated the means 61 are moved to act between and against the rear ones actuator supports 88 and the vertical projections 28 for lO 15 20 25 30 35 21 511 274 thereby moving the headbox 2 a desired piece in the direction of the nip 5 in order to adjust the outlet mouth ~ distance of the piece 77 to the nip 5 or the point of impact of mäldstrålen. Each is supported by 53 horizontal adjusting screws 66, 67 and the fixing screws 69 are then screwed on so that no further horizontal movement of the support ears 53 can take place, after which the fixing bolts 50 of the base plates 49 are loosened from the frame parts 13, 14. The movable actuators 61 then placed at the two front actuator supports 87, which are fixed to the frame parts 13, 14, and are brought to act against the horizontal projections of the lifting arms 18, 19 27 to lift the pivot and slide members 48 together with the base plates 49 screwed to them (fixing screws 69 are tightened). The promotion takes place until a required space is obtained under the base plates 49 for a number suitable for the desired change in height spacer plates 62 of predetermined thickness, which are slid in between the base plates 49 and the frame parts 13, 14, after which the actuators 61 are deactivated so that the headbox 2 is lowered slightly depending on the clearance to take its new position in height. The fastening bolts 50 are screwed tight in the frame parts 13, 14, after which a final alignment of the stock outlet 77 with respect to the angle of impact is made by rotating the headbox 2 around the lifting arms 18, 19 front storage means 38 by activating the two rear ones actuators 41, 42 using the driver 's side 4 arranged the gripper 46 after the adjusting screws 70 unloaded. After this angle change of the headbox 2 screwed, the steel screws 70 tighten. The said horizon- The displacement can of course be preceded by the said the rotation or of the vertical movement, if so desired. Each additional setting of the stock beam in in relation to the nip 5 involving altered impact angle, stock beam length and / or point of impact are available at the method described above with successive linear displacements and rotations using the 10 15 20 25 30 511 274 22 movable actuators 61 and the rear actuators 41, 42.

Thus, the alignment and position of the headbox is achieved 2 can be varied in a very simple, efficient and accurate and that the entire weight of the headbox 2 is car can rest on the stand 12 under the paper machine 3 operation, why the previous vibrations, involuntary the position changes of the headbox 2 and all the others initially mentioned problems with the hitherto devices, such as unstable link systems with large, clumsy jacks, can be eliminated.

The actuators 61 required for the inlet drawer 2 for movements can advantageously consist of pneumatic, hydraulic hydraulic or electric actuators, which are easy to handle unlike the considerably larger, fixed ones previously used mechanical jacks. The actuators 61 of the adjusting device 1 according to the invention can therefore easily moved by a single operator from a control donor support 74, 87, 88 to another.

It will be appreciated that the dimension, location and shape of the elements of the setting device described above the arrangement 1, for example the spacer plates 62, the screws, lifting arms 18, 19, etc., are adapted to either the driver page 4 or drive side 15, and to the current shape and the relative position of the others in the construction said construction elements.

Claims (8)

lO 15 20 25 30 35 23 511 274 P A T E N T K R A V A headbox (2) of a paper machine (3), which headbox (2) is included in the wet portion of the paper machine (3), which comprises a forming roll (10) and outer and inner wires (7, 8), as in the forming roll (10) converge to form a nip (5), which headbox (2) has a housing (75) with a nozzle chamber and a stock outlet (77) for ejecting a single or multilayer jet of stock, which stock jet has a fixed length, impact angle and point of impact relative to said nip (5), which headbox (2) comprises two frame parts (13, 14), which are arranged at the paper machine 19), which, seen in the machine direction, have front and rear (3) guides and drive sides (4, 15), lifting arms (18, storage means (38, 80) and extending above and along the frame parts (13, 14), and a device (1) for adjusting the position and alignment of the inlet carriage (2) so that the stock beam obtains said determined length, angle of impact and point of impact, which setting device (1) comprises has two rear, mechanical actuators (41, 42), which are rotatably mounted at the rear storage means (80) of the lifting arms (18, 19) and at the frame parts (13, 14), the inlet drawer (2) being adjustable by a rotational movement about said front storage means (38) of the lifting arms (18, 19), characterized in that the adjusting device (1) further comprises two horizontal base plates (49), which are releasably arranged at each frame part (13, 14) and support the lifting arms ( 18, 19); a first, front actuator support (87) at each machine side (4, 15), having a free, horizontal surface (89) and located downstream of said front storage means (38): at least one movable actuator (61) at each machine side (4, 15); A free horizontal pressing surface (92) formed by each lifting arm (18, 19) vertically above the surface (89) of the front actuator support; that said pressing surface (92) and surface (89) of the front actuator support (87) define between them a space for receiving the actuator (61), which upon activation has its opposing force-transmitting press surfaces in engagement with said press surface (92) of the lifting arm (18, 19) and the surface (89) of the actuator support for lifting the headbox (2) from the frame parts (13, 14) after said bottom plate (49) has been detached from the frame part (13, 14) to form a gap between the frame part (13, 14) and the bottom plate (49) detached from it; and a supply of spacer plates (62) for placement in said space between the base plate (49) and the frame part (13, 14) position of the headbox (2) (61). in a certain number corresponding to the necessary in- height after deactivation of the actuator Inlet drawer according to claim 1, characterized in that it comprises a second, rear actuator support (88) at each machine side (4, the part (13, 15), which is fixed to the frame 14), and a third, middle actuator support (74 ) at each machine side (4, 15) fixed to said base plate (49), which rear and middle actuator supports (88, 74) each have a free, vertical surface (90, facing away from each other and formed by each lifting arm 91); two free vertical pressing surfaces (93, 94), which (18, 19) are horizontally opposite each of said vertical surfaces (90, 91) of the rear and middle actuator supports (88, 74) to form spaces therebetween. for placing the actuator (61) therein, the inlet drawer (2) being arranged to be moved horizontally as required in the direction of the nip (5) or in the direction of the nip (5) after said bottom plates (49) have been detached from the frame parts (13). , 14) in that the actuator (61) at each machine side (4, 15) is arranged to act with its force-transmitting pressing surfaces against the vertical surface (91) of the central actuator support (74) and the lifting arm of the center actuator (74). (18, 19) vertical pressing surface (94) and against the vertical pressing surface (90) of the rear actuator support (88) and the vertical pressing surface (93) of the lifting arm (18, 19). Inlet drawer according to claim 2, characterized in that said horizontal pressing surface (92) and vertical pressing surfaces (93, 94) of the lifting arms (18, 19) are formed at a forwardly directed projection (27) and at a downwardly directed projection (28), respectively. A headbox according to any one of the preceding claims, characterized in that it further comprises on the one hand a gripper (46) arranged, at least on the driver's side (4), by means of which gripper (46) said rear actuator (41, 42) is arranged to be operated, so that the inlet drawer (2) can thereby be rotated around the front storage means (38) of the lifting arms (18, 19), and a parallel shaft (47), which is arranged to extend between said rear actuator (41, 42), whereby said rotation is synchronized and uniform. An inlet carriage according to any one of the preceding claims, characterized in that it further comprises a body structure (16) carrying the inlet carriage (2), which comprises said lifting arms (18, 19), at least one substantially perpendicular to the machine direction arranged elongately support means (20), which connects said lifting arms (18, 19) to the inlet drawer (2), and a rotating and sled means (48), which comprises a support ear (53), which has on the one hand a sliding part (54), which is releasable anchored to said base plate (49) and resting on a sliding plate (51) arranged therewith, on the one hand a holder part (55), at which the front storage means (38) of said lifting arm (18, 19) are arranged. 10 15 20 25 30 35 511 274 26 Inlet carriage according to one of the preceding claims, characterized in that front and rear abutments (58, 59) are arranged at each base plate (49), which abutments (58, 59) constitute fixed positions for a locking device (60). , which comprises a plurality of adjusting screws (66, 67, 70), whereby the lifting arm (18, 19) can be locked in a set desired position by means of a reading element (34) arranged at the lifting arm (18, 19), and the said recesses (58, 59). Inlet carriage according to claim 6, characterized in that said adjusting screws (66, 67, 70) comprise on the one hand horizontal adjusting screws (66, 67), which are arranged coaxially in a row one after the other between the front and rear counter stops (58, 59) and support ear (53), in which support ear (53) the horizontal adjusting screws (66, 67) are screwed in, and at least one further substantially vertical adjusting screw (70), which is rotatably mounted at the rear abutment (59), which vertical adjusting screw (70), which extends up to said locking element (34) at the lifting arm (18, 19), comprises partly a stop ring (72) and partly a number of nuts (73), which adjusting screws (66, 67, 70) can is fixed to the lifting arm (18, 19) in its set position partly by said horizontal adjusting screws (66, 67) abutting closely against said front and rear abutment (58, 59), partly by said stop ring (72) being able to clamped at said locking element (34) by means of said nuts (73). 1 <is1- that the base plate (49) is stably anchored by means of releasable mounting bolts (50) at the frame part An inlet carriage according to any one of the preceding claims, wherein: ec: kI1a (13, 14) and that a number of recesses (68) are received in the sliding part (54) along the vertical holder part (55), through which recesses (68) fasten screws (69) are releasably arranged at and during cooperation with said bottom plate (49) and the sliding plate (51) arranged on top of it.