JP2006263759A - Device for adjusting roll gap - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To provide a adjusting device of the roll gap with which the accurate gap adjustment is performed even in operation by accurately moving a cotter by the operation of a push-pull mechanism without being affected by a clearance even when the clearance such as backlash in the push-pull mechanism is present, pushing and pulling force is small even in the case compressive load is large, the push-pull mechanism the output of which is always small is sufficient, the deformation of a frame and a journal box is kept small and constant and, as a result, more precise gap adjustment is made possible. <P>SOLUTION: This device is provided with a first journal box 5 for supporting a first roll 3, a pressing means 30 for pressing the first journal box against and toward a second journal box 6 of the opposite second roll 4 and a gap adjustor 10 which is inserted between the first journal box and the second journal box and with which the gap is adjusted. The pressing means is composed of a pressing cylinder 32 for pressing the first journal box against and toward the second journal box, a load cell 34 for detecting the compressive load which acts on the gap adjustor and a pressing force controller 36 with which the pressing force of the pressing cylinder is controlled and the detected compressive load is held constant. <P>COPYRIGHT: (C)2007,JPO&INPIT

Description

  The present invention relates to a roll gap adjusting device that adjusts a gap between rolls that receive a compressive load.

  For example, Patent Documents 1 and 2 have already been disclosed as roll gap adjusting devices that adjust a gap between rolls by holding a cotter between axle boxes of a plurality of rolls and moving the cotter.

  As shown in FIG. 6, the “roll gap adjusting device” of Patent Document 1 includes a pair of rolls 61, 62 laid on bearings 63, 64 provided on a frame, and a cotter shape provided between the bearings. In the apparatus for adjusting the gap between the rolls by moving the slider 65, a pair of scaled main scale 66 and sub-scale 67 are attached to the bearing frame and the cotter-like slider.

  As shown in FIG. 7, a “thermoplastic resin sheet thickness automatic changing device” of Patent Document 2 is used to change the plate thickness while maintaining the stability of the bank. , 72, 73, and a die 74 for supplying a sheet-like molten resin between the rolls, and means 75 for setting the thickness of the sheet-like molten resin; Means for synchronizing the respective roll gaps and the rotation speed of the rolls are provided.

Japanese Unexamined Patent Publication No. Hei 4-349996, “Gap Adjustment Device for Rolls” Japanese Patent Application Laid-Open No. 2-94917, “Automatic thickness change device for thermoplastic resin sheet”

FIG. 5 is a diagram showing the balance of loads in the cotter. As shown in this figure, when the compression load is P, the inclination angle of the cotter 54 with respect to the horizontal is θ, and the friction coefficient of the tapered surface 54a is μ, the friction force on the lower surface of the cotter 54 is μP. Since the component force and the vertical force along the taper surface of the compression load P are Psinθ and Pcosθ, the frictional force is μPcosθ, and the horizontal components of the component force and the frictional force are Psinθcosθ and μPcos ² θ, respectively. .
Accordingly, the pressing force F2 that moves the cotter 54 to the left in the figure, opposite to the tensile force F1 that moves to the right in the drawing, is expressed by the equations (1) and (2).
Tensile force ^{F1 = μP + μPcos 2 θ +} Psinθcosθ ··· (1)
Pushing force F2 = μP + μPcos ² θ−Psin θcos θ (2)

Assuming that the ratio of the vertical movement amount and the horizontal movement amount of the cotter 54 is 1/10, tan θ = 0.1, θ is about 5.71 °, cos ² θ≈0.99≈1.0, sin θcos θ≈ 0.099≈0.1. Therefore, when the compressive load P is 10 tons = 10000 kg and the friction coefficient μ is 0.2, equations (3) and (4) are obtained.
Tensile force F1≈0.2 × 10000 + 0.2 × 10000 × 1.0 + 10000 × 0.1 = 2000 + 2000 + 1000 = 5000 kg (3)
Pushing force F2≈0.2 × 10000 + 0.2 × 10000 × 1.0 + 10000 × 0.1 = 2000 + 2000−1000 = 3000 kg (4)
In addition, the above is an example, the friction coefficient μ is usually about 0.1 to 0.4, and the ratio of the vertical movement amount and the horizontal movement amount of the cotter can be arbitrarily designed. It is about 10.

As can be seen from the above-described example, in the conventional roll gap adjusting device, when pushing and pulling the cotter (gradient plate), the frictional force on the upper and lower surfaces of the cotter and the horizontal force on the inclined surface of the gradient are required. .
As a result, the frictional force (4000 kg in the above example) is generally larger than the horizontal component force (1000 kg in the above example), so that the push-pull mechanism (for example, a bolt and a screw hole screwed into the bolt) is used. Due to the inevitably existing gap such as backlash, an error corresponding to the gap occurs in the push-pull mechanism during the push operation (leftward in the figure) and pull operation (rightward in the figure), and the operating position of the push-pull mechanism I cannot move the cotter accurately. For this reason, it is necessary to stop the operation and move the cotter accurately, and there is a problem that an accurate gap adjustment during the operation cannot be performed.

  Further, as can be seen from the above-described example, the tensile force and the pressing force required for the push / pull mechanism reach about 30% to 50% of the compression load P. The force becomes very large in proportion to the coefficient of friction, and a high-power push-pull mechanism is required.

  Furthermore, since the horizontal force corresponding to the tensile force and pressing force required for the push / pull mechanism acts on the frame of the device to which the roll gap adjusting device is attached, the frame is deformed, and precise gap adjustment becomes difficult. was there.

On the other hand, the pressing force for pressing the axle box that supports both ends of the roll also fluctuates due to the fluctuation of the rolling load acting between the rolls. That is, if the supporting force of the rolling load acting between the rolls is P1, the pressing force of the axle box is P2, and the compressive load of the cotter is P, the relationship of Expression (5) is established.
P = P1-P2 (5)
As is clear from this equation (5), when the pressing force P2 of the axle box is kept constant as in the prior art, the compression load P of the cotter fluctuates due to the fluctuation of the rolling load, and the deformation amount of the axle box and the push-pull mechanism The horizontal force due to the fluctuations caused the bending of the supporting frame, which affected the cotter movement direction, resulting in an error.

  The present invention has been made to solve such problems. That is, the objects of the present invention are as follows: (1) Even if there is a gap such as backlash in the push-pull mechanism, the cotter is moved accurately by the operation of the push-pull mechanism without being affected by the gap, and the accurate gap can be obtained even during operation. (2) The force of pushing and pulling is small even when the compression load is large, and a small output push-pull mechanism is always sufficient. (3) The amount of deformation of the frame and axle box can be kept small and constant. An object of the present invention is to provide a roll gap adjusting device capable of precise gap adjustment.

  According to the present invention, the first axle box that supports the first roll, the pressing means that presses the first axle box toward the second axle box of the second roll that faces the first axle box, the first axle box, There is provided a roll gap adjusting device characterized by comprising a gap adjuster that is sandwiched between biaxial boxes and adjusts the gap.

  According to the configuration of the present invention, the pressing means presses the first roll toward the opposing second roll via the first axle box, and the roll position is held against fluctuations in rolling load acting between the rolls. be able to. In addition, a predetermined compressive load is applied to the gap adjuster by this pressing means, and the gap adjustment by the gap adjuster can function properly.

  According to a preferred embodiment of the present invention, the pressing means includes a pressing cylinder that presses the first axle box toward the second axle box, a load cell that detects a compressive load acting on the gap adjuster, and the pressing It comprises a pressing force control device that controls the pressing force of the cylinder and holds the detected compression load constant.

With this configuration, in the above-described equation (5), the load cell detects the compression load P acting on the gap adjuster, and the pressing force control device controls the pressing force P2 of the pressing cylinder so as to hold the compression load constant. can do.
Therefore, even if the supporting force P1 of the rolling load fluctuates, the compressive load P acting on the gap adjuster is kept constant, the amount of deformation of the axle box and the horizontal force by the push-pull mechanism are kept constant, and the supporting frame and shaft The amount of deformation of the box can be kept small and constant, thereby enabling precise gap adjustment.
Even if the rolling load fluctuates, the force generated in the horizontal direction is always offset. As a result, the amount of deformation due to the bending of the support frame is always constant. This eliminates gap errors even when the rolling load varies.

The gap adjuster includes a receiving plate, a cotter, and a seat plate that are sandwiched between two parallel surfaces formed between a first axle box and a second axle box and receive a compressive load, and the cotter is disposed on the two surfaces. And a push-pull mechanism that moves in parallel with
The receiving plate is supported so as to be movable only in a direction orthogonal to the two surfaces,
The cotter has a constant gradient in which at least one of sliding surfaces of the receiving plate and the seat plate gradually increases or decreases in height in the moving direction with respect to the two surfaces.
Rolling friction members are respectively sandwiched between the cotter, the receiving plate, and the seat plate, so that the total sliding resistance is set smaller than the component force in the moving direction of the compression load.

  The rolling friction member is a bearing, a roller guide with a retainer, or a ball guide with a retainer.

According to this configuration, since the sliding resistance of the rolling friction member, that is, the rolling friction coefficient is about 0.003 at the maximum, the sliding resistance between the cotter, the receiving plate and the seat plate is about 1/30 to 1/1 of the conventional. It can be greatly reduced to about 100.
As a result, the above-described example is expressed by equations (6) and (7).
Tensile force F1≈0.003 × 10000 + 0.003 × 10000 × 1.0 + 10000 × 0.1 = 30 + 30 + 1000 = 1000 kg (6)
Pushing force F2≈0.003 × 10000 + 0.003 × 10000 × 1.0 + 10000 × 0.1 = 3000 + 3000−1000 = −940 kg (7)

That is, with the configuration of the present invention, the component force in the moving direction of the compression load (1000 kg in the above example) is always sufficiently larger than the friction force (60 kg in the above example). Directional load acts.
Therefore, even if there is a gap such as backlash, the gap is always pressed in the same direction, so the cotter can be moved accurately by the operation of the push-pull mechanism without being affected by the gap, and accurate even during operation. The gap can be adjusted.

  In addition, the pulling force and pressing force required by the push / pull mechanism have a very small sliding resistance, and thus substantially correspond to a component force in the moving direction of the compressive load, and approximately 10% of the compressive load P. Even when the compression load is large, the pushing force is small, and a small output push / pull mechanism is always sufficient. Therefore, the push-pull mechanism can be reduced in size and output.

  Furthermore, even if the tensile force and pressing force required for the push-pull mechanism act on the frame of the device to which the gap adjuster is attached, the tensile force and pressing force are small, so that there is little deformation of the mounting position and precise gap adjustment is possible. Is possible.

According to a preferred embodiment of the present invention, the push-pull mechanism has a self-locking mechanism so as to prevent the movement of the cotter due to a component force in the moving direction of the compression load.
With this configuration, it is possible to prevent the movement of the cotter due to the component force in the moving direction of the compression load without providing a brake mechanism (brake or the like) in the gap adjuster.

  As described above, the roll gap adjusting device of the present invention (1) can accurately move the cotter by the operation of the push-pull mechanism without the influence of the gap even if a gap such as backlash exists in the push-pull mechanism. (2) The force to push and pull is small even when the compression load is large, and a small output push-pull mechanism is always required. (3) The amount of deformation of the frame and axle box is small and constant. Can be held in this manner, and this has excellent effects such as enabling precise gap adjustment.

  Hereinafter, preferred embodiments of the present invention will be described with reference to the drawings. In each figure, common portions are denoted by the same reference numerals, and redundant description is omitted.

  FIG. 1 is an overall side view of the roll gap adjusting device of the present invention, and FIG. 2 is a cross-sectional view taken along the line AA of FIG.

  As shown in FIGS. 1 and 2, the roll gap adjusting device of the present invention includes a first axle box 5 that supports the first roll 3 and a second axle box of the second roll 4 that faces the first axle box 5. 6 and a gap adjuster 10 which is sandwiched between the first axle box 5 and the second axle box 6 and adjusts the gap.

The first roll 3 and the second roll 4 have a gap G therebetween, and the thickness of the target material 9 such as a resin sheet passing between the rolls 3 and 4 is controlled by this gap. In the present invention, the number of rolls is not limited to one pair (two), and may be three or more as long as it has a gap G to be adjusted between them. Further, the target material 9 passing through the gap is not limited to a resin sheet or the like, and may be a rolled material or the like.
In this example, the second axle box 6 is provided separately from the support frame 7. However, the second axle box 6 may be integrated with the support frame 7 as necessary.

The pressing means 30 includes a pressing cylinder 32, a load cell 34, and a pressing force control device 36.
The pressing cylinder 32 is a hydraulic cylinder or a gas pressure cylinder, and presses the first axle box 5 toward the second axle box 6 with a pressing force P <b> 2 in response to a command from the pressing force control device 36.
The load cell 34 is, for example, a strain gauge type force detector, and is sandwiched between the gap adjuster 10 and the second axle box 6 and detects a compressive load P acting on the gap adjuster 10. The mounting position of the load cell 34 is not limited to this position, and may be the upper surface of the gap adjuster 10 or the lower surface of the second axle box 6.

The pressing force control device 36 is a sequence controller, a computer, or a dedicated controller, and controls the pressing force P2 of the pressing cylinder 32 so as to hold the compression load P detected by the load cell 34 constant.
In this figure, 37a is an A / D converter that converts a load signal (analog) into a digital signal, and 37b is a D / A converter that converts a digital signal into a load signal (analog). These converters can be omitted if necessary.

With the above-described configuration, in the expression (5), the compression load P acting on the gap adjuster 10 is detected by the load cell 34, and the pressing cylinder 32 is pressed by the pressing force control device 36 so as to keep the compression load P constant. The force P2 can be controlled.
Therefore, the compressive load P acting on the gap adjuster 10 is kept constant even if the supporting force P1 of the rolling load fluctuates, and the deformation amount of the axle boxes 5 and 6 and the horizontal force by the push-pull mechanism are kept constant, The deformation amount of the support frame 7 and the axle boxes 5 and 6 can be kept small and constant, thereby enabling precise gap adjustment.
Even if the rolling load fluctuates, the force generated in the horizontal direction is always offset. As a result, the amount of deformation due to the bending of the support frame is always constant. This eliminates gap errors even when the rolling load varies.

FIG. 3A is a diagram showing a first embodiment of the gap adjuster in FIG. In this figure, a gap adjuster 10 includes a receiving plate 12 and a cotter 14 which are sandwiched between two parallel surfaces 1 and 2 formed between a first axle box 5 and a second axle box 6 and receive a compressive load. And a seat plate 16 and a push-pull mechanism 20 for moving the cotter 14 parallel to the two surfaces 1 and 2.
In this example, the two surfaces 1 and 2 are horizontal surfaces, and the moving direction of the cotter 14 is the horizontal left-right direction in the figure. However, the present invention is not limited to this, and the two planes 1 and 2 may be vertical planes other than horizontal and inclined planes. The case where the two surfaces 1 and 2 are horizontal surfaces will be described below unless otherwise specified.

The receiving plate 12 has a horizontal upper surface 12a that directly receives a compressive load P acting downward in the drawing from the surface 1, and left and right vertical outer surfaces 12b. In this example, the seat plate 16 is formed integrally with the main body 17. Note that the seat plate 16 and the main body 17 may be separately configured and integrally connected with a bolt or the like. The seat plate 16 and the main body 17 are preferably fixed to the horizontal lower surface 2 with bolts or the like (not shown).
The main body 17 has a through-hole 17a in the upper part, and the receiving plate 12 is fitted into this hole, and guides the vertical outer surface 12b to support the receiving plate 12 so as to be movable only in the vertical direction. Note that the support / guide means is not limited to this example, and other means (for example, a sliding key, a linear guide, etc.) as long as the support plate 12 is guided in a direction orthogonal to the two surfaces 1 and 2. But you can.

In this example, the cotter 14 has a tapered surface 14a whose height gradually decreases in the right direction in the figure on the upper surface, and the lower surface 14b is formed horizontally. Correspondingly, the lower surface 12c of the receiving plate 12 is also formed with the same gradient θ as the tapered surface 14a, and the upper surface 16a of the seat plate 16 is formed horizontally.
The configuration of the cotter is not limited to this example, and at least one of the sliding surfaces of the receiving plate and the seat plate has a certain gradient that gradually increases or decreases in height in the moving direction with respect to the two surfaces 1 and 2. If you do.

The gap adjuster 10 further includes a rolling friction member 18 (in this example, a linear roller bearing) between the cotter 14 and the receiving plate 12 and the seat plate 16. As other rolling friction members, other types of bearings, a roller guide with a retainer, or a ball guide with a retainer may be used.
In this example, the linear roller bearing 18 has a structure in which a cylindrical roller can circulate inside the main body, and the main body is fixed to predetermined positions of the receiving plate 12 and the seat plate 16 by mounting brackets (bolts or the like) not shown. Has been.
The main body of the linear roller bearing 18 may be fixed to one or both of the upper and lower surfaces of the cotter 14.

The push / pull mechanism 20 is, for example, a bolt having a self-locking function in a screw spiral groove and a screw hole that is screwed with the bolt, and has a function of moving the cotter 14 parallel to the two surfaces 1 and 2 and a movement of the cotter. And a self-locking mechanism for preventing. The movable part (rod or the like) of the push-pull mechanism 20 and the cotter 14 are connected by, for example, a pin 21 or the like.
The push-pull mechanism 20 is not limited to this example, and may be a screw jack, a combination of a servo motor and a screw screw, a linear motion cylinder, or the like.

  With the configuration described above, the rolling friction coefficient of the linear roller bearing 18 is about 0.003 at the maximum, so that the sliding resistance between the cotter 14, the receiving plate 12 and the seat plate 16 can be greatly reduced.

FIG. 3B is a diagram showing the balance of loads in the cotter of FIG. This figure is substantially the same as FIG. 4 described above, but differs greatly in that the friction coefficient μ is about 0.003 at the maximum in the present invention, compared to about 0.1 to 0.4 in the prior art. .
Accordingly, the term including the friction coefficient μ in the above-described equations (1) and (2) is about 1/30 to 1/100 of the conventional value, which is very small and can be ignored. 9) holds.
Tensile force F1 ≒ + Psinθcosθ (8)
Pushing force F2 ≒ -Psinθcosθ (9)

  That is, with this configuration, the component force (Psin θ cos θ) in the moving direction of the compression load P is always sufficiently larger than the frictional force, and therefore the load in the same direction (leftward in the figure) always acts on the push-pull mechanism. Therefore, even if there is a gap between the pin 21 and the backlash in the push-pull mechanism, the gap is always pressed in the same direction. Therefore, the push-pull mechanism can be operated accurately without the influence of the gap. Can move.

  In addition, the pulling force and pressing force required by the push / pull mechanism have a very small sliding resistance, and thus substantially correspond to a component force in the moving direction of the compressive load, and approximately 10% of the compressive load P. Even when the compression load is large, the pushing force is small, and a small output push / pull mechanism is always sufficient. Therefore, the push-pull mechanism can be reduced in size and output.

  Furthermore, even if the tensile force and pressing force required for the push-pull mechanism act on the frame of the device to which the gap adjuster is attached, the tensile force and pressing force are small, so that the mounting position is not deformed and precise gap adjustment is possible. Is possible.

FIG. 4A is a diagram illustrating a second embodiment of the gap adjuster. In this figure, a gap adjuster 10 according to the present invention includes a receiving plate 12, a cotter 14 and a seat plate 16 which are sandwiched between two parallel surfaces 1 and 2 and receive a compressive load, and the cotter 14 has two surfaces 1 and 2. And a push-pull mechanism 20 that moves in parallel with the actuator.
In this example, the cotter 14 has a tapered surface 14a whose height gradually increases in the right direction in the figure on the upper surface. Further, in this example, the push-pull mechanism 20 is a bolt and a screw hole screwed into the bolt.

Further, in this example, the bearing 18 is formed by arranging cylindrical rollers at regular intervals with a cage, and is sandwiched without being fixed at predetermined positions of the receiving plate 12 and the seat plate 16.
Further, in this example, the gap adjuster of the present invention includes an urging device 22 that urges the cotter 14 in the moving direction (right direction in this figure) in order to compensate for the decrease in the component force in the moving direction of the compression load. . In this example, the urging device 22 is a compression spring that presses the cotter 14 in the right direction, but may be a tension spring that pulls the cotter 14 in the right direction on the opposite side, or may be a pneumatic cylinder or a hydraulic cylinder.
That is, the urging force by the urging device 22 is set to be the same as the direction of the component force in the moving direction of the compression load. Further, the urging force F by the urging device 22 is set to be larger than the total sliding resistance.
Other structures are similar to those in FIG.

FIG. 4B is a diagram showing the balance of loads in the cotter of the second embodiment. This figure is substantially the same as FIG. 1B described above, but differs in that the upper surface of the cotter 14 is a tapered surface 14a that gradually increases in the right direction in the figure.
The term including the friction coefficient μ in the above-described equations (1) and (2) is about 1/30 to 1/100 of the conventional one and is very small, so this can be ignored, and the equations (10) and (11 ) Holds. Here, F is a rightward biasing force by the biasing device 22.
Tensile force F1 ≒ -Psinθcosθ-F (10)
Pushing force F2≈ + Psinθcosθ + F (11)

With the above-described configuration, the component force (Psin θ cos θ) in the moving direction of the compression load P is always sufficiently larger than the frictional force. Therefore, a load in the same direction (leftward in the drawing) always acts on the push-pull mechanism. Accordingly, even if there is a gap such as a backlash in the push-pull mechanism, the gap is always pressed in the same direction, so that the cotter can be accurately moved by the operation of the push-pull mechanism without the influence of the gap.
In addition, the configuration including the urging device 22 always sets the “component force in the moving direction of the compressive load + the urging force” to be sufficiently larger than the frictional force even when the compressive load decreases due to the mounting direction and the characteristics of the mounting device. Even if there is a gap such as backlash, the cotter can be accurately moved by the operation of the push-pull mechanism without the influence of the gap.

  In addition, this invention is not limited to the Example and embodiment mentioned above, Of course, it can change variously in the range which does not deviate from the summary of this invention. For example, you may provide a taper surface only in the lower surface of a cotter, or both upper and lower surfaces.

1 is an overall side view of a roll gap adjusting device of the present invention. It is sectional drawing in the AA of FIG. It is a 1st embodiment figure of a gap adjuster. It is a 2nd embodiment figure of a gap regulator. It is a figure which shows the balance of the load in a cotter. 1 is a configuration diagram of a “roll gap adjusting device” in Patent Document 1. FIG. FIG. 2 is a configuration diagram of a “thermoplastic sheet thickness automatic changing device” of Patent Document 2.

Explanation of symbols

1st, 2nd, 3rd roll, 4th roll,
5 First axle box, 6 Second axle box, 7 Support frame, 9 Target material,
10 gap adjuster, 12 backing plate,
12a upper surface, 12b vertical outer surface, 12c lower surface,
14 cotters, 14a taper surface, 14b bottom surface,
16 seat plate, 17 body, 17a through hole,
18 Rolling friction member (linear roller bearing),
20 push-pull mechanism, 21 pin, 22 biasing device,
30 pressing means, 32 pressing cylinder, 34 load cell,
36 Pushing force control device, 37a A / D converter, 37b D / A converter

Claims (5)

  A first axle box that supports the first roll; pressing means that presses the first axle box toward the second axle box of the second roll that faces the first axle box; and between the first axle box and the second axle box. A roll gap adjusting device comprising: a gap adjuster that is pinched and adjusts the gap.   The pressing means is detected by controlling a pressing cylinder that presses the first axle box toward the second axle box, a load cell that detects a compressive load acting on the gap adjuster, and a pressing force of the pressing cylinder. The roll gap adjusting device according to claim 1, comprising a pressing force control device that holds a compressive load constant. The gap adjuster includes a receiving plate, a cotter, and a seat plate that are sandwiched between two parallel planes formed between a first axle box and a second axle box and receive the compressive load; And a push-pull mechanism that moves in parallel with
The receiving plate is supported so as to be movable only in a direction orthogonal to the two surfaces,
The cotter has a constant gradient in which at least one of sliding surfaces of the receiving plate and the seat plate gradually increases or decreases in height in the moving direction with respect to the two surfaces.
The rolling friction member is sandwiched between the cotter, the receiving plate, and the seat plate, respectively, so that the total sliding resistance is set to be smaller than the component force in the moving direction of the compression load. The roll gap adjusting device according to 1.     The roll clearance adjusting device according to claim 3, wherein the rolling friction member is a bearing, a roller guide with a retainer, or a ball guide with a retainer. 4. The roll gap adjusting device according to claim 3, wherein the push-pull mechanism has a self-locking mechanism so as to prevent the movement of the cotter due to a component force in the moving direction of the compressive load.

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