TWI501822B - Ironing apparatus - Google Patents

Description

Pressing device

The present invention relates to an ironing apparatus for pressing a metal foil body against a take-up roll when the rolled metal foil body is taken up by a take-up roll.

The pressing device is provided to maintain the good quality of the metal foil wound on the take-up reel. When the metal foil body is wound up on the take-up roll, if the metal foil body is not pressed against the take-up roll, the metal foil body tends to be wound up in a state in which air is caught between the take-up rolls. Due to the entrapment of the air, the metal foil may be offset in its width direction. Therefore, the metal foil body is pressed against the take-up roller by the pressing means, whereby air is not caught between the winding roller and the metal foil body can be stably wound up. As a result, the good quality of the wound metal foil can be maintained.

An example of the configuration of the pressing device will be described with reference to FIGS. 1A and 1B. In FIG. 1A, the pressing device includes a cylinder device 31, a rocking arm portion 33, and a pressing roller 35. The rocking arm portion 33 is swung in the direction of the arrow in the drawing by the expansion and contraction operation of the cylinder device 31. A pressing roller 35 is attached to the rocking arm portion 33. The pressing roller 35 has its central axis arranged in parallel with the central axis of the winding roller 37. The pressing roller 35 presses the metal foil 1 against the take-up roller 37 by shaking the arm portion 33.

The pressing device as described above is described in, for example, Patent Document 1 below.

(previous technical literature) (Patent Literature)

Patent Document 1: Japanese Laid-Open Patent Publication No. 2004-136302

Even if the wound material 1a is increased in diameter, it is desirable to maintain the good quality of the wound metal foil.

For example, when the size of the wound material 1a (the outer diameter of the wound material) forming the wound metal foil body 1 is changed from the state of Fig. 1A to the state of Fig. 1B, the pressing roller 35 is in contact with the metal foil body. The circumferential distance of the position a (refer to the drawing) of the 1 and the winding position b (refer to the drawing) (that is, the distance around the central axis of the take-up roller 37) will be from an ideal position for preventing the above-mentioned air from being caught ( For example 20mm) offset. As a result, the shape of the wound 1a formed by the wound metal foil 1 may become unstable.

In this case, even if the wound material 1a is increased in diameter, the shape of the wound material does not become unstable by suppressing the change in the circumferential direction distance, and the metal foil body can be stably wound up, thereby maintaining Good quality of the coil 1a.

Further, in another example, once the winding amount of the wound material 1a is large, the direction of the cylinder device 31 is greatly different between the start of winding and the end of winding. As a result, the direction of the pressing force generated by the cylinder device 31 largely fluctuates, and the pressing of the metal foil body 1 with respect to the take-up roller 37 may become unstable.

In this case, even if the wound material 1a is increased in diameter, the shape of the wound material does not become unstable by reducing the fluctuation in the direction of the pressing force generated by the cylinder device 31, thereby maintaining the shape of the wound material. Good quality of the coil 1a.

In other words, in the case where the wound material 1a is increased in diameter, a device capable of winding the metal foil more stably than the pressing device having the configuration of the first embodiment is desired.

Accordingly, an object of the present invention is to provide a pressing device which can stably wind up a metal foil body even if the wound material is increased in diameter.

In order to achieve the above object, according to the present invention, there is provided a pressing device which is a pressing device for pressing a rolled metal foil body against a take-up roller when the rolled metal foil body is wound on a take-up roll The method includes a pressing roller that presses the metal foil body in the winding up on the winding roller, a rocking body that is attached to the one end side and that is rotatable around the rocking shaft at the other end portion, and shakes the foregoing a rocking shaft of the body is mounted in a rockable state, and a reciprocating body movable forward and backward with respect to the take-up roller; a driving device for moving the reciprocating body forward and backward relative to the winding roller; and generating a metal foil body a pressing device for pressing the force of the take-up roller; wherein the pressing device applies a force to the rocking body, and the rocking body is rocked toward the winding roller side, whereby the metal foil body is pressed via the pressing roller attached to the rocking body Press on the take-up roll.

According to a preferred embodiment of the present invention, the pressing device includes: a size sensor that detects a size of a wound body formed by winding a metal foil body of the winding roller; and detects a position of the reciprocating body a position sensor; and a control device for controlling the driving device according to the detected value of the size sensor, the detected value of the position sensor, and a preset operation mode, wherein the action mode is for the take-up object Each size determines the position of the reciprocating body.

According to a preferred embodiment of the present invention, the pressing device is a cylinder device having a cylinder and a piston, and the piston rod can be extended and retracted by the reciprocating operation of the piston, and one of the cylinder and the piston rod Rotatingly coupled to one end side of the rocking body, the other of the cylinder and the piston rod is rotatably coupled to the reciprocating body, thereby being supplied to the piston rod side cylinder chamber and the rod of the cylinder The fluid pressure of at least one of the head-side cylinder chambers is urged in a direction in which the swinging body is swung toward the winding roller side, and the operation mode is set such that the piston rod of the cylinder device does not elongate and continues Retreat.

According to still another preferred embodiment of the present invention, the operation mode is set such that a change in the distance between the position where the pressing roller contacts the metal foil body and the winding position is suppressed, and the winding position is taken up by the pressing roller. The intersection of the metal foil body and the metal foil body to be wound later.

According to a preferred embodiment of the present invention, the pressing device further includes: a force sensor that detects a force generated by the pressing device, wherein the control device is based on a detected value of the force sensor, and the size sense The detection value of the detector and the pressing force mode set in advance are used to control the pressing device, and the component of the pressing force from the position where the pressing roller applies the pressing force to the metal foil body toward the central axis of the winding roller is set as the center. The directional component, the pressing force mode is such that the center direction component is fixed regardless of the size of the wound material, and the force generated by the pressing device is determined for each size of the wound material.

According to the above aspect of the invention, since the reciprocating body mounts the oscillating body in a swingable state, and the urging means oscillates the oscillating body toward the take-up roller side to press the pressing roller against the take-up roller, by reciprocating The reciprocating motion of the body can adjust the position of the pressing roller or the shaking of the rocking body, whereby the metal foil body can be stably wound up even if the wound material is increased in diameter.

For example, since the pressing means applies a force to the rocking body, the rocking body is rocked toward the winding roller side, whereby the pressing roller is pressed against the metal foil body. At this time, the shaking body is shaken up to the amount corresponding to the position of the reciprocating body, and therefore, as long as the position of the reciprocating body is changed, the contact position of the pressing roller contact at the metal foil body (the pressing position toward the metal foil body) also changes. . Therefore, the adjustable range of the contact position becomes large. As a result, even if the wound material is increased in diameter, the metal foil body can be stably wound up.

Further, in another example, by adjusting the position of the reciprocating body, the rocking angle of the rocking body is adjusted, and the fluctuation of the direction of the pressing force generated by the pressing device can be suppressed. As a result, even if the wound material is increased in diameter, the metal foil body can be stably wound up.

The effects of the embodiments of the present invention will be described in detail below.

Embodiments of the present invention will be described based on the drawings. In addition, the same portions in the respective drawings are denoted by the same reference numerals, and the repeated description is omitted.

Fig. 2 is a view showing an example of the configuration of the pressing device 10 according to the embodiment of the present invention. The pressing device 10 is a device that presses the metal foil 1 being wound up against the winding roller 3 when the rolled metal foil 1 such as aluminum is taken up by the winding roller 3 . Fig. 3 is a view showing the configuration of the pressing device 10 according to the embodiment of the present invention. Fig. 2 shows a state in which the metal foil body 1 starts to be taken up by the take-up roll 3, and Fig. 3 shows a state in which the metal foil body 1 is taken up to the take-up roll 3 to some extent. The metal foil body 1 taken up by the take-up roll 3 may also be a metal foil body (for example, a thickness of 0.01 mm to 0.5 mm) rolled by a rough rolling mill, or a metal foil body rolled by a finish rolling mill. (for example, thickness 0.01 to 0.03 mm) and the like. Further, reference numeral 6 in FIGS. 2 and 3 is a guide roller that supports and guides the metal foil body 1.

The pressing device 10 includes a pressing roller 5, a rocking body 7, a reciprocating body 9, a driving device 11, a pressing device 13, a size sensor 15, a position sensor 17, a control device 29, and a force sensor 21.

The pressing roller 5 presses the metal foil 1 that is being wound up on the take-up roller 3 against the take-up roller 3. The pressing roller 5 is disposed such that its central axis C _{r is} parallel to the central axis C _{1 of the} take-up reel 3 . The pressing roller 5 is formed by pressing the metal foil 1 wound around the take-up roller 3 against the take-up roller 3 to prevent the air of the metal foil 1 from being caught, thereby stabilizing the winding of the metal foil 1. Further, in FIG. 2, the axes _{C 1, C 2, C 3} , C 4, C _r lines toward the direction perpendicular to the paper extends.

In the rocking body 7, the pressing roller 5 is attached to one end side. The pressing roller 5 is rotatable around its central axis C _r in a state of being attached to the rocking body 7.

In the reciprocating member 9, the other end portion of the rocker body 7 mounted to the state of the system around the pivot axis C ₂ at shaking. Preferably, the reciprocating body 9 is supported to reciprocate toward the guide rail 12 and to guide the reciprocating motion along the guide rail 12.

The driving device 11 moves the reciprocating body 9 forward and backward with respect to the take-up roller 3. Here, the front side is a position close to the take-up roll 3, and the rear side is a position away from the take-up roll 3.

The front and rear movements are in the direction of the guide rail 12 in the example of Fig. 2. In this example, the drive unit 11 has a cylinder 11a and a piston 11f, and a cylinder device that can expand and retract the piston rod 11d by the reciprocation of the piston 11f. In this case, one of the cylinder 11a and the piston rod 11d (the distal end portion of the piston rod 11d described later in the second drawing) is coupled to the reciprocating body 9, the other of the cylinder 11a and the piston rod 11d (the In the example of Fig. 2, the cylinder 11a) is fixed to the reference body 23.

The reference body 23 is a stationary support structure. In this configuration, the fluid pressure (the hydraulic pressure or the air pressure such as the hydraulic pressure) supplied to at least one of the piston rod side cylinder chamber 11a-2 and the head side cylinder chamber 11a-1 of the cylinder 11a is the same as the following. The cylinder device 11 is expanded and contracted to move the reciprocating body 9 forward and backward with respect to the take-up roller 3. The driving device 11 is preferably a hydraulic cylinder device as in the example of Fig. 2 or an embodiment to be described later. The hydraulic cylinder device will be described in detail in an embodiment to be described later.

The pressing device 13 generates a force for pressing the metal foil body 1 against the take-up roller 3. The pressing device 13 is a direction in which the rocking body 7 is swung toward the winding roller 3, and a force is applied to the rocking body 7, whereby the metal foil body 1 is pressed against the winding by the pressing roller 5 attached to the rocking body 7. Roller 3.

The pressing device 13 is a cylinder device having a cylinder 13a and a piston 14 in this example, and the piston rod 13g is extended and retracted by the reciprocation of the piston 14. In this case, one of the cylinder and the piston rod 13a of 13g (FIG. 2 of the second embodiment for the rod end portion 13g) is in the other end of the rocker body 7 may be combined into rotation around the rotation axis C _3, cylinder member 13a and the other of the piston rod 13g (Example 2 as the cylinder of FIG. 13a) is incorporated in the reciprocating member 9 to be rotatable about the rotation axis C _4. In this configuration, the fluid pressure (the hydraulic pressure or the air pressure such as the hydraulic pressure) supplied to at least one of the piston rod side cylinder chamber 13a-2 and the head side cylinder chamber 13a-1 of the cylinder 13a is the same as the following. The rocking body 7 is urged toward the direction in which the rocking body 7 is swung toward the winding roller 3 side.

The pressing device 13 is preferably an oil air cylinder device as in the example of Fig. 2 or an embodiment to be described later. The oil air cylinder device will be described in detail in the embodiments to be described later.

The size sensor 15 is a size for detecting the take-up 1a formed by the metal foil 1 wound up on the take-up roll 3.

For example, the size sensor 15 may be a well-known sensor that detects the position of the outer surface of the take-up object 1a (hereinafter referred to as the outer surface position) (for example, optically detecting the take-up object 1a in a non-contact manner) Sensor on the outer surface). In this case, the detected outer surface position may be output to the control device 19 as the size detection value of the take-up object 1a, or the detected outer surface position may be converted into the center of the take-up object 1a. (that is, the distance from the central axis C _{1 of the} take-up roller 3) to the outer surface of the take-up 1a (hereinafter referred to as the radius size), and the radius size is output to the control device as the size detection value of the take-up object 1a. 19.

The size sensor 15 of another example may measure the number of rotations of the take-up roll 3 when the metal foil body 1 is taken up by the take-up roll 3. In this case, the size sensor 15 can also calculate the outer surface position or radius size based on the number of rotations of the take-up roll 3, the known thickness of the metal foil body 1, and the known size of the take-up roll 3, and This calculated value is output to the control device 19 as the size detection value of the wound object 1a.

The position sensor 19 detects the position of the reciprocating body 9. The position sensor 17 is an optical ruler in the example of Fig. 2, but may be other suitable means.

The control device 19 is controlled based on the detected value of the size sensor 15 (i.e., the size detection value), the detected value of the position sensor 17 (i.e., the position of the reciprocating body 9), and a preset operation mode. Drive device 11. This operation mode determines the position of the reciprocating body 9 for each size of the take-up object 1a. Thereby, the control device 19 controls the drive device 11 so that the operation of the reciprocating body 9 follows the operation mode (described later).

Preferably, the above operation mode is to use the following first or second operation mode.

In the first operation mode, the reciprocating body 9 is set such that the piston rod 13g of the pressing device 13 (i.e., the cylinder device) does not elongate when the winding of the metal foil 1 is started by the winding roller 3 until the winding is completed. And will continue to retreat. According to the first operation mode, the control device 19 is caused to control the drive device 11, and the piston rod 13g of the pressing device 13 is constantly retracted from the start of winding to the end of winding.

Thereby, as described below, fluctuations in the pressing force of the metal foil body 1 by the pressing roller 5 can be suppressed. As the size of the take-up material increases, the piston rod 13g of the urging means 13 can often continue to retract. Therefore, the operating direction of the piston rod 13g of the pressing device 13 is not temporarily reversed. As a result, the pressing force generated by the pressing device 13 and the direction of the mechanical frictional force of the pressing device 13 do not reverse and change. Therefore, it is possible to suppress the pressing force of the pressing roller 5 with respect to the metal foil body 1 from fluctuating due to such a change in the pressing force and the frictional force.

The second operation mode is set to prevent the pressing roller 5 from contacting the circumference of the outer surface of the wound 1a at the position a (see FIG. 3) and the winding position b (see FIG. 3) of the metal foil body 1. The directional distance (i.e., the distance around the central axis C _{1 of the} take-up reel 3) fluctuates from the start of the winding to the end of the winding. Preferably, the second operation mode is set such that the circumferential distance is constant from the time of winding up by the take-up reel 3 to the end of winding, or the circumferential distance is as constant as possible. For example, the second operation mode is set such that the circumferential distance from the start of the winding to the end of the winding is in the range of 0 to 20 mm.

Further, the winding position b is a boundary position of the metal foil 1 that has been taken up by the pressing roller 5 and the metal foil 1 to be wound later, as shown in Fig. 3 .

According to the second operation mode, the control device 19 is caused to control the drive device 11, and the circumferential distance is suppressed from fluctuating from the start of winding to the end of winding. Preferably, the circumferential distance is maintained substantially constant from the start of winding to the end of winding, or within a minimum range of variation.

Thereby, the pressing position of the pressing roller 5 with respect to the metal foil body 1 (that is, the position a of FIG. 3) can be maintained in a desired range (for example, the circumferential distance is in the range of 0 to 20 mm). If the pressing position is too far from the winding position b, the air entrapment of the metal foil body 1 cannot be prevented. Therefore, even when the size of the wound 1a is greatly increased from the start of winding up to the end of winding, the pressing position of the pressing roller 5 can be maintained in a desired range for preventing air from being caught in accordance with the second operation mode. Therefore, the air entrapment of the metal foil body 1 can be prevented to achieve stable winding.

In addition, the first and second operation modes cannot be realized at the same time. When the distance in the circumferential direction is controlled to be constant, the operation direction of the pressing device 13 is reversed during winding. Therefore, the first and second operation modes cannot be realized at the same time, so it is necessary to select either of these two modes.

In addition, in any of the first and second operation modes, the fluctuation in the direction of the pressing force (the force F1 to be described later) generated by the pressing device 13 can be further suppressed as compared with the case of the first embodiment.

The force sensor 21 detects the force generated by the pressing device 13 (in this example, the force F ₁ of the pressing device 13 pressing the rocking body 7 (see FIG. 4)). In this case, the control device 19 preferably controls the pressing device 13 based on the detected value of the force sensor 21 (for example, F ₁ ), the detected value of the size sensor 15, and a preset pressing force mode. . The pressing force mode is determined based on the center direction component F ₂ shown in Fig. 4 . The center direction of the F ₂ component is a take-up roller 3 in the direction of the central axis C ₁ of the urging force component F ₃ F ₃ position of the pressing force from the pressing roller 5 of the metal foil member. The pressing force mode determines the force generated by the pressing device 13 for each size of the wound material 1a in such a manner that the center direction component F _{2 is} constant regardless of the size of the wound material 1a (in this case, pushing) The device 13 pushes the force F ₁ ) of the rocking body 7.

In other words, the position of the rocking axis C ₂ and the position a of the tangent of the pressing roller 5 and the take-up material 1a are determined from the size and operation mode of the wound material 1a at each time point (see FIGS. 3 and 4). From these positions, the relationship between F ₁ and F ₂ is determined by the following formula (1) of [Formula 1]. Therefore, the size of F ₂ is set to a predetermined value in advance, so that the predetermined value is constant regardless of the size of the take-up object 1a, and the respective sizes of the take-up object 1a are calculated according to the operation mode and the equation (1). The size of F ₁ is out. In this way, the magnitude of F ₁ calculated from each size of the take-up 1a can be used as the pressing mode.

Thereby, the control device 19 controls the pressing device 13 such that the pressing force F1 generated by the pressing device 13 follows the pressing force mode.

[Math 1]

According to Fig. 4, the symbols in the equation (1) are defined as follows. In Fig. 4, each member is indicated by a thin broken line.

F ₁ is the force at which the pressing device 13 acts on the rocking body 7. F ₁ is represented by a moment in Fig. 4, and its starting point is the rotation axis C ₃ .

F ₂ is a location of a pressing force from the pressing roller 5 to the metal foil member F ₃ 3 towards the center of the take-up roller axis C ₁ of the component of the pushing force F _3. F ₂ is represented by a moment in Fig. 4, and its starting point is position a. F ₃ is represented by a moment in Fig. 4, and its starting point is position a.

L ₁ is the distance between the plane P ₁ and the plane P ₂ . The plane P ₁ is indicated by a thick broken line in Fig. 4, and includes a moment F ₁ of the force acting on the rocking body 7 by the pressing means 13, and is a plane parallel to the central axis C _{1 of the} winding roller 3. The plane P ₂ is indicated by a thick broken line in Fig. 4 and is parallel to the plane P ₁ and contains a plane of the rocking axis C ₂ .

L ₂ is the distance between the plane P ₃ and the plane P ₂ . The plane P ₃ is parallel to the plane P ₁ and includes a plane of the contact line a between the pressing roller 5 and the metal foil 1 (that is, the position a of the second drawing and the fourth drawing). A contact line extending in the direction of the paper surface in FIG. 4 vertically, as described above, the pressing roller 5 is equivalent to a force F ₃ in the acting position of the metal foil 1.

W is the center of gravity of the pressing roller 5 and the object 7 integral swinging G as a starting point, the weight of the component 5 and the swing moment of the body 7 and the direction of the plane P ₁ parallel to the pressing roller. W is represented by a moment in Fig. 4, and its starting point is the center of gravity G.

L ₃ is the distance between the plane P ₂ and the plane P ₄ . The plane P ₄ contains a moment W and is parallel to the plane P ₁ .

α is an angle formed by the moment F ₂ and the moment F ₂ , and is an angle formed by a plane including the central axis C ₁ and the tangent a of the take-up reel 3 and the plane P ₃ described above.

Fig. 5 is a V-V arrow view of Fig. 2; As shown in Fig. 5, the rocking body 7 and the pressing device 13 are provided on both sides in the axial direction of the pressing roller 5. Therefore, the control device 19 controls the pair of pressing devices 13 in synchronization with each other in the above-described manner.

According to the above-described pressing device 10, by expanding the adjustable range in which the pressing roller 5 contacts the position a of the metal foil body 1 as described below, the metal foil body 1 can be stably wound up even if the winding material 1a is increased in diameter. . The force acts on the rocking body 7 in such a manner that the rocking body 7 is swung toward the winding roller 3 side, and the pressing device 13 can press the pressing roller 5 against the metal foil body 1. At this time, the swinging body 7 is shaken up to the position corresponding to the position of the reciprocating body 9, so that the pressing roller 5 contacts the contact position a of the metal foil body 1 as long as the position of the reciprocating body 9 fluctuates (for the metal foil body 1) The pressing position) will also change. Therefore, the adjustable range of the contact position a becomes large. As a result, even if the wound material 1a is increased in diameter, the metal foil body 1 can be stably wound up.

(Example)

The embodiment of the present invention will be described, but the points not described below may be the same as those of the above embodiment.

The drive device 11 of the embodiment is a hydraulic cylinder device. In this case, the hydraulic cylinder device 11 has the following configuration and is controlled by the control device 19 in the following manner.

The hydraulic cylinder device 11 has a cylinder 11a, a hydraulic source 11b, a servo valve 11c, and a piston rod 11d as shown in Fig. 2 . A head side cylinder chamber 11a-1 and a piston rod side cylinder chamber 11a-2 are formed inside the cylinder 11a. As shown in Fig. 2, the hydraulic source 11b is connected to the head side cylinder chamber 11a-1 and the piston rod side cylinder chamber 11a-2 by the hydraulic pressure supply pipe 11e. The servo valve 11c is provided in the hydraulic pressure supply pipe 11e for adjusting the hydraulic pressure supplied from the hydraulic pressure source 11b to the head side cylinder chamber 11a-1 and the piston rod side cylinder chamber 11a-2. The piston rod 11d is reciprocated back and forth with respect to the take-up reel 3 by the hydraulic pressure supplied to the head side cylinder chamber 11a-1 and the piston rod side cylinder chamber 11a-2. Here, the front side refers to a position close to the take-up roll 3, and the rear side refers to a position away from the take-up roll 3. The front end of the piston rod 11d is coupled to the reciprocating body 9, whereby the reciprocating body 9 reciprocates integrally with the piston rod 11d.

The control device 19 controls the hydraulic cylinder device based on the detected value of the size sensor 15, the detected value of the position sensor 17, and a predetermined operation mode (preferably, the first or second operational mode). 11. Specifically, the control device 19 controls the servo valve 11c to control the reciprocating body 9 to be detected at each detected value of the size sensor 15 in the operation mode for the size sensor 15 The position of the reciprocating body 9 determined.

The pressing device 13 is an oil air cylinder device. In this case, the oil sump cylinder device 13 has the following configuration and is controlled by the control device 19 in the following manner.

The oil sump cylinder device 13 includes a cylinder 13a, a pneumatic source 13b, servo valves 13c and 13d, a first pneumatic hydraulic converter 13e, a second pneumatic hydraulic converter 13f, and a piston rod (piston) 13g.

A reciprocating cylinder 13a is mounted to the movable member 9 is rotatable around a rotation axis C _4.

The air pressure source 13b is, for example, a compressor, and is connected to the air chambers 13e-1 and 13f-1 of the first and second air pressure hydraulic converters 13e and 13f by the air pressure supply pipe 13h as shown in Fig. 2 .

The servo valve 13c adjusts the air pressure supplied from the air pressure source 13b to the first and second air pressure hydraulic converters 13e and 13f.

The servo valve 13d adjusts the air pressure supplied from the air pressure source 13b to the first air pressure hydraulic converter 13e.

The oil chamber 13e-2 of the first air pressure hydraulic converter 13e is connected to the piston rod side cylinder chamber 13a-2 of the cylinder 13a, and the oil chamber 13f-2 of the second pneumatic oil pressure converter 13f is a cylinder. The head side cylinder chamber 13a-1 of the body 13a is connected.

The supply of the air pressure to the air chambers 13e-1 and 13-f1 in the first and second air-pressure hydraulic converters 13e and 13f is adjusted by the servo valves 13c and 13d to adjust the head side cylinder for the cylinder 13a. The hydraulic pressure is supplied to the body chamber 13a-1 and the piston rod side cylinder chamber 13a-2. Accordingly, the swing member 7 in a direction toward the swing body is mounted to the rotation axis C of the rod ₃ around the take-up roll 7 will 13g 3 thereof swings the rocker body 7 in force, with the result will be mounted via The pressing roller 5 of the rocking body 7 presses the metal foil body 1 against the winding roller 3.

Further, since the oil sump cylinder device 13 has the air pressure hydraulic converters 13e and 13f, even if the impact is received from the metal foil body 1 via the pressing roller 5 and the oscillating body 7, the air pressure hydraulic converter 13e can be used. The air pressure of 13f absorbs the impact. Therefore, even if the winding speed of the take-up roller 3 is increased, vibration is generated, and the pressing roller 5 is subjected to an impact, and the impact can be absorbed.

Further, reference numerals 13e-3 and 13f-3 in Fig. 2 denote pistons of the air pressure hydraulic converters 13e and 13f, respectively.

The control device 19 controls the oil air cylinder device 13 based on the detected value of the force sensor 21, the detected value of the size sensor 15, and a preset pressing force mode. Specifically, the control device 19 pushes the piston rod 13g by the force F1 of the piston rod 13g determined by the detected value for the detected value in the pressing mode according to each detected value of the size sensor 15. The servo valves 13e, 13f are controlled in such a manner that the movable body 7 is pressed.

The force sensor 21 of the example of Fig. 2 is a pressure sensor 21a that detects the pressure in the head side cylinder chamber 13a-1, and detects the pressure in the piston rod side cylinder chamber 13a-2. The pressure sensor 21b is constructed. 19 is a control means to control the servo valve 13c, 13d in accordance with the pressure sensor 21a, 21b of the detection value, the pressing force F ₁ so that the pressing force to follow the pattern.

Here, the control device 19 controls the servo valve 13d based on the detected value of the pressure sensor 21b, so that the oil pressure in the piston rod side cylinder chamber 13a-2 is maintained at a certain set value while being sensed according to the pressure. The detected value of the device 21a controls the servo valve 13c so that the oil pressure in the head side cylinder chamber 13a-1 follows the pressing mode. In this case, the pressing force mode is expressed by the following formula (2) of [Formula 2], and the control device 19 controls the servo valve 13c based on the detected value of the pressure sensor 21b to cause the head The oil pressure in the side cylinder chamber 13a-1 is Ph which makes the equation (2) into the equation (3) of [Formula 3].

[Math 2]

[Math 3]

In the formulas (2) and (3), the definition of the same symbol as the formula (1) is the same as in the case of the formula (1). The definitions of the new symbols in equations (2) and (3) are as follows.

Ph is the pressure in the head side cylinder chamber 13a-1 of the cylinder 13a.

Pr is the pressure in the piston rod side cylinder chamber 13a-2 of the cylinder 13a, and is a constant set value as described above.

Ah is an area in which the piston 13g receives pressure from the oil in the head side cylinder chamber 13a-1 toward the direction in which it extends.

Ar is an area in which the piston 13g receives pressure from the oil of the piston rod side cylinder chamber 13a-2 toward the retracting direction thereof.

Further, the number "2" in the equations (2) and (3) is that two oil air cylinder devices 13 are provided as shown in Fig. 5.

6A to 6C are graphs showing control according to the first operation mode. Fig. 6A shows the first operation mode, and Fig. 6B and Fig. 6C show the results when the first operation mode according to Fig. 6A is displayed.

The horizontal axis of Fig. 6A shows the size of the wound object, and the vertical axis shows the amount of elongation of the hydraulic cylinder device 11 (the stroke position of the piston rod 11d) as the position of the reciprocating body 9.

Q of Fig. 6B shows the amount of elongation of the oil sump device 13 (the stroke position of the piston rod 13g), and R is the maximum amount of elongation of the sump device 13 (the maximum stroke position of the piston rod 13g). The horizontal axis of Fig. 6B shows the size of the wound, and the vertical axis shows the amount of elongation of the oil cylinder device 13.

Fig. 6C is a view showing the circumferential distance of the pressing position a and the winding position b. The horizontal axis of Fig. 6C shows the size of the wound object, and the vertical axis shows the circumferential distance between the pressing position a and the winding position b.

The first operation mode can be obtained in advance, for example, by the following order (1) to (5).

(1) The retraction speed mode of the plurality of hydraulic cylinder devices 11 is set. Set the retraction speed modes A1, A2, and A3 shown in Fig. 7.

The curve B1 of Fig. 7 is an increase speed pattern showing the size of the take-up object known in advance. The increase in the size of the take-up object is such that the larger the size of the take-up object, the smaller.

The withdrawal speed modes A1, A2, A3 are set so as not to be too far from the mode B1 in Fig. 7. The withdrawal speed patterns A1, A2, and A3 are set to the line graphs in Fig. 7 in order to make the setting simple.

Figure 7 shows the setting of three retraction speed modes, but in fact, most of the retraction speed modes can be set.

(2) When the hydraulic cylinder device 11 is retracted in the retracting speed mode for each of the retracting speed modes A1, A2, and A3, the relationship between the elongation of the hydraulic cylinder device 13 and the size of the wound body is obtained by simulation ( Hereinafter, it is referred to as a telescopic mode of the hydraulic cylinder device 13). The simulation is performed based on the retraction speed mode, the known size of the wrap at each time point, and the geometry and size of the pressing device 10.

(3) From the expansion and contraction mode of the hydraulic cylinder device 13 obtained in the above-described (2) in accordance with each of the retracting speed modes, the expansion mode in which the hydraulic cylinder device 13 is constantly retracted as the size of the wound material increases is selected. .

(4) A line graph (retraction speed mode) of Fig. 7 corresponding to the selected expansion mode is approximated by a curve. Thereby, the operation of the hydraulic cylinder 11 according to the retracting speed mode is smoothed.

(5) The first operation mode shown in Fig. 6(A) is obtained based on the retraction speed mode of the approximate curve and the geometry and size of the pressing device 10 in the above (4).

8A to 8C are graphs showing control according to the second operation mode. Fig. 8A shows the second operation mode, and Fig. 8B and Fig. 8C show the results when the second operation mode following Fig. 8A is displayed.

The horizontal axis of Fig. 8A shows the size of the wound material, and the vertical axis shows the amount of elongation of the hydraulic cylinder device 11 (the stroke position of the piston rod 11d) as the position of the reciprocating body 9.

Q of Fig. 8B shows the amount of elongation of the oil cylinder device 13 (the stroke position of the piston rod 13g), and R is the maximum elongation of the oil cylinder device 13 (the maximum stroke position of the piston rod 13g). The horizontal axis of Fig. 8B shows the size of the wound object, and the vertical axis shows the amount of elongation of the oil cylinder device 13.

Fig. 8C is a view showing the circumferential distance of the pressing position a and the winding position b. The horizontal axis of Fig. 8C shows the size of the wound object, and the vertical axis shows the circumferential distance between the pressing position a and the winding position b.

The second operation mode can be obtained in advance by, for example, the following order (1) to (3).

(1) The above-described constant circumferential distance between the pressing position a and the winding position b is set.

(2) The position of the pressing roller 5 is obtained from each dimension of the wound object based on the set circumferential direction distance.

(3) When the position of the pressing roller 5 is obtained for each size of the wound material, the amount of expansion and contraction of the hydraulic cylinder device 11 is obtained from the position and the geometry and size of the pressing device 10. That is, the second operation mode is obtained.

Further, in the eighth (A) diagram, the second operation mode obtained in this manner is approximated by a polynomial equation. Therefore, in the eighth (C) diagram, the circumferential direction distance slightly varies from a constant value. However, in order to set the circumferential direction distance to a constant value, the second operation mode may not be approximated by a polynomial.

The present invention is not limited to the embodiments described above, and various modifications can be made without departing from the spirit and scope of the invention.

1. . . Metal foil

1a. . . Take up

3. . . Take-up roll

5. . . Press roller

7. . . Shake body

9. . . Reciprocating body

10. . . Pressing device

11. . . Drive unit (hydraulic cylinder unit)

11a, 13a. . . Cylinder block

11a-1, 13a-1. . . Head side cylinder chamber

11a-2, 13a-2. . . Piston rod side cylinder chamber

11b. . . Oil pressure source

11c, 13c, 13d. . . servo valve

11d. . . Piston rod

11e. . . Oil supply pipe

11f. . . piston

12. . . guide

13. . . Pushing device (oil air compressor device)

13b. . . Air pressure source

13e. . . First air pressure oil pressure converter

13e-1, 13f-1. . . Air room

13e-3, 13f-3. . . piston

13f-2. . . Oil room

13f. . . 2nd air pressure oil pressure converter

13g. . . Piston rod

13h. . . Air pressure supply pipe

14. . . piston

15. . . Size sensor

17. . . Position sensor

19. . . Control device

twenty one. . . Force sensor

21a, 21b. . . Pressure sensor

twenty three. . . Reference body

Fig. 1A is a view showing a configuration example of a conventional pressing device having a small outer diameter of the wound material.

Fig. 1B is a view showing an example of the configuration of a conventional pressing device having a large outer diameter of the wound material.

Fig. 2 is a view showing an example of the configuration of a pressing device according to an embodiment of the present invention.

Fig. 3 is a view showing a configuration example of a pressing device according to an embodiment of the present invention, and shows a state in which a coiled metal roll is wound with a certain degree of metal foil.

Fig. 4 is a view showing the positional relationship of each constituent member of the pressing device of Fig. 1.

Fig. 5 is a V-V arrow view of Fig. 2;

Fig. 6A is a graph showing the amount of elongation of the hydraulic cylinder device 11 according to the first operation mode.

Fig. 6B is a graph showing the amount of elongation of the oil cylinder device 13 according to the first operation mode.

Fig. 6C is a graph showing the circumferential distance between the pressing position a and the winding position b according to the first operation mode.

Fig. 7 is a view showing a plurality of retracting speed modes used when the first operation mode is requested.

Fig. 8A is a graph showing the amount of elongation of the hydraulic cylinder device 11 according to the second operation mode.

Fig. 8B is a graph showing the amount of elongation of the oil sump device 13 according to the second operation mode.

Fig. 8C is a graph showing the circumferential distance between the pressing position a and the winding position b according to the second operation mode.

1. . . Metal foil

3. . . Take-up roll

5. . . Press roller

7. . . Shake body

9. . . Reciprocating body

10. . . Pressing device

11. . . Drive unit (hydraulic cylinder unit)

11a, 13a. . . Cylinder block

11a-1, 13a-1. . . Head side cylinder chamber

11a-2, 13a-2. . . Piston rod side cylinder chamber

11b. . . Oil pressure source

11c, 13c, 13d. . . servo valve

11d. . . Piston rod

11e. . . Oil supply pipe

11f. . . piston

12. . . guide

13. . . Pushing device (oil air compressor device)

13b. . . Air pressure source

13e. . . First air pressure oil pressure converter

13e-1, 13f-1. . . Air room

13e-2, 13f-2. . . Oil room

13e-3, 13f-3. . . piston

13f. . . 2nd air pressure oil pressure converter

13g. . . Piston rod

13h. . . Air pressure supply pipe

14. . . piston

15. . . Size sensor

17. . . Position sensor

19. . . Control device

twenty one. . . Force sensor

21a, 21b. . . Pressure sensor

twenty three. . . Reference body

Claims (4)

A pressing device is a pressing device for pressing a rolled metal foil to a take-up roll when the rolled metal foil is wound on a take-up roll, and is characterized in that it is provided in a winding a metal foil body is pressed against a pressing roller of the winding roller; a rocking body is attached to the one end side, and the other end portion is rotatable around the rocking shaft; and the other end portion of the rocking body is mounted to be rockable. And a reciprocating body movable forward and backward with respect to the take-up roller; a driving device for moving the reciprocating body forward and backward with respect to the winding roller; and a pressing force for pressing the metal foil against the take-up roller The pressing device is configured to apply a force to the rocking body, and shake the rocking body toward the winding roller side, thereby pressing the metal foil body against the take-up roller via a pressing roller attached to the rocking body, and the pressing device Further comprising: a size sensor that detects the size of the wound material formed by the metal foil body of the take-up roll; a position sensor that detects the position of the reciprocating body; and a sensor according to the aforementioned size sensor Detected value, the aforementioned position sensor Detection value and the predetermined operation mode control means for controlling the driving device; wherein the operation mode for each line to determine the size of the winding was reciprocally movable body position. The pressing device according to claim 1, wherein the pressing device has a cylinder block and a piston, and a cylinder device capable of extending and retracting the piston rod by reciprocating movement of the piston, the cylinder body and One side of the piston rod is rotatably coupled to one end side of the rocking body, and the other of the cylinder and the piston rod is rotatably coupled to the reciprocating body, thereby being supplied to the piston rod side cylinder of the cylinder The fluid pressure of at least one of the body chamber and the head-side cylinder chamber is urged in a direction in which the swing body is swung toward the take-up roller side, and the operation mode is set such that the piston rod of the cylinder device does not Stretches and continues to retreat. The pressing device according to claim 1, wherein the operation mode is set such that a change in a distance between a position where the pressing roller contacts the metal foil body and the winding position is suppressed, and the winding position is taken up. The boundary position of the metal foil body of the pressing roller and the metal foil body to be wound later. The pressing device according to any one of claims 1 to 3, wherein the pressing device further includes: a force sensor that detects a force generated by the pressing device, wherein the control device is based on a force The detected value of the sensor, the detected value of the size sensor, and a preset pressing force mode are used to control the pressing device, and the pressing force is applied from the pressing roller to the metal foil body toward the center of the winding roller. The component of the pressing force in the direction of the axis is set as the center direction component, and the above-described pressing mode is based on the size of the wound object. The central direction components are all fixed, and the force generated by the above-mentioned pressing device is determined for each size of the wound material.