WO2012096089A1

WO2012096089A1 - Ironing apparatus

Info

Publication number: WO2012096089A1
Application number: PCT/JP2011/078881
Authority: WO
Inventors: 鈴木　勝; 勲手塚; 松村　英夫; 石井　肇; 本城　恒
Original assignee: 株式会社Ihi; Ｉｈｉメタルテック株式会社
Priority date: 2011-01-13
Filing date: 2011-12-14
Publication date: 2012-07-19
Also published as: TWI501822B; TW201235128A; JP5807835B2; CN103347623A; KR20130088894A; KR101615271B1; JP2012143794A; CN103347623B

Abstract

Provided is an ironing apparatus (10) such that when winding a rolled metal foil body (1) onto an uptake roll (3), the metal foil body (1) is pressed onto the uptake roll (3) during the winding. The ironing apparatus is provided with an ironing roll (5) that presses the metal foil body (1) onto the uptake roll (3) during the winding, a shaking body (7) to which the ironing roll (5) is attached on one side, a reciprocating body (9) to which the other end part of the shaking body (7) is attached so as to be shakable, a drive apparatus (11) that moves the reciprocating body (9) back and forth in relation to the uptake roll (3), and a pressing apparatus (13) that generates a force pressing the metal foil body (1) onto the uptake roll (3). The pressing apparatus (13) exerts a force on the shaking body (7) such that the shaking body (7) shakes on the side of the uptake roll, and by this means, the metal foil body (1) is pressed to the uptake roll (3) via the ironing roll (5) attached to the shaking body (7).

Description

Ironing equipment

The present invention relates to an ironing device for pressing a metal foil body onto a winding roll when the rolled metal foil body is wound around the winding roll.

The ironing device is provided in order to maintain the quality of the metal foil wound around the winding roll. If the metal foil body is not pressed against the winding roll when the metal foil body is wound around the winding roll, the metal foil body tends to be wound in a state where air is wound between the winding roll and the metal foil body. This air entrainment may cause the metal foil body to shift in the width direction. Therefore, a metal foil body can be stably wound up, without entraining air between a winding roll by pressing a metal foil body with a winding roll with an ironing apparatus. As a result, the quality of the wound metal foil can be maintained satisfactorily.

A configuration example of the ironing device will be described with reference to FIGS. 1A and 1B. In FIG. 1A, the ironing device includes a cylinder device 31, a swing arm 33, and an ironing roll 35. By the expansion and contraction operation of the cylinder device 31, the swing arm 33 is swung in the direction of the arrow in the figure. An ironing roll 35 is attached to the swing arm 33. The ironing roll 35 is arranged so that the central axis thereof is parallel to the central axis of the winding roll 37. As the swing arm 33 swings, the ironing roll 35 presses the metal foil 1 against the take-up roll 37.

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

JP 2004-136302 A

It is desired that the quality of the wound metal foil body be maintained well even if the coil 1a has a large diameter.

For example, when the dimension (coil outer diameter) of the coil 1a formed by the wound metal foil body 1 increases from the state of FIG. 1A to the state of FIG. 1B, the ironing roll 35 contacts the metal foil body 1. A circumferential distance between the position a (see the drawing) and the winding position b (see the drawing) (that is, the distance around the central axis of the winding roll 37) is a desirable position for preventing the air entrainment (for example, 20 mm). As a result, the shape of the coil 1a formed by the wound metal foil body 1 may become unstable.
For this reason, even if the diameter of the coil 1a is increased, by suppressing the change in the circumferential distance, the coil shape does not become unstable, and the metal foil body can be stably wound up. It is desired to maintain the quality of 1a well.

In another example, when the winding amount of the coil 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 by the cylinder device 31 varies greatly, and the pressing of the metal foil body 1 on the winding roll 37 may become unstable.
For this reason, even if the diameter of the coil 1a is increased, the coil shape does not become unstable by reducing the variation in the direction of the pressing force by the cylinder device 31, thereby improving the quality of the coil 1a. It is desired to maintain it well.

That is, a device capable of winding a metal foil more stably than the ironing device having the configuration shown in FIG. 1 is required in response to an increase in the diameter of the coil 1a.

Therefore, an object of the present invention is to provide an ironing device capable of stably winding a metal foil body even when the coil has a large diameter.

In order to achieve the above object, according to the present invention, when winding a rolled metal foil body around a winding roll, an ironing device for pressing the winding metal foil body against the winding roll,
An ironing roll that presses the metal foil being wound onto the winding roll;
An oscillating body in which an ironing roll is attached to one end side, and the other end can swing around its swinging axis;
A reciprocating body that is swingably attached to a swing shaft of the swing body and is movable back and forth with respect to a winding roll;
A drive device for moving the reciprocating body back and forth with respect to the winding roll; and
A pressing device that generates a force for pressing the metal foil against the take-up roll, and
The pressing device applies a force to the oscillating body so that the oscillating body oscillates on the winding roll side, and thereby presses the metal foil body against the winding roll via an ironing roll attached to the oscillating body. A featured ironing device is provided.

According to a preferred embodiment of the present invention, a dimension sensor for detecting a dimension of a coil formed by a metal foil wound around a winding roll;
A position sensor for detecting the position of the reciprocating body;
A control device that controls the driving device based on a detection value of the dimension sensor, a detection value of the position sensor, and a preset operation pattern;
The operation pattern defines the position of the reciprocating body with respect to each dimension of the coil.

According to a preferred embodiment of the present invention, the pressing device includes a cylinder and a piston, and is a cylinder device capable of extending and retracting a piston rod by reciprocating movement of the piston.
One of the cylinder and the piston rod is rotatably coupled to one end of the oscillating body, and the other of the cylinder and the piston rod is rotatably coupled to the reciprocating body. By the fluid pressure supplied to at least one of the side cylinder chambers, the swinging body is pressed in a direction in which the swinging body swings toward the take-up roll,
The operation pattern is set so that the piston rod of the cylinder device continues to contract without expanding.

According to another preferred embodiment of the present invention, the operation pattern is set to suppress a variation in the distance between the position where the ironing roll contacts the metal foil body and the winding position,
The winding position is a boundary position between the metal foil body that has already been wound around the ironing roll and the metal foil body that is to be wound up.

According to a preferred embodiment of the present invention, it further comprises a force sensor for detecting the force generated by the pressing device,
The control device controls the pressing device based on a detection value of the force sensor, a detection value of the dimension sensor, and a preset pressing force pattern,
The component of the pressing force in the direction from the position where the ironing roll applies the pressing force to the metal foil body toward the central axis of the winding roll is the center direction component,
In the pressing force pattern, the force generated by the pressing device is determined for each dimension of the coil so that the center direction component is constant regardless of the dimension of the coil.

According to the present invention described above, the reciprocating body is attached to the reciprocating body so as to be able to oscillate, and the pressing device swings the oscillating body toward the take-up roll and presses the ironing roll against the take-up roll. Thus, the position of the ironing roll or the swinging of the swinging body can be adjusted, whereby the metal foil body can be stably wound even if the diameter of the coil is increased.

For example, the pressing device presses the ironing roll against the metal foil body by applying a force to the swinging body so that the swinging body swings toward the winding roll. At this time, since the swinging body swings by an amount corresponding to the position of the reciprocating body, if the position of the reciprocating body changes, the contact position (the pressing position to the metal foil body) where the ironing roll contacts the metal foil body is also obtained. change. Therefore, the adjustable range of the contact position is expanded. As a result, the metal foil can be stably wound even if the coil has a large diameter.

In another example, by adjusting the position of the reciprocating body and adjusting the rocking angle of the rocking body, it is possible to suppress fluctuations in the direction of the pressing force generated by the pressing device. As a result, the metal foil can be stably wound even if the coil has a large diameter.

The effect by embodiment of this invention is clarified below.

The structural example of the conventional ironing apparatus with a small coil outer diameter is shown. The structural example of the conventional ironing apparatus with a large coil outer diameter is shown. 1 shows a configuration example of an ironing device according to an embodiment of the present invention. Although the structural example of the ironing apparatus by embodiment of this invention is shown, the winding roll shows the state which wound up the metal foil body to some extent. The positional relationship of each structural member of the ironing apparatus of FIG. 1 is shown. FIG. 5 is a view taken along arrow VV in FIG. 2. It is a graph which shows the expansion | extension amount of the hydraulic cylinder apparatus 11 by a 1st operation pattern. It is a graph which shows the expansion | extension amount of the hydraulic pneumatic cylinder apparatus 13 by a 1st operation | movement pattern. It is a graph which shows the circumferential direction distance of the press position a and the winding position b by a 1st operation pattern. A plurality of degeneration speed patterns used when obtaining the first operation pattern are shown. It is a graph which shows the expansion | extension amount of the hydraulic cylinder apparatus 11 by a 2nd operation | movement pattern. It is a graph which shows the expansion amount of the hydraulic pneumatic cylinder apparatus 13 by a 2nd operation | movement pattern. It is a graph which shows the circumferential direction distance of the press position a and the winding position b by a 2nd operation pattern.

Embodiments of the present invention will be described with reference to the drawings. In addition, the same code | symbol is attached | subjected to the common part in each figure, and the overlapping description is abbreviate | omitted.

FIG. 2 is a configuration example of the ironing device 10 according to the embodiment of the present invention. The ironing device 10 is a device that presses the metal foil body 1 being wound against the winding roll 3 when the rolled metal foil body 1 such as aluminum is wound around the winding roll 3. FIG. 3 is also a configuration diagram of the ironing device 10 according to the embodiment of the present invention. FIG. 2 shows the start of winding of the metal foil body 1 onto the winding roll 3, and FIG. 3 shows a state where the metal foil body 1 is wound up to some extent on the winding roll 3. The metal foil body 1 wound around the winding roll 3 is a metal foil body (for example, a thickness of 0.01 mm to 0.5 mm) that has been rolled by a rough rolling mill, or a metal foil body that has been rolled by a finish rolling mill (for example, And a thickness of 0.01 mm to 0.03 mm). 2 and 3, reference numeral 6 denotes a guide roll that supports and guides the metal foil body 1.

The ironing device 10 includes an ironing roll 5, a rocking body 7, a reciprocating body 9, a driving device 11, a pressing device 13, a dimension sensor 15, a position sensor 17, a control device 19, and a force sensor 21.

The ironing roll 5 presses the metal foil 1 being wound around the winding roll 3 against the winding roll 3. Ironing roll 5, the central axis C _r is parallel to the center axis C ₁ of the winding roll 3. The ironing roll 5 presses the metal foil 1 wound around the take-up roll 3 against the take-up roll 3, thereby preventing air entrainment of the metal foil 1 and stable winding of the metal foil 1. Let In FIG. 2, the axes _{_{_{_{C 1, C 2, C 3}}}} , C 4, C r extends in a direction perpendicular to the paper surface.

The swinging body 7 has an ironing roll 5 attached to one end side. Ironing roll 5, in a state mounted on the oscillator 7, is rotatable on the central axis C _r around.

The reciprocating member 9, the other end portion of the oscillator 7 is swingably attached to the pivot shaft C ₂ around. Preferably, the reciprocating body 9 is supported by the guide rail 12 so as to be reciprocally movable, and the reciprocating motion is guided along the guide rail 12.

The driving device 11 moves the reciprocating body 9 back and forth with respect to the winding roll 3. Here, the front is a position approaching the winding roll 3, and the rear is a position away from the winding roll 3.
This back-and-forth movement is a direction along the guide rail 12 in the example of FIG. In this example, the drive device 11 has a cylinder 11a and a piston 11f, and is a cylinder device capable of extending and retracting the piston rod 11d by reciprocation of the piston 11f. In this case, one of the cylinder 11a and the piston rod 11d (in the example of FIG. 2, the tip of a piston rod 11d described later) is coupled to the reciprocating body 9, and the other of the cylinder 11a and the piston rod 11d (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 cylinder device 11 is controlled by fluid pressure (hydraulic pressure such as hydraulic pressure or pneumatic pressure; the same applies hereinafter) supplied to at least one of the rod side cylinder chamber 11a-2 and the head side cylinder chamber 11a-1 of the cylinder 11a. The reciprocating body 9 is moved back and forth with respect to the winding roll 3. The drive device 11 is preferably a hydraulic cylinder device as in the example of FIG. The hydraulic cylinder device will be described in detail in an embodiment described later.

The pressing device 13 generates a force that presses the metal foil body 1 against the take-up roll 3. The pressing device 13 applies a force to the oscillating body 7 in the direction in which the oscillating body 7 oscillates toward the take-up roll 3, thereby winding the metal foil body 1 via the ironing roll 5 attached to the oscillating body 7. Press against the take-up roll 3.
In this example, the pressing device 13 has a cylinder 13 a and a piston 14, and is a cylinder device capable of extending and retracting the piston rod 13 g by reciprocating movement of the piston 14. In this case, (in the example of FIG. 2, the distal end of the piston rod 13g) one of the cylinder 13a and the piston rod 13g is rotatably coupled to the rotating shaft C ₃ around the other end of the rocking body 7, the cylinder 13a and a piston (in the example of FIG. 2, the cylinder 13a) other rod 13g is rotatably coupled to the rotating shaft C ₄ around the reciprocating member 9. In this configuration, the oscillating body 7 is caused by fluid pressure (hydraulic pressure such as hydraulic pressure or pneumatic pressure; the same applies hereinafter) supplied to at least one of the rod side cylinder chamber 13a-2 and the head side cylinder chamber 13a-1 of the cylinder 13a. The rocking body 7 is pressed in the direction of rocking toward the take-up roll 3 side.
The pressing device 13 is preferably an hydraulic / pneumatic cylinder device as in the example of FIG. The hydraulic / pneumatic cylinder device will be described in detail in an embodiment described later.

The dimension sensor 15 detects the dimension of the coil 1 a formed by the metal foil body 1 wound around the winding roll 3.
For example, the dimension sensor 15 is a known sensor (for example, a sensor that optically detects the outer surface of the coil 1a in a non-contact manner) that detects the position of the outer surface of the coil 1a (hereinafter referred to as the outer surface position). Good. In this case, the detected outer surface position may be output to the control device 19 as a dimension detection value of the coil 1a, or the detected outer surface position may be output to the center of the coil 1a (ie, the central axis C of the winding roll 3). ₁ ) to the distance from the outer surface of the coil 1a (hereinafter referred to as a radial dimension), and the radial dimension may be output to the control device 19 as a detected dimension value of the coil 1a.
As another example, the dimension sensor 15 may measure the number of rotations of the winding roll 3 from the start of winding of the metal foil body 1 by the winding roll 3. In this case, the dimension sensor 15 calculates the outer surface position or the radial dimension based on the number of rotations of the winding roll 3, the known thickness of the metal foil body 1, and the known dimension of the winding roll 3, You may output this calculated value to the control apparatus 19 as a dimension detection value of the coil 1a.

The position sensor 17 detects the position of the reciprocating body 9. The position sensor 17 is an optical linear scale in the example of FIG. 2, but may be other appropriate means.

The control device 19 drives the driving device based on the detection value of the dimension sensor 15 (that is, the dimension detection value), the detection value of the position sensor 17 (that is, the position of the reciprocating body 9), and a preset operation pattern. 11 is controlled. In this operation pattern, the position of the reciprocating body 9 is determined with respect to each dimension of the coil 1a. Thereby, the control device 19 controls the drive device 11 so that the operation of the reciprocating body 9 follows an operation pattern (described later).

The following first or second operation pattern may be used as the operation pattern described above.

In the first operation pattern, the piston rod 13g of the pressing device 13 (that is, the cylinder device) extends from the time when the reciprocating body 9 starts winding the metal foil body 1 by the winding roll 3 to the end of winding. It is set to continue to degenerate without. The control device 19 controls the driving device 11 based on the first operation pattern, so that the piston rod 13g of the pressing device 13 always continues to contract from the start of winding to the end of winding.
Thereby, the fluctuation | variation of the pressing force to the metal foil body 1 by the ironing roll 5 can be suppressed as follows. As the coil size increases, the piston rod 13g of the pressing device 13 can be continuously retracted. Therefore, the operation 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 friction force of the pressing device 13 are not reversed and fluctuated. Therefore, it can suppress that the pressing force with respect to the metal foil body 1 of the ironing roll 5 is fluctuate | varied by such fluctuation | variation of pressing force and frictional force.

The second operation pattern is the circumferential distance along the outer surface of the coil 1a between the position a (see FIG. 3) where the ironing roll 5 contacts the metal foil body 1 and the winding position b (see FIG. 3). (i.e., the center axis C ₁ distance around the take-up roll 3) is in until the completely wound from the time the winding start is set so as to suppress the variation. Preferably, the second operation pattern is set so that the circumferential distance is constant from the start of winding by the winding roll 3 to the end of winding, or the circumferential distance is as constant as possible. . For example, the second operation pattern is set so that the circumferential distance is within the range of 0 to 20 mm from the start of winding to the end of winding.
In addition, the winding position b is a boundary position between the metal foil body 1 that has already been wound around the ironing roll 5 and the metal foil body 1 that is to be wound up, as shown in FIG.
The control device 19 controls the drive device 11 based on the second operation pattern, whereby fluctuations in the circumferential distance are suppressed 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 changes within a minimum variation range.
Thereby, the pressing position of the ironing roll 5 against the metal foil body 1 (that is, the position a in FIG. 3) can be maintained in a desired range (for example, a range in which the circumferential distance is 0 to 20 mm). If this pressing position deviates greatly from the winding position b, it will not be possible to prevent the metal foil body 1 from being caught in the air. Therefore, even if the coil 1a dimension increases greatly from the start of winding to the end of winding, the pressing position of the ironing roll 5 can be maintained within a desirable range for preventing air entrainment by the second operation pattern. Thus, it is possible to prevent the metal foil body 1 from being entrained in air and realize stable winding.

Note that the first and second operation patterns cannot be made compatible. If the circumferential distance is controlled to be constant, the operation direction of the pressing device 13 is reversed during winding. Therefore, since the first and second operation patterns cannot be made compatible, one of these is selected.
Further, in both the first and second operation patterns, variation in the direction of the pressing force (force F ₁ described later) generated by the pressing device 13 can be suppressed as compared with the case of FIG.

The force sensor 21 detects a force generated by the pressing device 13 (in this example, a force F ₁ (see FIG. 4) by which the pressing device 13 presses the oscillating body 7). In this case, the control device 19 preferably controls the pressing device 13 based on the detection value (for example, F ₁ ) of the force sensor 21, the detection value of the dimension sensor 15, and a preset pressing force pattern. Pressing force pattern is determined based on the center direction component F ₂ shown in FIG. The center direction component F ₂ is a component of the pressing force F ₃ in the direction from the position where the ironing roll 5 provides a pressing force F ₃ to the metal foil element 1 to the center axis C ₁ of the winding roll 3. Pressing force pattern, as the center direction component F ₂ becomes constant irrespective of the size of the coil 1a, the force pressing device 13 is generated (in this example, the force F ₁ which the pressing device 13 presses the oscillator 7) Are defined for each dimension of the coil 1a.
That is, the dimensions and operation patterns of the coils 1a at each time point, the position of the pivot shaft C _2, and, ironing roll 5 and the tangent of the position a of the coil 1a (FIG. 3, see FIG. 4) is Sadamari, these From the position, the relationship between F ₁ and F ₂ is determined by the following equation (1). Therefore, the magnitude of F ₂ is set to a predetermined value, and for each dimension of the coil 1a, the predetermined value is constant regardless of the dimension of the coil 1a. keep calculating the magnitude of F _1. Thus, the magnitude of F ₁ calculated for each dimension of the coil 1a can be used as the pressing force pattern.
Thus, the control device 19, the pressing force F ₁ by the pressing device 13 controls the pressing device 13 to follow the pressure pattern.

Each symbol in Formula (1) is defined as follows based on FIG. In FIG. 4, each member is indicated by a thin broken line.
F ₁ is a force that the pressing device 13 acts on the rocking body 7. F ₁ is indicated by a vector in FIG. 4, and its starting point is the rotation axis C ₃ .
F ₂ is a component of the pressing force F _{3 in} the direction from the position where the ironing roll 5 applies the pressing force F ₃ to the metal foil body 1 toward the central axis C ₁ of the winding roll 3. F ₂ is indicated by a vector in FIG. 4, and its starting point is position a. F ₃ is indicated by a vector in FIG. 4, and its starting point is the 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 force vector F ₁ that the pressing device 13 acts on the oscillator 7 and is a plane parallel to the central axis C ₁ of the winding roll 3. is there. The plane P ₂ is indicated by a thick broken line in FIG. 4, is a plane parallel to the plane P ₁ and including the swing 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 contact line a (that is, a position a in FIGS. 2 and 4) between the ironing roll 5 and the metal foil body 1. Contact line a extends in the direction perpendicular to the paper in FIG. 4, as described above, corresponds to the position where ironing roll 5 exerts a force F ₃ on the metal foil element 1.
W is a component in the direction parallel to the plane P ₁ of the weight vector of the ironing roll 5 and the rocking body 7 starting from the center of gravity G of the object including the ironing roll 5 and the rocking body 7. In FIG. 4, W is indicated by a vector, 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 includes the vector W and is parallel to the plane P ₁ .
α is an angle formed by the vector F ₂ and the vector F ₃ , and is also an angle formed by a plane including the central axis C ₁ of the winding roll 3 and the tangent line a and the plane P ₃ described above.

FIG. 5 is a VV arrow view of FIG. As shown in FIG. 5, the rocking body 7 and the pressing device 13 are provided on both sides of the ironing roll 5 in the axial direction. Therefore, the control device 19 controls the pair of pressing devices 13 as described above in synchronization with each other.

According to the ironing device 10 described above, the metal foil body 1 can be stabilized even if the coil 1a has a large diameter by expanding the adjustable range of the position a where the ironing roll 5 contacts the metal foil body 1 as follows. And can be wound up. The pressing device 13 presses the ironing roll 5 against the metal foil body 1 by applying a force to the swing body 7 so that the swing body 7 swings toward the winding roll 3 side. At this time, the oscillating body 7 oscillates by an amount corresponding to the position of the reciprocating body 9, so that if the position of the reciprocating body 9 changes, the contact position a (metal foil body) where the ironing roll 5 contacts the metal foil body 1. The pressing position to 1) also changes. Therefore, the adjustable range of the contact position a is expanded. As a result, even if the diameter of the coil 1a is increased, the metal foil body 1 can be stably wound up.

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

In the embodiment, the driving device 11 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 as follows.

As shown in FIG. 2, the hydraulic cylinder device 11 includes a cylinder 11a, a hydraulic source 11b, a servo valve 11c, and a piston rod 11d. Inside the cylinder 11a, a head side cylinder chamber 11a-1 and a rod side cylinder chamber 11a-2 are formed. As shown in FIG. 2, the hydraulic pressure source 11b is connected to the head side cylinder chamber 11a-1 and the rod side cylinder chamber 11a-2 by a hydraulic pressure supply pipe 11e. The servo valve 11c is provided in the hydraulic pressure supply pipe 11e and adjusts the hydraulic pressure supplied from the hydraulic pressure source 11b to the head side cylinder chamber 11a-1 and the rod side cylinder chamber 11a-2. The piston rod 11d reciprocates back and forth with respect to the take-up roll 3 by the hydraulic pressure supplied to the head side cylinder chamber 11a-1 and the rod side cylinder chamber 11a-2. Here, the front is a position approaching the winding roll 3, and the rear is a position away from the winding roll 3. The tip 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 is based on the detection value of the dimension sensor 15, the detection value of the position sensor 17, and a preset operation pattern (preferably the first or second operation pattern described above). To control. Specifically, the control device 19 controls the servo valve 11c so that each detection value of the dimension sensor 15 is positioned at the position of the reciprocating body 9 determined with respect to the detection value of the dimension sensor 15 in the operation pattern. The reciprocating body 9 is controlled to be positioned.

The pressing device 13 is a hydraulic / pneumatic cylinder device. In this case, the hydraulic / pneumatic cylinder device 13 has the following configuration and is controlled by the control device 19 as follows.

The hydraulic / pneumatic cylinder device 13 includes a cylinder 13a, a pneumatic pressure source 13b,

servo valves

13c and 13d, a first air-hydro converter 13e, a second air-hydro converter 13f, and a rod (piston) 13g.
Cylinder 13a is in reciprocating member 9 is rotatably mounted on the rotary shaft C ₄ around.
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-

hydro converters

13e and 13f by an air pressure supply pipe 13h as shown in FIG. .
The servo valve 13c adjusts the air pressure supplied from the air pressure source 13b to the first and second air-

hydro converters

13e and 13f.
The servo valve 13d adjusts the air pressure supplied from the air pressure source 13b to the first air-hydro converter 13e.
The oil chamber 13e-2 of the first air-hydro converter 13e is connected to the rod-side cylinder chamber 13a-2 of the cylinder 13a, and the oil chamber 13f-2 of the second air-hydro converter 13f is connected to the head-side cylinder of the cylinder 13a. Connected to chamber 13a-1.
By adjusting the air pressure supplied to the air chambers 13e-1 and 13f-1 in the first and second air-

hydro converters

13e and 13f by the

servo valves

13c and 13d, the head side cylinder chamber 13a- of the cylinder 13a is adjusted. 1 and the hydraulic pressure supplied to the rod side cylinder chamber 13a-2 are adjusted. Thus, rotatably mounted rod 13g to the rotation axis C ₃ around the oscillator 7, the oscillator 7 is allowed to act a force on the oscillator 7 in the direction that swings the winding roll 3 side, as a result, The metal foil body 1 is pressed against the take-up roll 3 through the ironing roll 5 attached to the rocking body 7.
Further, since the hydraulic / pneumatic cylinder device 13 has the air-

hydro converters

13e and 13f, even if it receives an impact from the metal foil body 1 via the ironing roll 5 and the swinging body 7, this impact is transferred to the air-hydro converter. It can be absorbed by the air pressure of 13e and 13f. Therefore, even if vibration is generated by increasing the winding speed of the winding roll 3 and the ironing roll 5 receives an impact, it can be absorbed.
In FIG. 2, reference numerals 13e-3 and 13f-3 denote pistons of the air-

hydro converters

13e and 13f, respectively.

The control device 19 controls the hydraulic / pneumatic cylinder device 13 based on the detection value of the force sensor 21, the detection value of the dimension sensor 15, and a preset pressing force pattern. Specifically, for each detection value of the dimension sensor 15, the rod 13 g presses the oscillating body 7 with a force F ₁ that is determined with respect to the detection value in the pressing force pattern and presses the oscillating body 7. Thus, the control device 19 controls the

servo valves

13e and 13f.

In the example of FIG. 2, the force sensor 21 includes a pressure sensor 21a for detecting the pressure in the head side cylinder chamber 13a-1 and a pressure sensor 21b for detecting the pressure in the rod side cylinder chamber 13a-2. Control device 19, the pressure sensor 21a, on the basis of the detected value of 21b, by controlling the servo valve 13c, the 13d, the pressing force _{F 1} of the above is to follow the pressing force pattern.
Here, the control device 19 controls the servo valve 13d based on the detection value of the pressure sensor 21b so that the hydraulic pressure in the rod side cylinder chamber 13a-2 is maintained at a constant set value, and at the same time, the pressure sensor 21a. Based on the detected value, the servo valve 13c is controlled so that the hydraulic pressure in the head side cylinder chamber 13a-1 follows the pressing force pattern. In this case, the pressing force pattern is expressed by the following equation (2) of [Equation 2], and the control device 19 controls the servo valve 13c based on the detection value of the pressure sensor 21b, so that the head side cylinder oil pressure in the chamber 13a-1 is controlled to be _{P h} of the formula (3) is a modification of equation (2) [equation 3].

In the formulas (2) and (3), the definitions of the same symbols as those in the formula (1) are the same as those in the formula (1). Definitions of new symbols in the 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 rod side cylinder chamber 13a-2 of the cylinder 13a, and is a constant set value as described above.
A _h is an area where the piston 13g receives pressure in the extension direction from the oil in the head side cylinder chamber 13a-1.
_Ar is an area where the piston 13g receives pressure from the oil in the rod-side cylinder chamber 13a-2 in its retracting direction.
In the equations (2) and (3), the numeral “2” takes into consideration that two hydraulic / pneumatic cylinder devices 13 are provided as shown in FIG.

6A to 6C are graphs showing the control by the first operation pattern. FIG. 6A shows the first operation pattern, and FIGS. 6B and 6C show the results when the first operation pattern of FIG. 6A is followed.
In FIG. 6A, the horizontal axis indicates the coil dimensions, and the vertical axis indicates the extension amount of the hydraulic cylinder device 11 (the stroke position of the piston rod 11 d) as the position of the reciprocating body 9.
In FIG. 6B, Q indicates the extension amount (stroke position of the rod 13g) of the hydraulic / pneumatic cylinder device 13, and R indicates the maximum extension amount (maximum stroke position of the rod 13g) of the hydraulic / pneumatic cylinder device 13. In FIG. 6B, the horizontal axis indicates the coil dimensions, and the vertical axis indicates the extension amount of the hydraulic / pneumatic cylinder device 13.
FIG. 6C shows the above-described circumferential distance between the pressing position a and the winding position b. In FIG. 6C, the horizontal axis indicates the coil dimensions, and the vertical axis indicates the circumferential distance between the pressing position a and the winding position b.

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

(1) A plurality of degeneration speed patterns of the hydraulic cylinder device 11 are set. Degeneration speed patterns A1, A2, and A3 shown in FIG. 7 are set.
In FIG. 7, a curve B <b> 1 indicates a known increase rate pattern of coil dimensions. The increasing speed of the coil dimension decreases as the coil dimension increases.
The degeneration speed patterns A1, A2, and A3 are set so as not to be far from the pattern B1 in FIG. The reason why the degeneration speed patterns A1, A2, and A3 are set as line graphs in FIG. 7 is to simplify the setting.
In FIG. 7, three degeneration speed patterns are set, but in practice, a large number of degeneration speed patterns can be set.

(2) For each of the contraction speed patterns A1, A2, and A3, when the hydraulic cylinder device 11 is contracted by the contraction speed pattern, the relationship between the extension amount of the hydraulic cylinder device 13 and the dimensions of the coil (hereinafter referred to as the hydraulic cylinder device 13). (Referred to as an expansion / contraction pattern). This simulation is performed based on the degenerate speed pattern, the coil dimensions at each time point known in advance, and the geometric shape and dimensions of the ironing device 10.

(3) From the expansion / contraction pattern of the hydraulic cylinder device 13 obtained for each contraction speed pattern in (2) described above, select the expansion / contraction pattern in which the hydraulic cylinder device 13 always contracts as the coil size increases.

(4) The line graph (degeneration speed pattern) in FIG. 7 corresponding to the selected expansion / contraction pattern is approximated by a curve. Thereby, the operation | movement of the hydraulic cylinder 11 by a degeneracy speed pattern is made smooth.

(5) The first operation pattern shown in FIG. 6A is obtained based on the degeneration speed pattern by the curve approximated in (4) described above and the geometric shape and dimensions of the ironing device 10.

8A to 8C are graphs showing the control by the second operation pattern. FIG. 8A shows a second operation pattern, and FIGS. 8B and 8C show results when the second operation pattern in FIG. 8A is followed.
In FIG. 8A, the horizontal axis indicates the coil dimensions, and the vertical axis indicates the extension amount of the hydraulic cylinder device 11 as the position of the reciprocating body 9 (stroke position of the piston rod 11d).
In FIG. 8B, Q indicates the extension amount (stroke position of the rod 13g) of the hydraulic / pneumatic cylinder device 13, and R indicates the maximum extension amount (maximum stroke position of the rod 13g) of the hydraulic / pneumatic cylinder device 13. In FIG. 8B, the horizontal axis indicates the coil dimensions, and the vertical axis indicates the extension amount of the hydraulic / pneumatic cylinder device 13.
FIG. 8C shows the above-described circumferential distance between the pressing position a and the winding position b. In FIG. 8C, the horizontal axis indicates the coil dimensions, and the vertical axis indicates the circumferential distance between the pressing position a and the winding position b.

The second operation pattern can be obtained in advance by, for example, the following procedures (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 ironing roll 5 is obtained for each dimension of the coil based on the set circumferential distance.
(3) When the position of the ironing roll 5 is obtained for each dimension of the coil, the expansion / contraction amount of the hydraulic cylinder device 11 is obtained from this position and the geometric shape and dimensions of the ironing device 10. That is, the second operation pattern is obtained.
Since FIG. 8A approximates the second operation pattern obtained in this way by a polynomial, in FIG. 8C, the circumferential distance slightly varies from a constant value. However, in order to make the circumferential distance constant, the second operation pattern need not be approximated by a polynomial.

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

1 metal foil body, 1a coil, 3 winding roll, 5 ironing roll,
7 Oscillator, 9 Reciprocating body, 10 Ironing device,
11 driving device (hydraulic cylinder device), 11a cylinder, 11b hydraulic source,
11c Servo valve, 11d Piston rod, 11e Hydraulic supply pipe,
11f piston, 12 guide rail,
13 Pressing device (hydraulic / pneumatic cylinder device), 13a cylinder, 13b pneumatic source,
13c, 13d servo valve, 13e first air-hydro converter,
13f second air-hydro converter, 13g piston rod,
14 piston, 15 dimension sensor, 17 position sensor, 19 control device,
21 force sensor, 23 reference body

Claims

When winding the rolled metal foil body around the winding roll, the ironing device presses the winding metal foil body against the winding roll,
An ironing roll that presses the metal foil being wound onto the winding roll;
An oscillating body in which an ironing roll is attached to one end side, and the other end can swing around its swinging axis;
A reciprocating body attached to the other end of the rocking body so as to be rockable and movable back and forth with respect to the winding roll;
A drive device for moving the reciprocating body back and forth with respect to the winding roll; and
A pressing device that generates a force for pressing the metal foil against the take-up roll, and
The pressing device applies a force to the oscillating body so that the oscillating body oscillates on the winding roll side, and thereby presses the metal foil body against the winding roll via an ironing roll attached to the oscillating body. An ironing device that is characterized.
A dimension sensor for detecting the dimension of the coil formed by the metal foil wound around the winding roll;
A position sensor for detecting the position of the reciprocating body;
A control device that controls the driving device based on a detection value of the dimension sensor, a detection value of the position sensor, and a preset operation pattern;
The ironing device according to claim 1, wherein the operation pattern defines a position of the reciprocating body with respect to each dimension of the coil.
The pressing device has a cylinder and a piston, and is a cylinder device capable of extending and retracting a piston rod by a reciprocating movement of the piston.
One of the cylinder and the piston rod is rotatably coupled to one end of the oscillating body, and the other of the cylinder and the piston rod is rotatably coupled to the reciprocating body. By the fluid pressure supplied to at least one of the side cylinder chambers, the swinging body is pressed in a direction in which the swinging body swings toward the take-up roll,
The ironing device according to claim 2, wherein the operation pattern is set so that the piston rod of the cylinder device continues to be retracted without being expanded.
The operation pattern is set so as to suppress fluctuations in the distance between the position where the ironing roll contacts the metal foil body and the winding position,
The ironing device according to claim 2, wherein the winding position is a boundary position between the metal foil body that has already been wound around the ironing roll and the metal foil body that is to be wound up.
A force sensor for detecting a force generated by the pressing device;
The control device controls the pressing device based on a detection value of the force sensor, a detection value of the dimension sensor, and a preset pressing force pattern,
The component of the pressing force in the direction from the position where the ironing roll applies the pressing force to the metal foil body toward the central axis of the winding roll is the center direction component,
In the pressing force pattern, the force generated by the pressing device is determined for each dimension of the coil so that the central direction component is constant regardless of the dimension of the coil. The ironing device according to any one of claims 1 to 4.