WO2018220858A1 - Roll feeder - Google Patents

Abstract

Provided is a roll feeder having an excellent camper correction function. This roll feeder comprises a pair of rollers (11a, 11b) that grip and rotate a strip-shaped member to perform an operation of feeding the strip-form member, wherein the roll feeder is provided with a mechanism (40) that enables one first roller (11a) to be displaced relative to the other second roller (11b) such that the distance between the first roller (11a) and the second roller (11b) can be individually varied at both ends of the rollers (11a, 11b), and two drive sources (first motor (14), second motor (16)) that drive an operation whereby the first roller (11a) is displaced relative to the second roller (11b) by the mechanism (40).

Description

Roll feeder

The present invention relates to, for example, a roll feeder for supplying a strip material to a press machine.

Generally, for example, Patent Document 1 discloses a processing step of continuously supplying a strip-like material (hereinafter referred to as a strip) made of steel, aluminum or the like to a press machine or the like and performing pressing or cutting. Such is done by a series of equipment. That is, a coiled strip of material (that is, a coil material) is rotated in a unwinding direction by a machine called an uncoiler to draw out the strip from the outer periphery at any time, and the wake of the uncoiler (press machine etc. The above-mentioned strip material is sent out to a press machine or the like by a predetermined amount and positioned by a machine called a roll feeder (or simply referred to as a feeder or the like) in the forestream of the above (see Patent Document 1) . Further, the roll feeder generally has a configuration including a pair of rolls (upper roll and lower roll) for realizing the feeding operation of the strip material by holding the strip material and rotating it.
And when the said strip | belt-shaped material is aluminum in particular, there exist some with a large camber amount, It is calculated | required to reduce this camber amount at the time of delivery.
Here, the term "camber" means that the strip is bent in the left-right direction (the width direction of the strip) with respect to the feeding direction (traveling direction) of the strip (unrolling by being wound in a coil shape) Is not a curve), and the amount that is bent to the left and right is called the camber amount. The amount of camber tends to be large in a foreign-made or poor-quality metal material, and the following problems occur due to the large amount of camber.
(A) When feeding a strip with a roll feeder, the strip is bent to the left or right in the direction of movement, and the strip can not be passed or passed to a device such as a press machine in a post process. Will be very difficult. Here, the term "passing" refers to passing a material to a predetermined position of the device, and if it can not be passed, it is not possible naturally to press or the like with the device in the post process.
(B) The strip material having a large amount of camber may be discarded, in which case the cost of the product manufactured from the strip material is increased.
(C) The equipment (for example, a guide member for guiding the strip material) is a bent side of the strip material as the strip material bends to one side in the left-right direction Continued rubbing causes wear and requires repair and repair of the equipment.
(D) The camber causes a reduction in the feeding accuracy (the accuracy of the distance and speed of feeding the strip material) of the roll feeder.
Therefore, in the prior art, for example, by inserting a shim (a thin wedge) into the member supporting the upper roll or the lower roll, the relative movement between the upper roll and the lower roll during the feeding operation (when sandwiching and feeding the strip material) There is a roll feeder which enables to adjust a certain distance and angle (inclination degree) by human work. Patent Document 2 discloses that the angle with respect to the lower roll of the upper roll can be adjusted by the driving force of the motor. These roll feeders change the relative distance or angle between the upper roll and the lower roll during the feeding operation, so that the axial direction of the pressure for sandwiching the strip between the upper roll and the lower roll during the feeding operation The distribution in the longitudinal direction of each roll, which is a direction perpendicular to the feeding direction, is changed according to the state of the camber of the strip, whereby the strip is corrected by the clamping pressure at the time of feeding operation, It is an attempt to reduce the amount of camber.

Unexamined-Japanese-Patent No. 2003-181573 JP 2001-30029 A

However, first, in the case of the above-described roll feeder in which the relative distance and angle between the upper roll and the lower roll can be adjusted by human work, the following problems occur. That is, in the case of this roll feeder, the strip material and pressure-sensitive paper to be actually fed are sandwiched between the upper roll and the lower roll, and then the pressure-sensitive paper is taken out and the magnitude and distribution of pressure are checked. Depending on the results, after removing and inserting shims or changing the type and number of shims to be inserted, the strip and pressure-sensitive paper are again sandwiched between the upper roll and the lower roll, and then the pressure-sensitive paper is removed. It is necessary to repeat the human work of checking the magnitude and distribution of pressure by looking as many times as necessary. For this reason, there has been a problem that the adjustment requires a long time of, for example, about 2 to 3 hours. In addition, since it will be adjustment of the material combination which uses the actual strip material, if the condition of the camber of the strip material to be handled next is different from the previous one (for example, it is bent to the opposite side) There was a problem that the above-mentioned human work of time had to be performed again.
Further, the roll feeder disclosed in Patent Document 2 is a member that supports the rotation of the output shaft of the motor by means of a screw mechanism with a large backlash consisting of an external thread and an internal thread (the end of the upper roll is supported via a bearing) ) To change the vertical angle of the upper roll by raising and lowering only one end of the upper roll by this linear movement. Therefore, in the case of the roll feeder disclosed in Patent Document 2, for example, the relative distance and angle between the upper roll and the lower roll at the time of feeding operation can be adjusted with high accuracy and finely adjusted. There were problems such as being difficult or impossible. In particular, since only one end of the upper roll is moved up and down, the distance between the other end of the upper roll and the lower roll can not be adjusted at all by the driving force of the motor. There was a problem that it could not but be made the composition adjusted by work.
Therefore, the present invention is provided with a pair of rolls that realize the feeding operation of the strip by pinching and rotating the strip, and the relative distance and angle of these rolls are desirably adjusted with high accuracy and fineness. The purpose is to provide a roll feeder that is easy to use.

The roll feeder described in claim 1 of the present application is a roll feeder including a pair of rolls that realizes a feeding operation of the strip material by holding the strip material and rotating it.
The first roll relative to the second roll such that the distance between the first roll, which is one of the rolls, and the second roll, which is the other of the rolls, is separately variable at each end of each roll A mechanism that makes it displaceable,
And a plurality of drive sources for driving an operation of displacing the first roll relative to the second roll by the mechanism.
The roll feeder described in claim 2 of the present invention is characterized in that the mechanism is a five-bar link mechanism.
In addition, the roll feeder described in claim 3 of the present application is
The mechanism is driven by a first motor which is one of the drive source, a first member rotatably supporting the first roll, a second member rotatably supporting the second roll, and the drive source. A node having a first rotating shaft, a second rotating shaft disposed parallel to the first rotating shaft and driven by a second motor which is the other of the drive sources, and a third member A nodal rotation type link mechanism (a link mechanism in which five nodes (links) are connected by five joints (joints) for achieving a turning couple),
A first shaft portion rotatably attached to the second member and rotationally driven by the first motor, and the first rotation shaft is provided eccentrically on an extension of the first shaft portion; 1 with eccentric shaft,
The second rotation shaft is rotatably attached to the second member at a position different from the first shaft portion so as to be parallel to the first shaft portion, and rotationally driven by the second motor. And a second eccentric shaft portion provided eccentrically on an extension of the second shaft portion and rotatably mounted on the first member,
The third member is rotatably attached to the first member by a connecting shaft having one end side parallel to the first rotating shaft, and the other end is rotatably attached to a first eccentric shaft portion of the first rotating shaft It is characterized by the following.
The roll feeder described in claim 4 of the present application is
The first rotation shaft, the second rotation shaft, and the connection shaft are disposed in a torsional positional relationship with respect to the roll, and the first rotation shaft, the second rotation shaft, and the connection are provided. The axial direction of the shaft is set to be 90 degrees different from the axial direction of the roll,
The first member is a front first wall portion located forward of the center line of the roll in the front-rear direction, and a rear first wall portion located rearward of the center line of the roll in the front-rear direction Have and
The second member includes a front second wall portion positioned forward of the front first wall portion in the front-rear direction, and a rear side second rear portion positioned rearward of the rear first wall portion in the front-rear direction With 2 walls,
The third member is a front third member located on the front side with respect to the center line of the roll in the front-rear direction and having one end rotatably attached to the first front wall by the connecting shaft; There is provided a rear third member which is positioned rearward of the center line of the roll in the direction and one end of which is rotatably attached to the rear first wall by the connecting shaft,
The first rotation shaft is, as the first shaft portion, a front first shaft portion rotatably attached to the front second wall portion, and a rear side first rotatably mounted to the rear second wall portion. A front first eccentric shaft portion rotatably attached to the other end side of the front third member as the first eccentric shaft portion and having the shaft portion, and the other end side of the rear third member And a rear first eccentric shaft portion rotatably mounted on the
The second rotation shaft is, as the second shaft portion, a front second shaft portion rotatably attached to the front second wall portion, and a rear side second rotatably attached to the rear second wall portion. It has a shaft, and as the second eccentric shaft, it is rotatably attached to the front second eccentric shaft that is rotatably attached to the front first wall and to the rear first wall. And a rear second eccentric shaft portion,
The mechanism comprises a front link mechanism and a rear link mechanism,
The front side link mechanism includes the front side first wall portion, the front side second wall portion, the front side first shaft portion and the front side first eccentric shaft portion, the front side second shaft portion and the front side second eccentricity. It is a 5-node rotation type link mechanism which makes a shaft part and said front 3rd member a node,
The rear side link mechanism includes the rear side first wall portion, the rear side second wall portion, the rear side first shaft portion and the rear side first eccentric shaft portion, and the rear side second shaft portion. And a 5-node rotary type link mechanism having a rear second eccentric shaft portion and the rear third member as nodes.
The front link mechanism and the rear link mechanism are provided (preferably symmetrically) on the front side and the rear side with respect to a plane including the center line of the roll and orthogonal to the front-rear direction. It is characterized by

According to the roll feeder of claim 1 of the present application, the distance between the first roll which is one of the pair of rolls which realizes the feeding operation of the strip material by the operation of the plurality of drive sources and the second roll which is the other. However, since it becomes separately variable at both ends of each roll, it is possible to easily adjust (or change) the relative distance and angle of these rolls. Thereby, it is possible to easily reduce the amount of camber of the strip material by the roll feeder.
Moreover, in the embodiments according to claims 2 and 3 of the present application, the mechanism that makes the first roll displaceable with respect to the second roll is a five-bar link mechanism that can reduce the backlash compared to the screw mechanism. It is possible to adjust or change the relative distance and angle of the rolls with high accuracy and fineness.
In particular, according to the third aspect of the present invention, the mechanism is a 5-node rotary link mechanism, and the first rotary shaft and the second rotary shaft, which are two nodes (links) constituting the link mechanism, are used. The first member supporting the first roll can be operated in two degrees of freedom with respect to the second member supporting the second roll by rotationally driving each of the first motor and the second motor. In addition, since it is a 5-node rotation type link mechanism, all joints (joints) connecting the nodes and the nodes can be generally constituted by rotary bearings (bearings) with less rattling compared with a slide mechanism, a screw mechanism and the like. Therefore, by controlling the two motors, it is possible to easily adjust (or change) the relative distance and angle of the pair of rolls for feeding operation with high accuracy and fineness.
Further, in the aspect described in claim 4 of the present application, a front side link mechanism and a rear side link mechanism are provided as the mechanism, and these link mechanisms include the center line of the roll and the front and rear direction (the axial direction of the roll It is configured to be provided (preferably, symmetrically) on the front side and the rear side with respect to a plane which is different from the direction which is different, that is, the feeding direction of the strip material). As a result, at the time of the feeding operation for pinching the strip material by the roll, the force by which the third member or the like pushes the first member in the direction to press the first roll against the second roll Distributed on the near side. Moreover, in the aspect as set forth in claim 4 of the present application, the first rotating shaft, the second rotating shaft, and the connecting shaft are attached (or connected) to either the front or rear wall portion at both ends and supported Support structure. Therefore, according to the fourth aspect of the present invention, during the feeding operation for sandwiching the strip material by the roll, the stress or the deformation generated in the first member or each rotation shaft constituting the mechanism is suppressed. Problems such as deviation of the first roll from the proper position and posture due to this deformation are suppressed. Therefore, along with the feeding operation which is the original function of the roll feeder, the force for sandwiching the strip material is appropriately biased in the width direction of the strip material (that is, the axial distribution of the pressure for sandwiching the strip material is appropriate. It is possible to reduce the amount of camber of the belt-like material by setting it to (2) with high reliability and good results. Further, as described above, the force for pressing the first member is dispersed, and each shaft has a dual support structure, so that the load on each bearing that connects each shaft to the member and rotatably supports, for example, is reduced. There is also an effect of extending the life until the parts such as the bearing constituting the roll feeder are damaged by fatigue.

FIG. 1 is a top view of a roll feeder.
FIG. 2 is a front view (view in the direction of arrow X) of the roll feeder.
FIG. 3 is a side view (as viewed in the direction of the arrow Y) of the roll feeder.
FIG. 4 is a longitudinal cross-sectional view of the roll feeder, and is a cross-sectional view taken along line A in FIG.
(A) of FIG. 5 is a partially enlarged view of the A sectional view, and (b) of FIG. 5 is a view showing a first rotation axis.
FIG. 6 is a cross-sectional view of the roll feeder and is a cross-sectional view taken along line B in FIG.
7 is a cross-sectional view of C in FIG. 4 (partially E cross-sectional view or F cross-sectional view).
FIG. 8 is a cross-sectional view taken along the line D in FIG. 4 (a partial cross-sectional view taken along the line F).
FIG. 9 is a view showing an operation example of the first roll, in which (a) shows only the first roll, and (b) shows also the second roll.
FIG. 10 is a view showing an operation example of the first roll, in which (a) shows only the first roll, and (b) shows also the second roll.
FIG. 11 is a view showing an operation example of the first roll, in which (a) shows only the first roll, and (b) shows also the second roll.
FIG. 12 is a view for explaining the mechanical configuration and operation of a link mechanism which makes the first roll displaceable.
(A) of FIG. 13 is a figure which shows an example of supply equipment of a strip | belt-shaped material, (b) of FIG. 13 is a flowchart explaining the position setting (initial setting) of the 1st roll of a roll feeder.
(A) of FIG. 14 shows an example of a timing chart at the time of operation of the roll feeder, and (b) of FIG. 14 is a view for explaining the direction of the camber of the strip and the position to be rolled.
(A) of FIG. 15 shows a modification 1 of the timing chart during operation of the roll feeder, and (b) of FIG. 15 shows a modification 2 of the timing chart during operation of the roll feeder.
(A) of FIG. 16 is a view showing a modification of the roll feeder, and (b) of FIG. 16 is a view showing a comparative example of a timing chart at the time of operation of the roll feeder.

Hereinafter, a first embodiment which is an example of an embodiment of the present invention will be described based on the drawings.
First, an example of a strip material supply facility in which the roll feeder 10 of this embodiment is used will be described with reference to FIG. As shown in FIG. 13 (a), the equipment of this example includes an uncoiler 2 that rotates the coil material 1a in the unwinding direction and feeds the strip material 1 from the outer periphery at any time, and passes the strip material 1 downstream of the uncoiler 2 The leveler feeder 5 corrects flatly, the roll feeder 10 feeds out and positions the strip material 1 after correction to the press machine etc. by a predetermined amount downstream of the leveler feeder 5, the roll feeder 10 and the leveler feeder 5 are fixed. The controller 20 has a controller 20 that operates with small intermittent feed and continuously operates the uncoiler 2 basically at a constant speed (however, there may be speed switching).
Here, as shown in FIG. 13, the roll feeder 10 has a pair of feed rolls 11 a and 11 b that realize the feeding operation of the strip 1 by holding the strip 1 and rotating, and the feed rolls 11 a and 11 b. A motor 12 (servo motor) for driving at least one of them and a position detector 13 (for example, a pulse generator; a so-called encoder) for outputting a position detection signal according to the rotation of the motor 12 are provided. And although roll feeder 10 of this example is mentioned below for details, it may be called upper feed roll 11a (following, upper roll 11a or the 1st roll 11a) in addition to motor 12 (feed motor) for sending. And motors 14 and 16 (servo motors) for moving the lower feed roll 11b with respect to the lower feed roll 11b (hereinafter sometimes referred to as the lower roll 11b or the second roll 11b) and the rotation of these motors 14 and 16). And a position detector (for example, a pulse generator; a so-called encoder) for outputting each position detection signal. In the present application, the feed roll may be referred to simply as a roll.
Further, on the upstream side of the roll feeder 10, there is provided an R guide 10a (for example, one comprising a plurality of guide rolls not shown) contacting the lower surface of the end of the slack portion (loop 1b) of the strip 1 . Also, the feed rolls 11a and 11b are rolls that apply a force to the strip material 1 to feed the strip material 1 to the downstream equipment (for example, a press machine). The feed roll 11 b on the side is rotationally driven by the motor 12. Further, the operation of each of the motors 12, 14, 16 is feedback-controlled by a controller (not shown) in the control device 20. That is, during operation, the motor 12 is driven by the control device 20 so that, for example, the deviation of the rotational position of the motor 12 (the difference between the command value and the feedback value) always approaches zero. It is sent out by a set feed amount at a predetermined timing synchronized with the operation. FIG. 13A schematically shows the roll feeder 10 and the like, and the detailed configuration of the roll feeder 10 will be described later.
Next, unlike the simple leveler, the leveler feeder 5 can perform feedback control of the feeding operation in the same manner as the roll feeder 10. For example, as shown in FIG. 13, in addition to the correction rollers 6 alternately arranged for correction, the pair of feed rolls 7a which realize the feeding operation of the strip 1 by holding the strip 1 and rotating it. , 7b and a motor 8 (servo motor) for driving at least one of the feed rolls 7a and 7b, and a position detector 9 (for example, a pulse generator for outputting a position detection signal according to the rotation of the motor 8). A so-called encoder). Further, on the downstream side and the upstream side of the leveler feeder 5, a plurality of R guides 5a and 5b (for example, not shown) are in contact with the lower surface of the end of the slack portion (loop 1b or loop 1c described later) of the strip 1 Are provided respectively). Further, the operation of the motor 8 is feedback controlled by a controller (not shown) in the controller 20. Here, the correction roller 6 is configured to flatten the strip material 1 by removing the winding bend caused by the strip material 1 being wound in a coil shape.
Next, the uncoiler 2 includes a drum 2a that supports the coil material 1a from the inside, and a motor 3 that drives the drum 2a. The motor 3 is controlled by a controller (not shown) for the uncoiler 2 in the controller 20. In the case of this example, the slack portion (loop 1c) of the strip 1 is also formed between the uncoiler 2 and the leveler feeder 5. Although not shown, a sensor (loop sensor) for detecting the size (loop amount) of the slack portion of the loop 1c is provided, and the motor 3 is set to the loop amount of the loop 1c detected by the loop sensor. In response, the rotational speed is switched. Therefore, the controller for the uncoiler 2 that controls the motor 3 does not necessarily need to perform feedback control, as long as it can simply change the rotational speed of the motor 3. In addition, the acceleration at the time of switching of the rotational speed of the motor 3 is controlled to a small value (a value significantly smaller than 1 G) in consideration of the magnitude of inertia of the load (the coil material 1a etc.).
The control device 20 corresponds to the entire control system including the above-described controllers (the controller for the uncoiler 2, the controller for the leveler feeder 5, and the controller for the roll feeder 10), and corresponds to control means.
Although not shown, the control device 20 includes an operation panel (operation unit) provided with various push buttons for operation and a display unit. Manual operation of each motor and various data setting operations are possible from this operation panel. In addition, as data preset by the operator from the operation panel, a target feed amount in a single feeding operation of the strip 1 (for example, the strip 1 is specified for one operation of a press machine which is a downstream equipment). 14 (a), a predetermined value (top speed) of the feed speed illustrated in the lower part of FIG. 14 (a), acceleration time and deceleration time illustrated in the lower part of FIG. 14 (a), FIG. Data for specifying the vertical position (described later) of the upper roll both ends illustrated in the upper part of) (data for specifying the position change pattern during release operation in addition to the set values Z1 and Z2 input in the initial setting described later) There is.
In the configuration example shown in FIG. 13 (a), the relative acceleration of the loop (the slack portion of the strip 1) during operation is realized while realizing the highest acceleration of the feeding operation of the strip to the press machine or the like. In order to prevent damage to the strip 1 and damage to the machine such as the roll feeder due to loop fluttering (looping), two feed mechanisms (leveler feeder 5) in the wake of the uncoiler 2, which is a type of feed mechanism. And a roll feeder 10), and also form a strip loop (loop 1b) between the two feeding mechanisms, including the uncoiler 2, three feeding mechanisms and two loops (loop 1b, loop 1c). It is provided. In this configuration, each motor 3 of each feed mechanism (uncoiler 2, leveler feeder 5, roll feeder 10) so that relative acceleration of each loop (loop 1b, loop 1c) is always 1 G or less (gravitational acceleration or less). , 8 and 12 greatly reduce loop sway, and further, the maximum acceleration of the feeding operation to the press machine etc. (in this case, the maximum value of the acceleration of the feeding operation by the roll feeder 10) It can be done. For example, when the feed operation of the downstream feed mechanism (for example, the roll feeder 10) downstream of the loop 1b is in an accelerated state of, for example, 2G (twice the gravitational acceleration), the upstream feed mechanism (for example, For example, when the feed operation of the feeder 5) is in an acceleration state of 1 G (gravity acceleration) and the feed operation of the downstream side feed mechanism is a deceleration state of 2 G, the feed operation of the upstream side feed mechanism is in a deceleration state of 1 G With such control, the relative acceleration of each loop is always 1 G or less, and the swing acceleration of each loop is significantly reduced because gravity acceleration is not exceeded. Moreover, the maximum acceleration of the supply operation to the press machine or the like (in this case, the maximum value of the acceleration of the feed operation by the roll feeder 10) can be set to 2 G, for example.
However, the configuration shown in FIG. 13A is only one specific example, and various other configurations may be possible (other configuration examples will be described later).
Next, the roll feeder 10 to which the present invention is applied will be described in detail below.
The above-described leveler feeder 5 includes a configuration as a roll feeder consisting of a pair of rolls (feed rolls 7a and 7b) for feeding the strip 1, and the present invention is directed to the roll feeder portion of the leveler feeder 5. It is also possible to apply the present invention, but in the present example, the case where the present invention is applied to the downstream side roll feeder 10 will be described below.
1 is a top view of the roll feeder 10, FIG. 2 is a front view of the roll feeder 10 (viewed in the direction of arrow X in FIG. 1), and FIG. 3 is a side view of the roll feeder 10 (in the view of arrow Y in FIG. 4A is a cross-sectional view of FIG. 1A, FIG. 5A is a partial enlarged view of the A cross-sectional view, and FIG. 5B is a view showing a first rotation shaft 43 described later. 6 is a B cross-sectional view in FIG. 2, FIG. 7 is a C cross-sectional view (partially E cross-sectional view or F cross-sectional view) in FIG. 4 and FIG. 8 is a D cross-sectional view in FIG. F cross section).
As described with reference to FIG. 13A, the roll feeder 10 may be provided with a device such as the above-mentioned R guide 10a for guiding the strip 1, for example. The illustration is omitted in FIG.
The roll feeders 10 are disposed in parallel to each other as shown in FIGS. 1 to 3 and the like, and hold the strip 1 and rotate it to realize a pair of rolls (first rolls 11 a, The distance between the second roll 11 b), the first roll 11 a (upper roll 11 a) which is one of the rolls, and the second roll 11 b (lower roll 11 b) which is the other of the rolls is both axial ends of each roll A mechanism 40 for enabling the first roll 11a to be displaced relative to the second roll 11b so as to be independently variable on the side, and an operation for the first roll 11a to be displaced relative to the second roll 11b by this mechanism 40 And two drive sources (motors 14 and 16) for driving the Here, the two drive sources are the motors 14 and 16 described above, and hereinafter, the motor 14 may be referred to as a first motor 14 and the motor 16 may be referred to as a second motor 16.
The rolls (the first roll 11a and the second roll 11b) have, as shown in FIG. 8, a cylindrical portion (reference numeral omitted) for holding the strip at the outer periphery in the central portion. It has a configuration having a mounting shaft portion (reference numeral omitted) smaller in diameter than the cylindrical portion coaxially extending from both sides.
The mechanism 40 is mechanistically a five-bar linkage. The five-bar linkage mechanism includes, for example, a linear motion type five-bar linkage mechanism in which two pairs are constituted by straight pairs (for example, a pair consisting of cylinders etc.), but in the mechanism 40 of this example, all pairs are rotational pairs. It is a rotating five-bar linkage that is (rotational couple).
That is, as shown in FIGS. 2 to 8, the mechanism 40 includes a first member 41 rotatably supporting the first roll 11 a, a second member 42 rotatably supporting the second roll 11 b, and the second member 42. A first rotary shaft 43 (shown in FIG. 6 and the like) driven by a first motor 14 which is one of the drive sources, and the two drives arranged in parallel to the first rotary shaft 43 The second rotation shaft 44 (shown in FIG. 6 and the like) driven by the second motor 16, which is the other of the sources, and the third member 45 or 46 (FIG. 5) connected to the first member 41 by the connecting shaft 47. This is a five-bar rotating link mechanism in which five nodes are shown in (a) and the like. The five-link type link mechanism (also referred to as a rotary five-link mechanism etc.) has five joints (links) by five joints (for example, joints such as a rotary bearing called bearings) that realize a turning couple. It is a linked link mechanism.
Here, the first rotation shaft 43, the second rotation shaft 44, and the connecting shaft 47 are twisted relative to the rolls (the first roll 11a and the second roll 11b) as shown in FIGS. The first rotary shaft 43, the second rotary shaft 44, and the axial direction of the connecting shaft 47 are set in the front-rear direction different by 90 degrees from the axial direction of the roll.
For example, the upward direction in the paper surface of FIG. 1 is the feed direction for feeding the strip 1 (the feed direction for the strip 1), and a direction parallel to this feed direction is referred to as the front-rear direction of the roll feeder. Then, as shown in FIG. 3, in the front-rear direction, the entry side of the strip material 1 into the roll feeder 10 is referred to as the rear side of the roll feeder 10, and the delivery side from which the strip material 1 exits the roll feeder 10 Is called the front side of the roll feeder 10. And the said front-back direction is usually parallel to the floor surface (usually horizontal surface) which installs the roll feeder 10 (that is, normally horizontal direction).
Further, the left-right direction in the paper surface of FIG. 2 is the axial direction of the rolls (the first roll 11a and the second roll 11b) (that is, the width direction of the strip 1 pinched by the rolls). The right side in the left-right direction (the side on which the feed motor 12 is attached) may be referred to as the drive side, and the left side in the left-right direction may be referred to as the reverse drive side. And the said left-right direction is also parallel to the floor surface (usually horizontal surface) which installs the roll feeder 10 normally (that is, it is normally horizontal).
Further, as shown in FIGS. 1 to 8, the first member 41 has a front first wall portion 41 a positioned on the front side of the center line of the roll in the front and rear direction, and a center line of the roll in the front and rear direction. The rear first wall portion 41b located on the rear side than the rear side, the left first wall portion 41c (see FIG. 2 etc.) whose lower end extends to the left position of the first roll 11a, and the lower end is the first roll 11a And the right side first wall portion 41 d (see FIG. 2 etc.) extending to the right side position. Among them, on the left side of the lower end portion of the front side first wall portion 41a, as shown in FIG. 5A, a notch for passing the first rotation shaft 43 while avoiding interference with the front side first wall portion 41a. The part 41e is provided. Similarly, a notch 41f is provided on the left side of the lower end portion of the rear first wall 41b so as to prevent the first rotary shaft 43 from interfering with the rear first wall 41b (see FIG. 7 and 16). And as shown in FIG. 7, the both ends of the 1st roll 11a (ends of the above-mentioned attachment axial part) are left-hand 1st wall 41c and bearing 48 and 49 (for example, ball bearings; ball bearings) respectively. The first roll 11 a is rotatably supported by the first member 41 by being attached to the right first wall portion 41 d. In addition, what is shown with the code | symbol 50 in FIG. 2 is an upper side synchronous gear which is a right end part (attachment axial part of the right side) of the 1st roll 11a, and is fixed inside the right side 1st wall part 41d. The upper synchronization gear 50 is not shown in FIGS. 7 and 8 or the like.
Next, as shown in FIGS. 1 to 8, the second member 42 includes a front second wall portion 42a positioned on the front side of the front first wall portion 41a in the front-rear direction, and a second rear portion in the front-rear direction The second rear wall 42b located rearward of the first wall 41b, and the second rear wall 42c whose lower end extends further downward through the left side of the second roll 11b (see FIG. 2 etc.) , The right lower second wall 42 d (see FIG. 2 etc.) extending at the lower end by passing the right side of the second roll 11 b, and the rear lower side further behind the rear second wall 42 b) A side outer wall 42e (see FIG. 1 and the like) and a front side wall 42f (see FIGS. 2 and 3 and the like) located below the front second wall 42a.
The second member 42 is basic to the floor surface on which the roll feeder 10 is installed, for example, in any one or more of the front side wall portion 42f, the left side second wall portion 42c, and the right side second wall portion 42d. Fixed. At this time, it may be fixed directly to the floor or may be fixed to a rack mounted on the floor. Thus, the roll feeder 10 is installed at a predetermined place by the second member 42 being fixed. However, the roll feeder 10 (second member 42) may be fixed to a movable carriage (not shown), for example, and may be moved during non-operation to easily change the installation location.
Then, as shown in FIG. 8, both end portions of the second roll 11b (end portions of the mounting shaft portion) are respectively connected to the left second wall portion 42c via bearings 51 and 52 (for example, ball bearings; ball bearings). The second roll 11b is rotatably supported by the second member 42 by being attached to the right second wall portion 42d. In addition, what is shown with the code | symbol 53 in FIG. 2, FIG. 8 etc. is a right end part (attachment axial part of the right side) of the 2nd roll 11b, and the lower side fixed to the inside inside rather than the 2nd right wall part 42d. It is a synchronous gear. The lower synchronization gear 53 meshes with the above-described upper synchronization gear 50 to synchronize and rotate the first roll 11 a as the second roll 11 b rotates.
The first roll 11a can move up and down or tilt relative to the second roll 11b by means of a mechanism 40 (five-bar link mechanism) (details will be described later), but the movement is small. The state in which the teeth of the lower synchronous gear 53 and the teeth of the upper synchronous gear 50 are engaged with each other is maintained even if the first roll 11a moves.
Moreover, what is shown with the code | symbol 54 in FIG. 1 is an attachment member for fixing the feed motor 12 to the outer surface side of the right side 2nd wall 42d of the 2nd member 42. As shown in FIG. The inside of the mounting member 54 is hollow, and a coupling (part connecting the shaft and the shaft) 55 is disposed inside the mounting member 54. The coupling 55, as shown in FIG. 2, includes the output shaft 12a of the feed motor 12 disposed substantially on the same axial center line as the second roll 11b, and the end of the attachment shaft on the right side of the second roll 11b. Are linked. As a result, the second roll 11 b is directly connected to the output shaft 12 a of the feed motor 12 and driven by the feed motor 12 to rotate.
As mentioned above, although the 1st member 41 and the 2nd member 42 were explained, the relation of the 1st member 41 and the 2nd member 42 is explained here. The first member 41 and the second member 42 are independent members, and the first member 41 is a vertical direction with respect to the second member 42 (a direction perpendicular to the front-rear direction and the left-right direction, and is usually vertical While being able to move in the direction), it is also possible to move slightly in the lateral direction. That is, as shown in FIG. 6 and FIG. 16 described later, it comprises the front first wall 41a, the rear first wall 41b, the left first wall 41c, and the right first wall 41d of the first member 41. When the horizontal cross section has a hollow rectangular shape, the horizontal cross section including the front second wall 42a, the rear second wall 42b, the left second wall 42c, and the right second wall 42d of the second member 42 is hollow. The first member 41 can be moved up and down with respect to the second member 42 by a predetermined clearance in the inside of the rectangular portion, and further in the left and right direction. It is possible to move slightly. Here, the predetermined gap means a gap that allows the first member 41 to move relative to the second member 42 (including tilting to move in an inclined manner) by the operation of the mechanism 40 (five-bar link mechanism). Do. However, in the case of this example, the first member 41 can hardly move in the front-rear direction, and the first roll 11a is approximately directly above the second roll 11b (the center line of the first roll 11a And the state in which the center line of the second roll 11b is in substantially the same plane orthogonal to the front-rear direction is maintained.
In the present specification, the vertical direction (the direction perpendicular to the longitudinal direction (the feeding direction of the strip material) and the horizontal direction (the axial direction of each roll)) in the sheet of FIG. 2 is referred to as the vertical direction for convenience. To However, although the vertical direction is usually the vertical direction, it is not limited to the vertical direction. This is because the entire roll feeder 10 may be installed obliquely with respect to the vertical direction.
Next, the third members 45 and 46 are rotatably attached to the first member 41 by the connecting shaft 47 whose one end side (upper end side in this example) is parallel to the first rotation shaft 43, and the other end side (this example) Then, the lower end side is rotatably attached to a first eccentric shaft (the front first eccentric shaft 43c or the rear first eccentric shaft 43d) of the first rotation shaft 43 described later.
In detail, as shown in FIG. 5 and the like, as the third member, a third front member 45 positioned on the front side of the center line of the roll in the front-rear direction and a center line of the roll in the front-rear direction A rear side third member 46 located at the rear side is provided. The front third member 45 is rotatably attached to the front first wall 41a of the first member 41 by the connecting shaft 47 at one end (the upper end in this example), and the other end (the lower end in this example) ) Is rotatably attached to a front first eccentric shaft portion 43c (described later) of the first rotation shaft 43. Further, the rear side third member 46 is rotatably attached to the rear side first wall portion 41b of the first member 41 by the connecting shaft 47 at one end side (upper end side in this example), and the other end side (in this example) The lower end side) is rotatably attached to a rear first eccentric shaft portion 43 d of the first rotation shaft 43 described later.
Here, as shown in FIG. 5, the connecting shaft 47 has its front end attached to the front first wall 41 a of the first member 41 and its rear end attached to the rear first wall 41 b of the first member 41. It is an axis that Further, as shown in FIG. 5, the upper end of the front third member 45 is attached to the outer periphery on the front side of the center of the connecting shaft 47 via a bearing 61 (for example, roller bearing), whereby the front third member 45 is connected to the connecting shaft It is rotatable around 47. Similarly, the upper end of the rear third member 46 is attached to the outer periphery on the rear side of the center of the connecting shaft 47 via a bearing 62 (for example, a roller bearing), whereby the rear third member 46 is connected to the connecting shaft 47. It is rotatable around the Note that both ends of the connecting shaft 47 may be non-rotatably fixed to the front first wall portion 41a and the rear first wall portion 41b, or may be rotatably mounted. The connecting shaft 47 may be attached to the first member 41 so as not to drop off from the attachment position shown in FIG. 5 with respect to the front side first wall portion 41a and the rear side first wall portion 41b.
Next, a first shaft 43 (left eccentric shaft) is rotatably attached to the second member 42 and is rotatably driven by the first motor 14, and an extension of the first shaft. And a first eccentric shaft provided eccentrically. In detail, as shown in FIG. 5, the first rotary shaft 43 is a front first shaft portion 43a rotatably attached to the front second wall portion 42a as the first shaft portion, and a rear second wall portion And a rear first shaft portion 43b rotatably attached to 42b, and rotatably attached to the other end side (the lower end side in this example) of the front third member 45 as the first eccentric shaft portion. It has a front first eccentric shaft portion 43c and a rear first eccentric shaft portion 43d rotatably mounted on the other end side (lower end side in this example) of the rear third member 46.
Here, the center lines of the front side first shaft portion 43a and the rear side first shaft portion 43b coincide, and the center lines of the front side first eccentric shaft portion 43c and the rear first eccentric shaft portion 43d coincide with each other. ing. However, the center lines of the front first shaft portion 43a and the rear first shaft portion 43b, and the center lines of the front first eccentric shaft portion 43c and the rear first eccentric shaft portion 43d are shown in FIG. 5 (b). As shown in FIG. 5, the eccentricity is offset by a predetermined eccentricity amount G1. Therefore, the first rotary shaft 43 is driven by the first motor 14 in the first eccentric shaft portion (the first front eccentric shaft portion 43c and the rear first eccentric shaft portion 43d) of the first rotary shaft 43. Then, it rotates with respect to the second member 42, and revolves with the eccentricity amount G1 as a radius of revolution. Therefore, the first rotation shaft 43 can be considered mechanically as a link (node) having a length of the eccentricity amount G1.
Although the amount of eccentricity G1 varies depending on the range of the thickness of the strip 1 to be handled, etc., it is, for example, a small size about the maximum thickness of the strip 1 to be handled.
Further, as shown in FIG. 5, the first rotary shaft 43 is rotatably attached to the front second wall portion 42a by bearings 63 (for example, roller bearings) on the outer periphery of the front first shaft portion 43a, and the rear first shaft It is rotatably attached to the rear second wall portion 42b by a bearing 64 (for example, a roller bearing) on the outer periphery of the portion 43b. As shown in FIG. 5, the lower end of the front third member 45 is attached to the outer periphery of the front first eccentric shaft portion 43c via a bearing 65 (for example, a roller bearing), whereby the front third member 45 is It is rotatable about the eccentric shaft portion 43c. Similarly, the lower end of the rear third member 46 is attached to the outer periphery of the rear first eccentric shaft portion 43d via a bearing 66 (for example, a roller bearing), whereby the rear third member 46 is mounted on the rear third side. It is rotatable about the eccentric shaft portion 43d.
In addition, as shown in FIG. 5 and FIG. 6 etc., cylindrical or donut shapes whose reference numerals are omitted at positions adjacent to the bearings on the outer periphery of the first rotary shaft 43, the second rotary shaft 44 and the connecting shaft 47. A member is attached. These cylindrical or doughnut-shaped members are members having functions such as positioning by restricting movement of the bearings, the first member 41, the third member 45 or 46 in the front-rear direction, and the like. However, in FIG. 6, there are places where illustration is omitted about a part of these cylindrical or doughnut-shaped members.
As shown in FIGS. 4 and 6, the rear first shaft portion 43b of the first rotation shaft 43 extends rearward through the rear second wall portion 42b, and the rear first shaft portion The first motor 14 is disposed substantially on the same center line as 43 b. The first motor 14 is fixed to the aforementioned rear outer wall portion 42e of the second member 42 with the output shaft 14a thereof directed forward. The output shaft 14a of the first motor 14 extends forward of the rear outer wall 42e, and the coupling 70 is disposed in the space between the rear outer wall 42e and the rear second wall 42b. It is connected with the back side 1st axial part 43b. Thus, the first rotation shaft 43 is directly connected to the output shaft 14 a of the first motor 14 and driven by the first motor 14 to rotate.
Next, the second rotation shaft 44 (right eccentric shaft) is parallel to the first shaft portion of the first rotation shaft 43 (front first shaft portion 43a, rear first shaft portion 43b). A second shaft portion rotatably attached to the second member 42 at a position different from the first shaft portion and rotationally driven by the second motor 16, and provided eccentrically on an extension of the second shaft portion And a second eccentric shaft portion rotatably attached to the first member 41. In detail, as shown in FIG. 6, the second rotation shaft 44 is a second shaft portion, and a front second shaft portion 44a rotatably attached to the front second wall portion 42a, and a rear second wall portion A front second eccentric shaft 44c rotatably attached to the front first wall 41a as the second eccentric shaft, and having a rear second shaft 44b rotatably attached to the housing 42b; And a rear second eccentric shaft 44d rotatably mounted on the rear first wall 41b.
Here, the center lines of the front side second shaft portion 44a and the rear side second shaft portion 44b coincide, and the center lines of the front side second eccentric shaft portion 44c and the rear second eccentric shaft portion 44d coincide with each other. ing. However, as shown in FIG. 6, the central lines of the front second axial portion 44a and the rear second axial portion 44b and the central lines of the front second eccentric shaft portion 44c and the rear second eccentric shaft portion 44d. The eccentricity is offset by a predetermined eccentricity amount G2. Therefore, the second rotary shaft 44 is driven by the second motor 16 in the second eccentric shaft portion of the second rotary shaft 44 (the front second eccentric shaft portion 44c and the rear second eccentric shaft portion 44d). Then, it rotates with respect to the second member 42 and revolves with the eccentricity amount G2 as a radius of revolution. Therefore, the second rotation shaft 44 can be considered mechanically as a link (node) having a length of the eccentricity amount G2.
The eccentricity amount G2 is different depending on the range of the thickness of the strip 1 to be handled, etc., but is, for example, a small size about the maximum thickness of the strip 1 to be handled. The eccentricity amount G2 may be the same as the eccentricity amount G1 described above, but may be different.
Further, as shown in FIG. 6, the second rotary shaft 44 is rotatably attached to the front second wall portion 42a by a bearing 71 (for example, a roller bearing) on the outer periphery of the front second shaft portion 44a. It is rotatably attached to the rear second wall portion 42b by a bearing 72 (for example, a roller bearing) on the outer periphery of the portion 44b. Further, as shown in FIG. 6, the second rotation shaft 44 is rotatably attached to the front first wall portion 41a by bearings 73 (for example, roller bearings) on the outer periphery of the front second eccentric shaft portion 44c. A bearing 74 (for example, a roller bearing) is rotatably attached to the rear first wall portion 41b on the outer periphery of the bi-axial shaft portion 44d.
Further, as shown in FIG. 6, the rear second shaft portion 44b of the second rotary shaft 44 extends rearward through the rear second wall portion 42b, and substantially extends with the rear second shaft portion 44b. The second motor 16 is disposed on the same center line. The second motor 16 is fixed to the aforementioned rear outer wall portion 42e of the second member 42 with the output shaft 16a thereof directed forward. The output shaft 16a of the second motor 16 extends forward of the rear outer wall 42e, and the coupling 75 is disposed in the space between the rear outer wall 42e and the rear second wall 42b. It is connected to the rear second shaft portion 44b. Thus, the second rotary shaft 44 is directly connected to the output shaft 16 a of the second motor 16 and driven by the second motor 16 to rotate.
Next, based on the above description, the characteristic configuration and operation of the mechanism 40 for displacing the first roll 11a with respect to the second roll 11b by the driving force of the first motor 14 and the second motor 16 will be described. The mechanism 40 is a rotary five-bar linkage mechanism in which all the pairs are mechanically rotational pairs (rotational pairs) as described above.
As can be understood from the structure shown in FIG. 5A, FIG. 6 and the like and the description so far, the mechanism 40 of this example is configured such that two identical link mechanisms are provided in parallel in the front-rear direction. That is, the mechanism 40 of this example includes a front link mechanism 40a and a rear link mechanism 40b driven by a common drive source (the first motor 14 and the second motor 16), and these front link mechanism 40a and the rear link The mechanism 40b is provided symmetrically with respect to a plane including the center line of the roll and orthogonal to the front-rear direction (a plane corresponding to the F cross section shown in FIG. 4).
Here, the front side link mechanism 40a includes a front side first wall portion 41a, a front side second wall portion 42a, a front side first shaft portion 43a and a front side first eccentric shaft portion 43c, a front side second shaft portion 44a and a front side. It is a five-node rotation type link mechanism in which the second eccentric shaft portion 44c and the front third member 45 form five nodes. The bearings as joints connecting the respective nodes of the front link mechanism 40a are bearings 61, 63, 65, 71, 73.
Further, the rear link mechanism 40b includes the rear first wall portion 41b, the rear second wall portion 42b, the rear first shaft portion 43b and the rear first eccentric shaft portion 43d, and the rear second It is a five-link rotation type link mechanism in which the shaft portion 44b, the rear second eccentric shaft portion 44d, and the rear third member 46 form five nodes. Bearings as joints connecting the respective nodes of the rear link mechanism 40b are bearings 62, 64, 66, 72, 74.
FIG. 12 is a diagram for easily understanding the mechanical configuration and operation of the mechanism 40 (the front link mechanism 40a and the rear link mechanism 40b), but the ratio of the length of the nodes and the angle of the nodes are different from the actual FIGS. 6A and 6B are diagrams showing the basic configuration and operation of the mechanism 40 in an easy-to-see manner. In the upper part of FIG. 12, the reference numerals attached to the joints (in this case, the joints realizing the turning couple) are the reference numerals of the corresponding bearings of the rear link mechanism 40b described above. However, the front link mechanism 40a and the rear link mechanism 40b have the same configuration and operation except that they are arranged differently, and even if the reference numerals of the corresponding bearings of the front link mechanism 40a are given, the same configuration and operation are obtained.
Here, the mechanical configuration illustrated in FIG. 12 is a mechanical framework when the mechanism 40 is viewed from the rear in the front-rear direction (that is, from the direction indicated by X in FIG. 1). In FIG. 12, a node (link D) between the joint 64 and the joint 66 is a node consisting of the first rotation shaft 43 (left eccentric shaft) and has a length corresponding to the eccentricity amount G1 described above. It is. Further, in FIG. 12, a node (link E) between the joint 72 and the joint 74 is a node consisting of the second rotation axis 44 (right eccentric axis) and has a length corresponding to the eccentricity amount G2 described above. It is.
Here, in the middle stage of FIG. 12, from the state of the upper stage of FIG. 12, the output shaft 14a of the first motor 14 is stopped at a fixed rotational position and only the second motor 16 is operated to rotate only the output shaft 16a. The right rotation (clockwise rotation) of the second rotation shaft 44 (link E) is viewed from the rear. In this case, the mechanism 40 can be regarded as a link mechanism with one four-joint degree of freedom, and the first member 41 (link B) as shown by a dotted line along with the clockwise rotation of the second rotation shaft 44 (link E). The third member 46 (link A) moves, and as a result, the first member 41 is displaced while being inclined so that the right side of the first member 41 mainly rises. Then, along with the displacement of the first member 41, the first roll 11a (upper roll) supported by the first member 41 is also displaced while being inclined so that the right side mainly rises.
Next, in the lower part of FIG. 12, from the state of the upper part in FIG. 12, the output shaft 16a of the second motor 16 is stopped at a fixed rotational position and only the first motor 14 is operated to rotate only the output shaft 14a. This is a case where only the first rotation shaft 43 is turned left (counterclockwise) when viewed from the rear. In this case, the mechanism 40 can be regarded as a link mechanism having four-joint degrees of freedom 1 and the first member 41 (link B as shown by a dotted line along with the counterclockwise rotation of the first rotation shaft 43 (link D). And the third member 46 (link A) move, and as a result, the first member 41 is displaced while being inclined so that the left side of the first member 41 mainly rises. Then, along with the displacement of the first member 41, the first roll 11a (upper roll) supported by the first member 41 is also displaced while being inclined so that the left side is mainly lifted.
Although not shown, as can be understood from the above description, the direction in which both motors 14 and 16 are simultaneously described from the upper state of FIG. 12 (the first rotation shaft 43 rotates counterclockwise, the second rotation shaft 44) can move the first member 41 so that the left and right end sides of the first roll 11a ascend as a whole by approximately the same distance.
Further, the first member 41 and the first roll 11a are described above by moving the motors 14 and 16 in the opposite direction to the direction described above (the first rotation shaft 43 is clockwise and the second rotation shaft 44 is counterclockwise). It is also possible to lower as in the rising operation (lowering mainly the right side, mainly lowering the left side, and further, approximately the same distance as a whole).
In addition, by simultaneously moving the motors 14 and 16 in a predetermined direction (for example, the direction in which the first rotation shaft 43 rotates clockwise and the second rotation shaft 44 also rotates clockwise), It is also possible to change the vertical direction position of only the other end side without changing the vertical direction position of one end side.
Therefore, according to the mechanism 40, the first roll 11a is displaced relative to the second roll 11b so that the distance between the first roll 11a and the second roll 11b can be varied independently and independently at both ends of each roll. It is possible to Furthermore, by controlling the rotational position of each of the motors 14 and 16, the distance (gap) at the left end position of the first roll 11a and the second roll 11b and the right end position of the first roll 11a and the second roll 11b The intervals (gaps) can be set independently and can be changed independently.
Next, an actual operation example of the mechanism 40 will be described with reference to FIGS. 9 to 11. 9 to 11 are cross-sectional views (mainly showing a C cross section in FIG. 4) substantially similar to FIG. 7 described above. However, FIGS. 9 to 11 also show the rear first shaft portion 43b and the rear second shaft portion 44b which can not be seen in the C cross section so that the eccentricity state of the rotary shafts 43 and 44 can be understood. 4 is a view including the D cross section in FIG. The specific numerals shown in FIGS. 9 to 11 are those of a prototype or the like, and are merely an example.
FIG. 9 shows a state in which the position of the first roll 11a and the rotational positions of the first rotation shaft 43 and the second rotation shaft 44 are at the origin (hereinafter referred to as the origin state). In the state of this origin, as shown in FIG. 9A, the distance between the first roll 11a and the second roll 11b (the distance between the outer peripheries of the central cylindrical portions sandwiching the strip material 1) is zero. As shown in 9 (b), from the center line of the second roll 11b (lower roll) to the lower edge of the outer circumference (the outer circumference of the central cylindrical portion sandwiching the strip 1) of the first roll 11a (upper roll) The distance is 31.5 mm, which is the radius of the second roll 11 b (lower roll).
Further, in the state of the origin, the direction of eccentricity of the first rotation shaft 43 (left eccentric shaft) and the second rotation shaft 44 (right eccentric shaft) is as shown in FIG. 9A.
That is, the center of the decentered portion of the first rotation shaft 43 such as the rear first eccentric shaft portion 43d is not eccentric such as the rear first shaft portion 43b in the plane of FIG. 9A. It is at a position separated by the eccentricity amount G1 to the lower right from the center of the part. And the distance of the above-mentioned up-and-down direction of these centers is 1.5 mm, as shown in Drawing 9 (a). Further, the center of the decentered portion of the second rotation shaft 44 such as the rear second eccentric shaft portion 44d is not eccentric such as the rear second shaft portion 44b in the plane of FIG. 9A. It is located at the lower left from the center of the part by the eccentricity amount G2. The distance between the centers in the vertical direction is also, for example, 1.5 mm.
Next, in FIG. 10, from the above-described origin state, only the second motor 16 is operated while the first motor 14 is stopped, and the second rotation shaft 44 (right side) is stopped while the first rotation shaft 43 is stopped at the origin state. A state in which only the eccentric shaft is rotated clockwise (hereinafter, referred to as a right side rotation state) is shown. In the right-handed rotation state, as shown in FIG. 10A, the first roll 11a ascends and rises together with the first member 41, and the right side of the first roll 11a ascends larger. In this rightward rotation state, as shown in FIG. 10A, the distance between the first roll 11a and the second roll 11b (the distance between the outer peripheries of the central cylindrical portions sandwiching the strip 1) is, for example, 0. It becomes 04 mm, and becomes 1.6 mm at the right end. Also, in this right-handed rotation state, as shown in FIG. 10 (b), the central cylindrical shape sandwiching the strip 1 from the center line of the second roll 11b (lower roll) from the center line of the first roll 11a. The distance to the lower edge of the outer circumference of the portion is larger than the radius of the second roll 11b (lower roll), and is 32 mm at the left end and 33 mm at the right end.
In the right side rotation state shown in FIG. 10A, the center of the eccentric portion of the second rotation shaft 44 such as the rear second eccentric shaft portion 44d and the eccentricity of the rear second shaft portion 44b It shows a state in which the second rotation shaft 44 is rotated clockwise until the distance in the vertical direction with respect to the center of the non-portion becomes about 0 mm, and the operating condition is slightly different from FIG. 10 (b) .
Further, the principle that the right side of the first member 41 and the first roll 11a (upper roll) is raised more largely in the right side rotation state is as described in the middle part of FIG.
Next, in FIG. 11, from the origin state described above, only the first motor 14 is operated while the second motor 16 is stopped, and the first rotation shaft 43 (left side) is stopped while the second rotation shaft 44 is stopped at the origin state. A state in which only the eccentric shaft is rotated counterclockwise (hereinafter, referred to as a left side rotation state) is shown. In the left-handed rotation state, as shown in FIG. 11A, the first roll 11a ascends and rises together with the first member 41, and the left side of the first roll 11a ascends larger. In this left-handed rotation state, as shown in FIG. 11A, the distance between the first roll 11a and the second roll 11b (the distance between the outer circumferences of the central cylindrical portions sandwiching the strip 1) is, for example, 1. It becomes 6 mm, and becomes 0.04 mm at the right end. Further, in the left side rotation state, as shown in FIG. 11B, a cylindrical shape in the center of the outer periphery (upper roll) of the first roll 11a (upper roll) from the center line of the second roll 11b (lower roll). The distance to the lower edge of the outer circumference of the portion is larger than the radius of the second roll 11b (lower roll), and is 33 mm at the left end and 32 mm at the right end.
In the left side rotation state shown in FIG. 11A, the center of the eccentric portion of the first rotation shaft 43 such as the rear first eccentric shaft portion 43d and the eccentricity of the rear first shaft portion 43b It shows a state in which the first rotation shaft 43 is rotated counterclockwise until the distance in the vertical direction with respect to the center of the non-portion becomes about 0 mm, and the operating condition is slightly different from FIG. It is different.
Further, the principle that the left side of the first member 41 and the first roll 11a (upper roll) is raised more largely in the left-handed rotation state is as described in the lower part of FIG.
Next, the operation including the feeding operation of the roll feeder 10 will be described together with the function of the control device 20 related to the roll feeder 10.
The control device 20 can initialize the vertical direction positions of both ends of the first roll 11a (upper roll), for example, by the operation input from the operation panel described above. Here, the two ends of the first roll 11a mean the left and right ends of the lower edge of the central cylindrical portion (the part holding the strip 1) of the first roll 11a. And in the case of this example, a state where the clearance between the lower edge of the cylindrical portion of the first roll 11a (upper roll) and the upper edge of the cylindrical portion of the second roll 11b (lower roll) is zero (FIG. 9) Specifically, the vertical length of the gap between the lower edge of the cylindrical portion of the first roll 11a and the upper edge of the cylindrical portion of the second roll 11b is It corresponds to the value of the vertical position of the first roll 11a. That is, the vertical length of the gap at the left end of the cylindrical portion of the first roll 11a and the second roll 11b corresponds to the value of the vertical position of the left end of the first roll 11a, for example, as shown in FIG. In the state of), the value of 0.04 mm corresponds to the value of the vertical position of the left end of the first roll 11a. The vertical length of the gap at the right end of the cylindrical portion of the first roll 11a and the second roll 11b corresponds to the value of the vertical position of the right end of the first roll 11a, for example, as shown in FIG. In the state of), a value of 1.6 mm corresponds to the value of the vertical position of the right end of the first roll 11a.
FIG. 13 (b) is a flowchart showing an operation of initial setting of vertical positions of both ends of the first roll 11 a described above. In this initial setting, the vertical position (Z1) of the reverse drive side (left end) of the first roll 11a is set first (step S1), and then the vertical position of the drive side (right end) of the first roll 11a The setting of (Z2) is performed (step S2), and then the vertical position of the reverse side (left end) and the driving side (right end) of the first roll 11a is set to the position (Z1, S2) set in steps S1 and S2, respectively. A move to Z2) is performed.
Here, in steps S1 and S2, for example, when the operator operates the operation panel of the control device 20, the values of the vertical position of the left end or the right end of the first roll 11a are respectively in predetermined units (for example, 0.001 mm units, 0 , 005 mm, or 0.01 mm, etc.). In a prototype manufactured by the applicant, a signal for controlling the rotational position of each motor (the first motor 14 and the second motor 16) is, for example, a pulse signal, and both ends of the first roll 11a per pulse of this pulse signal. It has been confirmed that the amount of movement in the vertical direction is approximately 0,001 mm, and that the position in the vertical direction can be set in such a fine unit as described above.
In step S3, for example, the rotational position (ie, the rotational position of each of the motors 14 and 16 that realizes the vertical position (Z1, Z2) set in steps S1 and S2 by the control device 20 according to preset data or program. The rotational positions of the first rotational shaft 43 and the second rotational shaft 44 are determined by calculation, and the upper and lower sides set by automatically operating the respective motors 14 and 16 to reach the determined rotational position. Movement to the direction position (Z1, Z2) is performed.
The movement in step S3 may be automatically started and executed under the control of control device 20 when the setting in steps S1 and S2 is completed, or the operator may perform the setting in steps S1 and S2. It may be configured to be executed under control of the control device 20 when an operation of instructing movement to the vertical position set to the control device 20 is performed.
According to the prototype manufactured by the applicant, it has been confirmed that the control of determining the positions by vertically changing the vertical positions of both ends of the first roll 11a with an accuracy of 0.01 mm or less is possible.
The above-described initial setting can be easily repeated several times while changing the numerical value to be input. Moreover, it is also possible to carry out the above-mentioned initial setting while passing the strip 1 through the roll feeder 10 (that is, keeping the strip 1 between the rolls 11a and 11b). The above-mentioned initial setting can be easily performed again with a different numerical value in consideration of the state of the camber of the strip 1 which has been fed out by temporarily stopping the feeding operation. For example, in order to know the numerical value of the vertical position that is optimal for the type and properties of the strip 1, it is possible to feed the strip 1 by actually performing the feeding operation of the strip 1 while changing the values set in steps S1 and S2. It is also possible to easily carry out trial and error work such as re-doing the above initial setting with different numerical values until the amount of camber is sufficiently reduced in view of the state of the camber of the strip material 1 as described above. However, for example, in the case of the strip material 1 whose optimum numerical value is known in advance as the numerical value set in steps S1 and S2, the above-described initial setting may be performed only once.
Next, when the equipment for feeding the strip 1 is in operation, the control device 20 displays the roll feeder 10 as shown in FIG. 14A, for example, according to various data preset by the operator and a program registered in advance. Perform control to operate. In addition to the preset values (Z1 and Z2) of the vertical position described above, the data set in advance includes the length of the feed period and interval period described later, the maximum value of the feed speed in the feed period, and the acceleration (during deceleration The feed amount (the length of sending the strip 1 in a single feed period) that determines the acceleration of (1), and setting data etc. for the vertical position of the left end and the right end of the first roll 11a in the interval period.
FIG. 14A is an example of a timing chart when the roll feeder 10 is in operation, where the horizontal axis is time, and the upper vertical axis is the vertical position of both ends of the upper roll (that is, both ends of the first roll 11a). The lower vertical axis is the feed speed. The feed speed is the rotational speed of the feed motor 12 and the second roll 11b (lower roll) driven thereby, and in the case of this example, the first roll 11a (upper roll) that rotates in synchronization with the second roll 11b. It is also the rotational speed of Further, the feeding speed is a feeding speed of the strip 1 pinched and fed by each roll in a normal state without slip.
In the timing chart in the upper part of FIG. 14A, the vertical position of the left end of the first roll 11a (the vertical position of the upper end of the upper roll) is indicated by a solid line, and the vertical position of the right end of the first roll 11a (upper roll right end The vertical position of) is indicated by a dotted line.
In the timing chart in the upper part of FIG. 14A, the minimum pressing amount for preventing the strip 1 from slipping due to the thickness of the strip 1 by the above-described initial setting in the vertical direction position (Z1) of the upper roll left end This is a specific example in which the vertical roll position (Z2) at the right end of the upper roll is set to a value obtained by subtracting the rolling down amount in addition to the minimum pressing down from the thickness of the material. .
In this case, as shown in the lower part of FIG. 14A, in the feed period, the feed speed rises to a predetermined maximum value (top speed) (that is, the feed motor 12 accelerates), and then the feed speed is increased. The feed motor 12 is controlled to be maintained at a predetermined maximum value (i.e., the feed motor 12 is operated at a constant speed) and then the feed rate is reduced to zero (i.e., the feed motor 12 decelerates and stops). As a result, the feeding operation of sending the strip material 1 by a set predetermined amount (that is, sending a fixed size) is performed. During this feeding period, the vertical position of the upper end of the upper roll is maintained at Z1 set in the initial setting, and the vertical position of the right end of the upper roll is maintained at Z2 set in the initial setting, Each motor (the first motor 14 and the second motor 16) is controlled. As a result, the strip 1 is fed while the right side of the strip 1 is rolled by the amount of depression of the rolling set in the initial setting, and correction for reducing the amount of camber can be realized (this effect will be described in detail) Will be described later). In addition, as shown to Fig.14 (a), the feed period mentioned above is periodically repeated according to operation | movement, such as a press machine etc., while the installation containing a press machine etc. is in operation.
Then, as shown in FIG. 14 (a), in the interval period between the feeding period and the next feeding period, the upper roll (the first roll 11a) is entirely on the upper surface of the material while the feed motor 12 is stopped. Ascends to a position higher than the position (the position of the upper surface of the strip 1), then is maintained at a position generally higher than the upper surface position of the material, and then descends back to the initialized position (Z1, Z2) Thus, each motor (the first motor 14 and the second motor 16) is controlled. As a result, a release period in which the strip 1 is released from the pinched state by each roll (that is, released) is realized during this interval period. In addition, usually, in the case of processing a material (strip 1) in a downstream press machine or the like, this release period is required because positioning is performed uniquely. If the roll feeder holds the strip 1 by the respective rolls, the movement of the strip 1 is impeded, which makes it difficult to position the strip 1 in a downstream press machine or the like. In the roll feeder 10 to which the present invention is applied, the release operation for forming the release period can be well realized by the mechanism 40 (link mechanism). Here, the release operation is an operation in which at least one of the rolls is moved in a direction away from the other roll such that the gap between the rolls is larger than the thickness of the strip as described above. is there.
According to the embodiment described above, the following effects can be obtained.
That is, according to the roll feeder 10 of the present embodiment, the first of the pair of rolls that realizes the feeding operation of the strip material by the operation of the two drive sources (the first motor 14 and the second motor 16) As the distance between the roll 11a and the other second roll 11b becomes variable independently at both ends of each roll, it is easy to adjust (or change) the relative distance and angle of these rolls Possible. Thus, the amount of camber of the strip 1 can be easily reduced by the roll feeder 10.
That is, for example, when a camber with a right curve is present in the strip 1 as shown on the right side of FIG. 14 (b), the left end of the first roll 11a as shown on the upper side of FIG. The setting value (Z1) of the vertical position of the first roll 11a is smaller than the thickness of the strip 1 by the minimum pressing amount, and the setting value (Z2) of the vertical position of the right end of the first roll 11a is added to the minimum pressing amount. The first roll 11a is inclined in the direction in which the right end approaches the second roll 11b by the amount of depression of rolling, if the amount of depression of rolling is set smaller than the thickness of the strip 1, and the feeding period The strip 1 is more strongly clamped at the right end side of the first roll 11a. As a result, during the feeding period, as shown on the right side of FIG. 14 (b), the right side of the strip 1 is appropriately stretched by holding the right side of the strip 1 more firmly with each roll and appropriately stretching it. By this elongation, the amount of right-handed camber is made substantially zero (or largely reduced), for example, the strip 1 is sent out to the wake as an ideal linear state (that is, after correcting the existing camber Can be sent out).
For example, as shown on the left side of FIG. 14 (b), when a camber having a left curve is present in the strip 1, contrary to the upper stage of FIG. 14 (a) described above, the right end of the first roll 11a The set value (Z2) of the vertical position is smaller than the thickness of the strip 1 by the minimum pressing amount, and the setting value (Z1) of the vertical position of the left end of the first roll 11a is added to the minimum pressing amount. If the amount of depression of rolling is set smaller than the thickness of the strip 1, the first roll 11a is inclined in the direction in which the left end approaches the second roll 11b by the amount of depression of rolling, during the feeding period. The strip 1 is more strongly clamped at the left end side of the first roll 11a. As a result, during the feeding period, as shown on the left side of FIG. 14 (b), the left side of the strip 1 is appropriately stretched by holding the left side of the strip 1 more firmly with each roll and appropriately stretching it. By this elongation, the amount of left-handed camber is made substantially zero (or greatly reduced), and the strip 1 is sent to the wake as, for example, an ideal linear state (that is, after correcting the existing camber Can be sent out).
As described above, according to the roll feeder 10 of the present embodiment, the direction of the camber present in the strip 1 is corrected to the left or right to correct the strip 1 into, for example, an ideal straight line state and feed it as a wake The camber of any orientation is extremely easy and short as compared with the conventional method using shims etc. only by setting the rotational positions of the two drive sources (first motor 14 and second motor 16). It is possible to correct the camber of the strip 1 by work. For this reason, various practically effective effects such as improvement of productivity (or efficiency of processing, etc.) in equipment using the roll feeder 10, improvement of quality of products and processed products, reduction of discarded materials, reduction of worn parts, etc. realizable. This effect is particularly remarkable when the material is aluminum.
Further, in the roll feeder 10 of this example, in addition to the movement of the camber straightening roll (in this case, the first roll 11a) by the mechanism 40 and the two drive sources, the roll of the interval period release operation. Movement is also realized. For this reason, compared with the case where a drive source and a drive mechanism are separately provided for the release operation, the configuration of the roll feeder 10 is greatly simplified, and the downsizing and cost reduction of the roll feeder are also realized.
Moreover, in the roll feeder 10 of the present embodiment, the mechanism 40 that allows the first roll 11a to be displaced relative to the second roll 11b is a 5-node link mechanism that can reduce backlash more than a screw mechanism or the like. It becomes possible to adjust (or change) the relative distance and angle of the rolls (the first roll 11a and the second roll 11b) with high accuracy and fineness. Thus, the camber correction and release operations described above can be performed with higher accuracy.
In particular, in the roll feeder 10 of the present embodiment, the mechanism 40 is a 5-node rotary type link mechanism (a link mechanism in which five nodes (links) are connected by five joints (joints) for achieving a rotating couple). The first roller 11a is driven by rotating the first rotating shaft 43 and the second rotating shaft 44, which are the two nodes (links) that make up this link mechanism, by the first motor 14 and the second motor 16, respectively. Can be operated with two degrees of freedom with respect to the second member 42 supporting the second roll 11 b. In addition, since it is a 5-node rotation type link mechanism, all joints (joints) connecting the nodes and the nodes can be generally constituted by rotary bearings (bearings) with less rattling compared with a slide mechanism, a screw mechanism and the like. For this reason, it is possible to easily adjust (or change) the relative distance and angle of the pair of rolls for the feeding operation by controlling the two motors 14 and 16 with high accuracy and fineness. In addition to the correction of the camber described above, the release operation can be well realized.
In the case where the drive transmission system for moving the roll (for example, the upper roll) includes an element with a large backlash such as a screw mechanism, as shown in FIG. On the other hand, a delay or an insufficiency occurs in the actual position change of the roll, which makes a good release operation difficult. Similarly, it is difficult to accurately and finely shift one of the rolls for correcting the strip camber. However, in the roll feeder 10 of this example, since there is no element with a large backlash such as a screw mechanism in the drive transmission system, such a problem does not occur, and for example, the ideal as shown in the upper stage of FIG. Position change can be realized by actual movement.
Further, in the roll feeder 10 of this embodiment, the front link mechanism 40a and the rear link mechanism 40b are provided as the mechanism 40, and these link mechanisms 40a and 40b are the centers of the rolls (the first roll 11a and the second roll 11b). It is configured to be symmetrically provided on the front side and the rear side with respect to a plane including the line and orthogonal to the front-rear direction (that is, the feeding direction of the strip material). As a result, at the time of the feeding operation for sandwiching the strip 1 by the rolls, the force by which, for example, the third members 45 and 46 press the first member 41 in the direction of pressing the first roll 11a against the second roll 11b Are dispersed on the side of the roll and on the side of the roll. For example, as shown by an arrow in FIG. 4, the force f by which the front first wall portion 41 a is pushed down by the third members 45 and 46 via the connecting shaft 47 and the rear first wall portion 41 b via the connecting shaft 47 The force f is distributed to the forces f pushed down by the third members 45 and 46, and these forces are in balance with the reaction force 2f applied to the first member 41 from the first roll 11a.
Moreover, in the aspect of the roll feeder 10 of the present embodiment, the first rotating shaft 43, the second rotating shaft 44, and the connecting shaft 47 are attached to (or connected to) either the front or rear wall at both ends. Support structure. For this reason, according to the aspect of the present embodiment, the stress and the deformation generated in the first member 41 and the respective rotation shafts 43 and 44 constituting the mechanism 40 are suppressed during the feeding operation of sandwiching the strip 1 by the roll. Problems such as deviation from the proper position and posture of the first roll 11a due to this deformation are suppressed. Therefore, along with the feeding operation which is the original function of the roll feeder, the force for sandwiching the strip 1 is appropriately biased in the width direction of the strip 1 (that is, the pressure in the axial direction of the roll for sandwiching the strip 1). It can be realized with high reliability and good reduction of the amount of camber of the strip material 1 by setting the distribution appropriately. Further, as described above, the force for pressing the first member 41 is dispersed, and each shaft has a double-supported support structure, thereby reducing the load of each bearing or the like that connects each shaft to the member and rotatably supports it. Therefore, there is also an effect of extending the life until the parts such as the bearing constituting the roll feeder are damaged by fatigue.
Furthermore, in the present embodiment, the second member 42 is, for example, a member fixed to a rack on which the roll feeder 10 is installed at the installation location, and the feed motor 12 for driving the roll is shown in FIG. It is attached to the side surface of the second member 42 in the axial direction of the roll, and the output shaft 12a of the feed motor 12 is connected to the second roll 11b, whereby the driving force of the feed motor 12 drives the second roll 11b. It is configured to be rotationally driven. The first motor 14 and the second motor 16 for moving the first roll 11a in the vertical direction are attached to the rear surface side of the second member 42 in the front-rear direction as shown in FIG. The output shafts of the motor 14 and the second motor 16 are connected to the first rotation shaft 43 and the second rotation shaft 44, respectively, and rotationally drive the first rotation shaft 43 and the second rotation shaft 44, respectively. .
Therefore, the installation space of the equipment including the roll feeder 10 in the front-rear direction (the feeding direction of the strip 1) can be reduced (or kept small). Since the feed motor 12 is disposed on the side surface of the second member 42 and the first motor 14 and the second motor 16 are disposed to project rearward on the rear surface of the second member 42, these motors are disposed. This is because the installation space does not increase in the front-rear direction in order to do so. As described with reference to FIG. 13A, the loop 1b (slack portion) of the strip 1 is provided on the rear side of the roll feeder 10 (the flow of the strip 1 on the upstream side of the roll feeder 10). In the case of the configuration of the present example in which the first motor 14 and the second motor 16 are disposed rearward as described above, a vacant space above the loop 1 b (for example, the above-described The space above the R guide 10a shown in FIG. 13 (a) is effectively used as the arrangement space for the first motor 14 and the second motor 16, and the installation space is increased by the arrangement of the first motor 14 and the second motor 16 Absent. Further, in the roll feeder 10 of this example, the mechanism 40 including the front link mechanism 40a and the rear link mechanism 40b is disposed mainly in the upper space of each roll (the first roll 11a and the second roll 11b). Also in terms of the arrangement of the mechanism 40, the empty space is effectively used and the installation space in the front-rear direction is not enlarged.
The present invention is not limited to the above-described first embodiment, and various modifications and applications may be made.
For example, the operation mode (operation pattern) of the movable side roll (the first roll 11a which is the upper roll in the first embodiment) controlled by the control device 20 is not limited to the mode illustrated in the upper stage of FIG. For example, the aspect shown in FIG. 15 (a) or FIG. 15 (b) may be used. Here, in the mode shown in FIG. 15A and FIG. 15B, the maximum value of the vertical position of the upper roll right end in the release period described above is the same position as the upper roll left end. That is, in the release operation, the upper roll right end is also raised to the same height as the upper roll left end. Among them, the mode shown in FIG. 15 (b) raises the right end of the upper roll at a higher speed at the start of the release operation and the speed of the right end of the upper roll at the higher speed at the end of the release operation. It is a mode to which it descends. In this case, in order to correct the camber of the strip 1, the upper roll right end is slightly lowered in the vertical direction of the feeding period than the upper roll left end, but downward. For this reason, as shown in FIGS. 15A and 15B, the upper end of the upper roll is raised and lowered at high speed than the upper end of the upper roll at the time of release operation. The release operation can be realized with the same margin, and the release period can be increased without changing the above-mentioned interval period. The relationship between the upper roll right end and the upper roll left end is reversed if the direction of the camber of the strip 1 changes.
Next, the configuration of the mechanism 40 is not limited to the configuration in which two link mechanisms are provided in parallel as described above, and may be, for example, only the front link mechanism 40a or only the rear link mechanism 40b.
For example, FIG. 16 (a) is a perspective view showing a structure of a modification of a roll feeder in which the mechanism 40 comprises only the rear link mechanism 40b. In FIG. 16A, the components corresponding to the components of the first embodiment described above are denoted by the same reference numerals, and the first member 41, the second member 42, etc. are partially shown to show the inside. The broken state is illustrated.
As described above, the structure can be simplified as an aspect including only the link mechanism on one side, and cost reduction and the like can be achieved. However, in the case of this aspect, the force pressing the first member 41 in the direction of pressing the first roll 11a against the second roll 11b during the feeding operation of sandwiching the strip 1 by the roll The effects distributed to the forward side and the front side disappear. For example, in the case where only the rear link mechanism 40b is used as shown in FIG. 16A, the two forces f shown in FIG. 4 are the third member 46 with the rear first wall portion 41b via the connecting shaft 47, for example. The force changes only to a force 2 f (not shown) pressed down by this force, and this force balances with the reaction force 2 f applied to the first member 41 from the first roll 11 a. Moreover, in the aspect shown to Fig.16 (a), the 1st rotating shaft 43, the 2nd rotating shaft 44, and the connecting shaft 47 are attached to (or connected with) only the wall part 41b or 42b of back side, and are supported. Support structure. For this reason, in the mode of FIG. 16 (a), the stress and deformation generated in the first member 41 and the respective rotation shafts 43, 44, etc. constituting the mechanism 40 are relatively large during the feeding operation of sandwiching the strip 1 by the roll. It tends to be large, and it is necessary to increase the strength by increasing the thickness of each member and the diameter of the rotation shaft to suppress the adverse effects such as the deviation from the proper position and posture of the first roll 11a due to this deformation. There is.
Further, the roll which can be displaced in the roll feeder may be a lower roll (lower roll) of a pair of rolls for holding the material. For example, a structure obtained by inverting the structure of the first embodiment shown in FIGS. 2 and 3 up and down may be in principle possible.
Further, the lower synchronous gear 53 and the upper synchronous gear 50 for synchronizing the rotation of each roll may be omitted.
Next, in the first embodiment described above, an example in which the present invention is applied to the roll feeder 10 in the equipment configuration illustrated in FIG. 13A has been described, but the scope of application of the present invention is limited to this Absent.
For example, the present invention is applied to the component as a roll feeder in the leveler feeder 5 shown in FIG. 13 (a), and in the equipment configuration illustrated in FIG. 13 (a) The correction of the In this case, since the correction of the camber of the strip 1 is also performed by the leveler feeder 5 in addition to the correction for flattening the strip 1, the roll feeder 10 thereafter has the strip 1 with a camber amount of zero or a slight amount. It will be good if it sends out as it is. That is, in this case, the roll feeder 10 can be specialized to the original feeding operation.
Further, in the equipment configuration illustrated in FIG. 13A, the present invention is applied to both the leveler feeder 5 and the roll feeder 10, and both the leveler feeder 5 and the roll feeder 10 have cambers of the strip 1 in multiple stages, for example. There may also be a mode in which correction is performed.
Moreover, it is set as the installation configuration which deleted one of the leveler feeder 5 or the roll feeder 10 in the installation configuration illustrated to Fig.13 (a), applies this invention to the leveler feeder 5 or the roll feeder 10 in this installation configuration, The said leveler feeder There may also be an aspect in which the camber is corrected by the 5 or roll feeder 10.

1 Band material (material)
10 roll feeder 11a feed roll (upper roll, first roll, roll)
11b Feed roll (lower roll, second roll, roll)
12 Motor (feed motor)
14 Motor (1st motor)
16 motor (second motor)
40 mechanism 40a front side link mechanism 40b rear side link mechanism 41 first member 41a front side first wall portion 41b rear side first wall portion 41c left side first wall portion 41d right side first wall portion 42 second member 42a front side second wall portion 42b rear side second wall portion 42c left side second wall portion 42d right side second wall portion 43 first rotation shaft 43a front side first shaft portion 43b rear side first shaft portion 43c front side first eccentric shaft portion 43d rear side first Eccentric shaft 44 Second rotating shaft 44a Front second shaft 44b Rear second shaft 44c Front second eccentric shaft 44d Rear second eccentric shaft 45 Third member (front third member)
46 Third member (rear third member)
47 connecting shaft

Claims (4)

1. A roll feeder comprising a pair of rolls for realizing a feeding operation of a strip material by holding the strip material and rotating it.
   The first roll relative to the second roll such that the distance between the first roll, which is one of the rolls, and the second roll, which is the other of the rolls, is separately variable at each end of each roll A mechanism that makes it displaceable,
   And a plurality of driving sources for driving an operation of displacing the first roll relative to the second roll by the mechanism.
2. The roll feeder according to claim 1, wherein the mechanism is a five-bar linkage.
3. The mechanism is driven by a first motor which is one of the drive source, a first member rotatably supporting the first roll, a second member rotatably supporting the second roll, and the drive source. A node having a first rotating shaft, a second rotating shaft disposed parallel to the first rotating shaft and driven by a second motor which is the other of the drive sources, and a third member Nodal rotation type link mechanism,
   A first shaft portion rotatably attached to the second member and rotationally driven by the first motor, and the first rotation shaft is provided eccentrically on an extension of the first shaft portion; 1 with eccentric shaft,
   The second rotation shaft is rotatably attached to the second member at a position different from the first shaft portion so as to be parallel to the first shaft portion, and rotationally driven by the second motor. And a second eccentric shaft portion provided eccentrically on an extension of the second shaft portion and rotatably mounted on the first member,
   The third member is rotatably attached to the first member by a connecting shaft having one end side parallel to the first rotating shaft, and the other end is rotatably attached to a first eccentric shaft portion of the first rotating shaft The roll feeder according to claim 2, characterized in that:
4. The first rotation shaft, the second rotation shaft, and the connection shaft are disposed in a torsional positional relationship with respect to the roll, and the first rotation shaft, the second rotation shaft, and the connection are provided. The axial direction of the shaft is set to be 90 degrees different from the axial direction of the roll,
   The first member is a front first wall portion located forward of the center line of the roll in the front-rear direction, and a rear first wall portion located rearward of the center line of the roll in the front-rear direction Have and
   The second member includes a front second wall portion positioned forward of the front first wall portion in the front-rear direction, and a rear side second rear portion positioned rearward of the rear first wall portion in the front-rear direction With 2 walls,
   The third member is a front third member located on the front side with respect to the center line of the roll in the front-rear direction and having one end rotatably attached to the first front wall by the connecting shaft; There is provided a rear third member which is positioned rearward of the center line of the roll in the direction and one end of which is rotatably attached to the rear first wall by the connecting shaft,
   The first rotation shaft is, as the first shaft portion, a front first shaft portion rotatably attached to the front second wall portion, and a rear side first rotatably mounted to the rear second wall portion. A front first eccentric shaft portion rotatably attached to the other end side of the front third member as the first eccentric shaft portion and having the shaft portion, and the other end side of the rear third member And a rear first eccentric shaft portion rotatably mounted on the
   The second rotation shaft is, as the second shaft portion, a front second shaft portion rotatably attached to the front second wall portion, and a rear side second rotatably attached to the rear second wall portion. It has a shaft, and as the second eccentric shaft, it is rotatably attached to the front second eccentric shaft that is rotatably attached to the front first wall and to the rear first wall. And a rear second eccentric shaft portion,
   The mechanism comprises a front link mechanism and a rear link mechanism,
   The front side link mechanism includes the front side first wall portion, the front side second wall portion, the front side first shaft portion and the front side first eccentric shaft portion, the front side second shaft portion and the front side second eccentricity. It is a 5-node rotation type link mechanism which makes a shaft part and said front 3rd member a node,
   The rear side link mechanism includes the rear side first wall portion, the rear side second wall portion, the rear side first shaft portion and the rear side first eccentric shaft portion, and the rear side second shaft portion. And a 5-node rotary type link mechanism having a rear second eccentric shaft portion and the rear third member as nodes.
   The front link mechanism and the rear link mechanism are provided on the front side and the rear side with respect to a plane including the center line of the roll and orthogonal to the front-rear direction. Roll feeder described in.

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