JP2009056469A - Feed device of belt-like material - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To provide a feed device wherein the swinging of a loop is prevented even when feeding at high speed, as the feed device of a belt-like material, wherein a loop is formed between two feed mechanisms on the upstream side and the downstream side. <P>SOLUTION: The feed device of the belt-like material which is composed of an upstream-side feed mechanism (leveler feeder 5) for feeding the belt-like material on the upstream side of a line for supplying the belt-like material 1 and a downstream-side feed mechanism (roll feeder 10) for feeding the belt-like material on the downstream side of this upstream-side feed mechanism and in which the loop 1b is formed between the two feed mechanisms to absorb the difference between the feed motions of the two feed mechanisms, is constituted by providing a controlling means (controller 40) for controlling the feed motion of each feed mechanism so that the difference between acceleration of feed motions in the two feed mechanisms does not approximately exceed gravitational acceleration. <P>COPYRIGHT: (C)2009,JPO&INPIT

Description

  The present invention relates to a feeding device that supplies a strip material to a press machine, for example.

In general, a processing step of continuously supplying a thin strip material (strip material) made of steel, aluminum, or the like to a press machine or the like to perform press processing or cutting processing is as shown in FIG. 9A, for example. This is done by a series of equipment. That is, the belt-shaped material 1 wound in a coil shape (that is, the coil material 1a) is rotated in the unwinding direction by a machine called an uncoiler so that the belt-shaped material 1 is fed out from the outer periphery as needed, and the wake of this uncoiler ( In the upstream of a press machine, etc., the belt 1 is straightened through a straightening device (so-called leveler) and then straightened by a machine called a roll feeder (or coil feeder) to the press machine by a predetermined amount. On the other hand, it sends out and positions and performs press work (refer patent documents 1 and 2).
In addition, as shown to Fig.9 (a), R guide which contacts the lower surface of the edge of the slack part of the said strip | belt-shaped material is each provided in the downstream of the leveler, and the upstream of the roll feeder. Conventionally, such a distance between the R guides has been a fixed value determined by, for example, the maximum line thickness specification of the line. Normally, the allowable radius of curvature of the steel sheet (the limit curvature at which plastic deformation does not occur) is about 500 times the plate thickness. For example, when the maximum plate thickness of the steel plate is 3.2 mm, between the R guides The distance is fixed to 3200 mm (= 3.2 × 500 × 2).

  In the above equipment, the roll feeder includes a feeding mechanism including at least a pair of feed rolls that realizes a feeding operation of the strip 1 by sandwiching and rotating the strip 1, and the leveler includes a similar feeding mechanism. However, the roll feeder operates intermittently in response to the request of the belt-side material supply side device (that is, a press machine, for example), and realizes the feeding operation requested at a predetermined timing as fast as possible. On the other hand, the leveler and the uncoiler conventionally perform the feeding operation of the strip 1 continuously at a constant speed, although the speed is generally switched stepwise as will be described later. For this reason, in order to absorb such a difference in feeding operation, a slack portion of the belt-like material 1 as indicated by reference numeral 1b in FIG. Called a loop 1b) in the following. This is because, as described in Patent Document 1, since the inertia of the uncoiler including the coil material 1a is very large, it is difficult to intermittently operate the leveler and the uncoiler at the same acceleration as the roll feeder.

  As a general example, levelers and uncoilers are driven as follows. That is, as shown in FIG. 9A, a loop sensor for detecting the sag of the loop 1b (hereinafter referred to as the loop amount) in stages is provided in the loop pit, and a plurality of loop amounts of the loop 1b are set. Which of the ranges (A1, A2, A3, A4 from the smallest) is detected. As shown in FIG. 9B, when the loop amount of the loop 1b is in the range A1, the speed of the leveler or the like is controlled to a high speed (speed larger than the average feed speed of the roll feeder), and the loop amount is When in the range A2, the speed of the leveler or the like is controlled to a medium speed (a speed lower than the high speed), and when the loop amount is in the range A3, the speed of the leveler or the like is set to a low speed (a speed lower than the medium speed). When controlled and the loop amount is in the range A4, the speed of the leveler or the like is controlled to zero (ie, stopped). Conventionally, the acceleration (including negative acceleration during deceleration) when switching the speed of the leveler or uncoiler is set to a sufficiently small value in consideration of the large load (the large inertia described above) in the uncoiler. Therefore, it is much smaller than the acceleration (including negative acceleration during deceleration) during the feeding operation performed by the roll feeder.

By the way, in a roll feeder that finally feeds the strip 1 to a press machine or the like, a higher speed and higher acceleration feed (i.e., higher top speed and acceleration / deceleration time) due to demands for improving productivity and the like. Short feed) is required.
In particular, in a press processing facility using a servo press that has recently been developed as an alternative to the conventional double crank type die cutting machine and hydraulic type die cutting machine, the acceleration required for the feeding device is from 1G to 2G. More than ever. The servo press is a die-cutting machine that pressurizes the die-cutting part by controlling the servo motor, and can arbitrarily set the die-cutting speed, position, and pressure.

JP 2003-181573 A JP 2004-142876 A

  However, the inventors have clarified that the above-mentioned conventional feeders such as roll feeders have the following problems in realizing the required high acceleration of 2G or more. Yes. That is, when the acceleration of the feeding operation of the roll feeder is increased in the conventional apparatus configuration, the loop 1b is swayed, and there is a risk of damaging the belt 1 or the machine such as the roll feeder as well as noise. There was a problem of getting bigger.

FIG. 6 is a diagram for explaining the swing of the loop 1b. FIGS. 6 (a) to 6 (c) are diagrams for explaining the lifting of the loop 1b. FIGS. 6 (d) to 6 (e) are diagrams. It is a figure explaining the rolling of the said loop 1b.
Among these, Fig.6 (a) is a figure which shows the state of the loop 1b at the time of acceleration of the feed operation of a roll feeder. As shown in this figure, when the roll feeder is accelerated, the downstream side of the loop 1b is suddenly sent to the downstream side, so that the loop 1b changes from the state indicated by the dotted line to the state indicated by the solid line. Next, FIG.6 (b) is a figure which shows the state of the loop 1b at the time of deceleration of the feed operation of a roll feeder. As shown in this figure, when the roll feeder is decelerated, the loop 1b floats due to inertia from the state indicated by the dotted line to the state indicated by the solid line, and in the vicinity of the downstream side R guide (that is, the roll feeder side R guide). 1 buckling occurs, and in this vicinity, the belt-like material 1 rises greatly locally. Next, FIG.6 (c) is a figure which shows the state of the loop 1b after the feed operation of a roll feeder stops. As shown in this figure, after the roll feeder is stopped, the local lift generated at the time of deceleration propagates upstream. In particular, the higher the acceleration of the roll feeder exceeds 1G of gravitational acceleration, the more remarkable the jump.

Next, FIG.6 (d) is a figure which shows the state of the loop 1b at the time of the feed operation of a roll feeder. As shown in this figure, during the feeding operation of the roll feeder, the downstream side of the loop 1b is suddenly brought to the downstream side and the feeding operation on the leveler side seems to be delayed, so the state shown by the solid line from the state shown by the dotted line The loop 1b changes (i.e., changes in the direction in which the loop amount decreases particularly on the downstream side). Next, FIG.6 (e) is a figure which shows the state of the loop 1b after the feed operation of a roll feeder stops. As shown in this figure, after the roll feeder is stopped, only the leveler-side feeding operation continues. Therefore, the loop 1b is indicated by a solid line from the state indicated by the dotted line so as to compensate for the downstream part that is carried. The state changes (that is, the loop 1b moves downstream), and rolls occur.
In actuality, the above-described lifting and rolling are combined, and the swinging movement of the loop 1b is generated.

  Accordingly, the present invention provides a belt-shaped material feeding device in which a loop is formed between two feeding mechanisms on the upstream side and the downstream side, and the feeding device prevents the loop from shaking even at high-speed feeding. It is an object.

The belt-like material feeding device of the present application includes an upstream-side feeding mechanism that sends the belt-like material upstream of a line that supplies the belt-like material, and a downstream-side feeding mechanism that sends the belt-like material downstream from the upstream-side feeding mechanism. In order to absorb the difference in the feeding operation of the upstream feeding mechanism and the downstream feeding mechanism, a slack portion of the strip material is formed between the upstream feeding mechanism and the downstream feeding mechanism. A material feeder,
Control means for controlling the feed operation of the upstream feed mechanism and the downstream feed mechanism so that the difference in acceleration between the feed operation of the upstream feed mechanism and the feed operation of the downstream feed mechanism does not exceed substantially gravitational acceleration. It is provided with.

Here, “upstream side feed mechanism” and “downstream side feed mechanism” mean a feed mechanism (mechanism having a function of feeding material) on both sides of a portion where a slack (loop) of the belt-like material is formed, For example, the leveler and roll feeder in the above-described strip-shaped material supply facility may be used, and when a loop is formed between the uncoiler and the leveler, the uncoiler and the leveler may be used. When a loop is formed between two roll feeders, the roll feeder on the upstream side of the loop corresponds to the “upstream feeding mechanism”, and the roll feeder on the downstream side of the loop becomes the “downstream feeding mechanism”. Equivalent to. In other words, the “upstream side” of the “upstream side feed mechanism” merely means that it is relatively upstream from the “downstream side feed mechanism”.
“Gravity acceleration” means so-called 1G.

  In the feeding device of the present application, control is performed so that the difference in acceleration between the feeding operation of the upstream feeding mechanism and the feeding operation of the downstream feeding mechanism does not exceed substantially gravitational acceleration. That is, for example, when the feed operation of the downstream feed mechanism is in the 2G acceleration state, the feed operation of the upstream feed mechanism is at least 1G acceleration state, and conversely, the feed operation of the downstream feed mechanism is in the 2G deceleration state. In some cases, the feed operation of the upstream feed mechanism is set to a deceleration state of at least 1G. For this reason, the relative acceleration of the loop is always about 1 G or less and does not exceed the substantially gravitational acceleration, so that the loop vibration described above is greatly reduced. In addition, the inventors have confirmed through experiments that the loop shake described above occurs remarkably at 1 G or more. In addition, when accelerating and decelerating the downstream side feed mechanism at 2G, for example, it is confirmed by experiments that if the upstream side feed mechanism is accelerated and decelerated at 1G at the same time, the loop between the feed mechanisms hardly fluctuates.

Next, in a preferred aspect of the present application, the control means intermittently performs a feed operation in which the downstream feed mechanism is operated with a trapezoidal or triangular downstream speed change pattern in response to a request of a device to which the strip-shaped material is supplied. The upstream side feed mechanism also intermittently executes a feed operation that operates with a trapezoidal or triangular upstream side speed change pattern, and the top of the downstream side speed change pattern and the upstream side speed change pattern The configuration is such that the feed operation of the upstream feed mechanism is synchronized with the feed operation of the downstream feed mechanism so that the center position coincides with the time axis, and the difference in acceleration does not exceed the gravitational acceleration. Parameters for determining the inclination of the acceleration / deceleration unit of the downstream speed change pattern and the upstream speed change pattern (for example, acceleration time, deceleration time and rated speed illustrated in FIG. 8A) are set. And the downstream speed so that the feed amount by one feed operation (feed operation for one trapezoidal or triangular speed change pattern) is the same in the upstream feed mechanism and the downstream feed mechanism. The trapezoidal or triangular areas formed by the change pattern and the upstream speed change pattern are set to be the same.
In addition, the “upstream feed mechanism” in this aspect, like the “downstream feed mechanism”, needs to perform the feed operation intermittently in response to the request of the belt-side material supply side device. Due to the size, it is usually difficult to apply this embodiment to an uncoiler. For this reason, this aspect is normally applied to other than an uncoiler (for example, a leveler or a leveler feeder and a roll feeder, or a roll feeder and a roll feeder).

  Such an aspect further has the following effects. That is, since the top center position of the downstream speed change pattern and the upstream speed change pattern coincide with each other on the time axis, the acceleration at the time of acceleration / deceleration is different and the start time and the end time of the feed operation are different. Since the feeding operations of the upstream feeding mechanism and the downstream feeding mechanism are synchronized (that is, semi-synchronized), the deformation of the loop is extremely small, and the vibration of the loop is particularly reduced. Further, as described above, the upstream feed mechanism and the downstream feed mechanism are semi-synchronized, and the feed operation is relatively different in a slight period during acceleration / deceleration, and the deviation of the feed amount in that period. However, since only a small feed amount is required, the loop amount itself can be remarkably reduced. When the loop amount is reduced, there is no need to provide a large space for loops (for example, loop pits). Further, when the loop amount is reduced, the shaking object itself becomes smaller (lighter), so that the energy of the shaking is reduced, and there is an advantage that the machine damage and noise due to the shaking are further reduced. In addition, since the feed amount by one feed operation is the same in the upstream feed mechanism and the downstream feed mechanism, the loop amount is calculated except that the loop amount slightly fluctuates during acceleration / deceleration of the feed operation. Always constant. If the loop amount becomes constant, depending on the operating conditions such as the strip thickness and feed length, find a loop amount with particularly small fluctuations in advance and set that loop amount to minimize the loop amount. It is possible to always hold it, and also in this respect, the vibration of the loop can be reduced.

  Next, the feeding device of the present application is provided with R guides that are in contact with the lower surface of the end of the slack portion of the belt-like material on the downstream side of the upstream feeding mechanism and the upstream side of the downstream feeding mechanism, The distance between these R guides is variable.

  With such a configuration, the distance between the R guides is changed to the minimum value according to the plate thickness of the belt-like material, and the loop is made at the limit of the allowable curvature radius of each plate thickness (the limit curvature at which plastic deformation does not occur). It can be formed and has the following advantages. First, the material can be given tension according to the plate thickness, and this tension can limit the degree of freedom of loop shaking, thereby further reducing loop shaking. Further, by using the tension of the material to propagate the kinetic energy supplied from the upstream feed mechanism, the acceleration / deceleration (inertia) pulled by the downstream feed mechanism can be absorbed or offset. Further, the contact area of the material with the R guide is increased, the holdability is increased, the degree of freedom of the material swinging can be reduced, and also from this point, the loop swing can be reduced. If the R guide is unnecessarily separated, the contact area with the R guide is reduced, and the degree of freedom of the material around the fulcrum of the swing as shown in FIG.

  According to the belt-shaped material feeding device of the present invention, it is possible to significantly reduce the loop vibration described above.

Hereinafter, embodiments of the present invention will be described with reference to the drawings.
FIG. 1 is a diagram showing a configuration of the feeding device of this example. FIG. 2 is a diagram showing changes in the feed speed and the like in a single feed operation of the leveler feeder 5 and the roll feeder 10 to be described later, with the upper part showing the temporal change of the feed amount and the lower part showing the temporal change of the feed speed. Indicates. 3A and 3B are diagrams for explaining the setting of the distance between the R guides. FIG. 3A shows a case where the plate thickness is relatively thick, and FIG. 3B shows a case where the plate thickness is relatively thin. FIG. 4 is a side view showing a specific example of the roll feeder. FIG. 5 is a diagram for explaining an example of the control system of the roll feeder 10.

  As shown in FIG. 1, the present apparatus includes an uncoiler 2 that rotates the coil material 1 a in the unwinding direction and feeds the belt-shaped material 1 from the outer periphery as needed, and a leveler that corrects flatly through the belt-shaped material 1 downstream of the uncoiler 2. A feeder 5, a roll feeder 10 that sends and positions the straight strip 1 after correction to the press machine or the like by a predetermined amount downstream of the leveler feeder 5, and the roll feeder 10 and the leveler feeder 5 are fixed as described later. A controller 40 that operates intermittently and basically continuously operates the uncoiler 2 at a constant speed (however, with speed switching).

  Here, as shown in FIG. 1, the roll feeder 10 includes at least a pair of feed rolls 11a and 11b that realize a feeding operation of the strip 1 by sandwiching and rotating the strip 1 and the feed rolls 11a and 11b. A motor 12 (for example, a servo motor) that drives at least one of them, and a position detector 13 (for example, a pulse generator; a so-called encoder) that outputs a position detection signal corresponding to the rotation of the motor 12. Further, on the upstream side of the roll feeder 10, there is provided an R guide 10a (consisting of a plurality of guide rolls 30 described later in this example) that comes into contact with the lower surface of the end of the slack portion (loop 1b) of the strip 1. Yes. The operation of the motor 12 is feedback-controlled by a controller 14 (shown in FIG. 5) that forms part of the control device 40.

Referring to the specific example of FIG. 4, the roll feeder 10 includes guide rolls 30 and 31 and a pair of feed rolls 11 a and 11 b arranged along the passing position of the belt-shaped material 1. And a controller 14 (shown in FIG. 5) and an operation panel (not shown).
Here, the guide rolls 30 and 31 are rotatably provided on the inlet side of the strip 1 and guide the strip 1 toward the feed rolls 11a and 11b. Among these, the guide roll 30 constitutes the R guide 10a, and the position in the left-right direction (feeding direction of the belt-like material 1) is variable by, for example, a support mechanism indicated by reference numeral 10b in FIG. . The position change of the R guide 10a may be performed by human power, but may be configured such that some kind of actuator is provided to drive the R guide 10a and the position change is performed without human power.
The support mechanism 10b has a structure in which a leg 10c is extended below a member that supports both ends of the guide roll 30 constituting the R guide 10a, and a caster 10d that rolls on the floor is attached to the lower end of the leg 10c. Between the R guide 10a and the main body portion of the roll feeder 10, a guide 10e that can be expanded and contracted in the feed direction is provided, and the R guide 10a is moved away from the main body portion of the roll feeder 10 (for example, FIG. 1). In the state shown in (b), the guide 10e guides the strip 1 between the R guide 10a and the main body portion of the roll feeder 10.

  The feed rolls 11a and 11b are rolls that apply a force for feeding the strip 1 to the downstream equipment (for example, a press) to the strip 1 and are rotatably arranged with the strip 1 sandwiched therebetween. In this case, the lower feed roll 11b is rotationally driven by the motor 12 disposed below the lower feed roll 11b. 4, reference numerals 32, 33, and 34 denote a belt (for example, a timing belt) and a pulley for decelerating and transmitting the rotation output of the motor 12 to the feed roll 11b. The motor 12 is a servo motor, and an encoder 13 (drive side position detector) that receives the rotation of the output shaft of the motor 12 is coaxially attached.

  Next, the operation panel is an operation unit that is electrically connected to a host device that constitutes a feed length setting unit 16 (shown in FIG. 5) described later, and various push buttons and display units for operation are provided on the upper surface. Is provided. Manual operation of the motor 12 and various data setting operations can be easily performed from the operation panel. In addition, as data set by the operator in advance from the operation panel, the target feed amount in one feed operation of the strip 1 (the strip 1 is predetermined for the operation of one cycle of the press machine, for example, a press machine). (Feed length when sending at timing), rated speed (top speed) illustrated in FIG. 8A, acceleration time and deceleration time illustrated in FIG. 8A, and the like.

  In addition, what is shown with the code | symbol 15 in FIG. 5 is a position speed conversion part which produces | generates a speed feedback value by differentiating a position detection signal (output of the position detector 13). Reference numeral 16 denotes a feed length setting unit that appropriately sets and outputs a position command (command value for the rotational position of the motor 12) according to a feed amount set by a user operation, for example. Reference numeral 17 denotes a speed command generation unit that generates and outputs a speed command (command value for the rotational speed of the motor 12) according to a deviation (positional deviation) between the position command and the position feedback value. Reference numeral 18 denotes a torque command generator that generates and outputs a torque command (output torque of the motor 12, that is, a command value of the current of the motor 12) according to a deviation (speed deviation) between the speed command and the speed feedback value. It is. Reference numeral 19 denotes a motor drive signal (for example, duty of a drive circuit when the motor 12 is PWM-driven) according to a deviation (torque deviation) between the torque command and a torque feedback value (current detection value of the motor 12) described later. This is a motor drive signal generator that generates and outputs a signal for instructing the ratio. Reference numeral 20 denotes a motor drive unit (a so-called servo control amplifier) that controls energization of the motor 12 in accordance with the motor drive signal.

  Here, the feed length setting unit 16 includes means (for example, a sequencer) that receives an operation signal (or setting data) from an operation panel (not shown) and performs control processing in accordance with a set program. Is a synchronous signal (for example, an absolute encoder or a rotary cam for detecting the rotational position of the crankshaft of the press machine) in order to feed the strip 1 by a feed amount set at a predetermined timing. While reading a signal of a switch or the like, or a signal in place of such a signal), a signal or data for instructing the target rotational position of the motor 12 is generated and output (or written) to the speed command generator 17. Is.

  The motor drive unit 20 includes, for example, a drive circuit for PWM driving the motor 12 (for example, a bridge circuit in which four switching elements such as FETs are connected to the motor 12 in an H-bridge shape), and this drive circuit. And a current detection circuit for detecting a current value of the motor 12 as a torque feedback value.

The controller 14 may be provided as an integrated unit that includes all of the above-described elements, but is typically configured from a plurality of units. For example, the host device as the feed length setting unit 16 and the speed command generation unit 17, the position / speed conversion unit 15, the torque command generation unit 18, the motor drive signal generation unit 19, and the drive unit as the motor drive unit 20 Consists of units.
In any case, according to the controller 14, the motor 12 is driven so that the deviation of the rotational position of the motor 12 (difference between the command value and the feedback value) always approaches zero. Only the feed amount set at a predetermined timing synchronized with the operation of the facility is sent out.

  Next, unlike the level feeder, the leveler feeder 5 is capable of feedback control of the feeding operation similarly to the roll feeder 10. For example, as shown in FIG. 1, in addition to the correction rollers 6 arranged alternately for correction, at least a pair of feed rolls 7a that realize the feeding operation of the band 1 by sandwiching and rotating the band 1 7b, a motor 8 (for example, a servo motor) that drives at least one of the feed rolls 7a and 7b, and a position detector 9 (for example, a pulse) that outputs a position detection signal corresponding to the rotation of the motor 8. Generator; so-called encoder). Further, on the downstream side and the upstream side of the leveler feeder 5, R guides 5a and 5b (for example, the guide rolls described above) that contact the lower surface of the end of the slack portion (the loop 1b or the loop 1c described later) of the strip 1 30). The operation of the motor 8 is feedback controlled by a controller for the leveler feeder 5 (not shown) (having the same configuration as the controller 14 shown in FIG. 5). The R guide 5a may have a variable position in the left-right direction, similar to the R guide 10a.

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 for the uncoiler 2 (not shown). In the case of this example, a slack portion (loop 1 c) of the strip 1 is also formed between the uncoiler 2 and the leveler feeder 5. Although not shown, the loop 1c is provided with a loop sensor similar to that described with reference to FIG. 9A, and the motor 3 includes these loop sensors as described with reference to FIG. 9B. The rotation speed is switched in accordance with the loop amount of the loop 1c detected by. Therefore, the controller for the uncoiler 2 that controls the motor 3 does not necessarily need to perform feedback control, and can simply change the rotational speed of the motor 3 as described in FIG. 9B. Any configuration is possible. The acceleration at the time of switching the rotational speed of the motor 3 may be a small value (a value much smaller than 1G) in consideration of the magnitude of the load (coil material 1a, etc.) inertia.
In the case of this example, the control device 40 shown in FIG. 1 is an entire control system composed of the above-described controllers (the controller for the uncoiler 2, the controller for the leveler feeder 5, and the controller 14 for the roll feeder 10). And corresponds to the control means of the present invention.

Next, characteristic functions of the control device 40 (each controller) and characteristics (speed change patterns) of the feeding operation of the leveler feeder 5 and the roll feeder 10 will be described.
The controller 40 controls the upstream feed mechanism and the downstream feed so that the difference in acceleration between the feed operation of the upstream feed mechanism and the feed operation of the downstream feed mechanism on both sides of the loop 1b or the loop 1c does not exceed the gravitational acceleration. Controls the feed operation of the mechanism. That is, when looking at the loop 1c, the difference in acceleration between the feed operation of the uncoiler 2 (upstream side feed mechanism) and the feed operation of the leveler feeder 5 (downstream side feed mechanism) should not always exceed the gravitational acceleration (1G). The feeding operation of the uncoiler 2 and the leveler feeder 5 is controlled. In this case, specifically, the controller of the leveler feeder 5 controls the acceleration of the feeding operation (including a negative acceleration during deceleration) to 1 G, as will be described later. As a result, the uncoiler 2 and the leveler feeder 5 The acceleration difference does not always exceed 1G.

  Next, in view of the loop 1b, the control device 40 always determines that the difference in acceleration between the feed operation of the leveler feeder 5 (upstream side feed mechanism) and the feed operation of the roll feeder 10 (downstream side feed mechanism) is the gravitational acceleration (1G). The feed operation of the leveler feeder 5 and the roll feeder 10 is controlled so as not to exceed. In this case, specifically, the controller of the leveler feeder 5 controls the acceleration of the feeding operation (including a negative acceleration during deceleration) to 1G, as will be described later, and the feeding operation of the roll feeder 10 is accelerated or decelerated. In this state, the feed operation of the leveler feeder 5 is always controlled to accelerate or decelerate similarly (however, the acceleration of the roll feeder 10 is 2G). As a result, the difference in acceleration between the leveler feeder 5 and the roll feeder 10 Always does not exceed 1G.

  Further, as shown in the lower part of FIG. 2, the control device 40 moves the roll feeder 10 (downstream feeding mechanism) to, for example, a trapezoidal downstream speed in response to a request from a device to be fed (for example, a press machine) of the strip 1 On the other hand, the leveler feeder 5 (upstream feed mechanism) is also operated intermittently with, for example, a trapezoidal upstream speed change pattern, and the downstream speed change pattern and the upstream speed change pattern are The configuration is such that the feed operation of the leveler feeder 5 (upstream side feed mechanism) is synchronized with the feed operation of the roll feeder 10 (downstream side feed mechanism) so that the top center position coincides with the time axis. The inclination of the acceleration / deceleration unit of the downstream speed change pattern and the upstream speed change pattern is determined so that the difference in acceleration of the feeder 5 does not exceed the gravitational acceleration (1G). Parameters (for example, acceleration time, deceleration time and rated speed illustrated in FIG. 8A) are set, and a single feed operation (feed operation for one trapezoidal or triangular speed change pattern) The areas of trapezoids or triangles formed by the downstream speed change pattern and the upstream speed change pattern are set to be the same so that the upstream feed mechanism and the downstream feed mechanism have the same feed amount. Note that the downstream speed change pattern and the upstream speed change pattern described above may be trapezoidal as shown in the lower part of FIG. 2 or FIG. 8A, but are shown in FIGS. 8B and 8C. Thus, it may be triangular. Here, FIG. 8A shows a relatively long feed, FIG. 8B shows a medium feed, and FIG. 8C shows a short feed. Although details will be described later, as shown in FIGS. 10A to 10C, a speed change pattern in which the acceleration / deceleration portion is S-shaped may be used.

  That is, in this case, the speed change pattern in the feeding operation of the leveler feeder 5 and the roll feeder 10 is set as shown in the lower part of FIG. In the lower part of FIG. 2, reference numeral VL indicates a speed change pattern (upstream speed change pattern) of the leveler feeder 5, and reference sign VR indicates a speed change pattern (downstream speed change pattern) of the roll feeder 10. In the downstream side speed change pattern VR, the inclination of the acceleration / deceleration part (that is, the inclination of the inclined parts on the left and right sides of the trapezoidal or triangular pattern) is a value corresponding to, for example, 2G in order to correspond to the required high-speed feed. ing. On the other hand, in the upstream speed change pattern VL, the acceleration / deceleration unit has an inclination corresponding to, for example, 1 G in order to always set the difference in acceleration between the leveler feeder 5 and the roll feeder 10 to 1 G or less. Then, the output of the feed length setting unit 16 described above is controlled so that the top center positions of the downstream speed change pattern VR and the upstream speed change pattern VL coincide on the time axis as shown in the lower part of FIG. Further, the area of the trapezoid or the triangle formed by the downstream speed change pattern VR and the upstream speed change pattern VL is set to be the same, and as shown in the upper part of FIG. The roll feeder 10 has the same configuration.

In the belt-like material feeding device of this example configured as described above, the acceleration of the feeding operation of the uncoiler 2 (upstream feeding mechanism) and the feeding operation of the leveler feeder 5 (downstream feeding mechanism) can be seen from the loop 1c. The feeding operations of the uncoiler 2 and the leveler feeder 5 are controlled so that the difference does not exceed the gravitational acceleration (1G). For this reason, the relative acceleration of the loop 1c is always 1G or less and does not exceed the gravitational acceleration, so that the vibration of the loop 1c as described above is significantly reduced.
As for loop 1b, the difference in acceleration between the feed operation of the leveler feeder 5 (upstream side feed mechanism) and the feed operation of the roll feeder 10 (downstream side feed mechanism) does not always exceed the gravitational acceleration (1G). The feeding operations of the leveler feeder 5 and the roll feeder 10 are controlled. In this case, for example, when the feed operation of the roll feeder 10 is in a 2G acceleration state, the feed operation of the leveler feeder 5 is at least 1G acceleration state. Conversely, when the feed operation of the roll feeder 10 is in a 2G deceleration state, The feeding operation of the leveler feeder 5 is set to a deceleration state of at least 1G. For this reason, the relative acceleration of the loop 1b is always 1G or less and does not exceed the gravitational acceleration, so that the vibration of the loop 1b as described above is significantly reduced.

  Further, as shown in the lower part of FIG. 2, since the center positions of the tops of the downstream speed change pattern VR and the upstream speed change pattern VL coincide with each other on the time axis, the acceleration at the time of acceleration / deceleration differs and the start point of the feeding operation Since the feed operation of the leveler feeder 5 (upstream side feed mechanism) and the roll feeder 10 (downstream side feed mechanism) is synchronized (that is, semi-synchronized) except for the point that the end time is different from that of the loop 1b. The deformation is extremely small, and the vibration of the loop 1b is particularly reduced. Further, as described above, the leveler feeder 5 (upstream side feed mechanism) and the roll feeder 10 (downstream side feed mechanism) are semi-synchronized, and the feed operations are relatively different in a short period during acceleration / deceleration. Further, as shown in FIG. 2, since the deviation of the feed amount during that period is only a slight feed amount, the loop amount itself of the loop 1b can be remarkably reduced. When the loop amount of the loop 1b is reduced, it is not necessary to provide a large space (for example, a loop pit) for the loop 1b. Further, when the loop amount is reduced, the shaking object itself becomes smaller (lighter), so that the energy of the shaking is reduced, and there is an advantage that the machine damage and noise due to the shaking are further reduced. Further, since the feed amount by one feed operation is the same in the leveler feeder 5 (upstream feed mechanism) and the roll feeder 10 (downstream feed mechanism), the loop amount is slightly increased during acceleration / deceleration of the feed operation. Except for the fluctuating point, the loop amount of the loop 1b is always constant. If the loop amount becomes constant, depending on the operating conditions such as the strip thickness and feed length, find a loop amount with particularly small fluctuations in advance and set that loop amount to minimize the loop amount. It is possible to always hold it, and also in this respect, the vibration of the loop 1b can be reduced.

Moreover, in this apparatus, as described above, the leveler feeder 5 (upstream side feed mechanism) and the roll feeder 10 (downstream side feed mechanism) are configured to be semi-synchronized, and the loop amount of the loop 1b is always substantially constant. An R guide 5a that contacts the lower surface of the end of the slack portion (loop 1b) of the strip 1 is provided downstream of the leveler feeder 5 (upstream feed mechanism) and upstream of the roll feeder 10 (downstream feed mechanism). The R guide 10a is provided, for example, by changing the position of the R guide 10a (or the R guide 5a or both of the R guide 5a and the R guide 10a) in the left-right direction, the distance between these R guides can be changed. ing.
For this reason, the distance between the R guides is changed to the minimum value according to the plate thickness of the strip 1 and the loop 1b is formed with the limit of the allowable curvature radius of each plate thickness (the limit curvature at which plastic deformation does not occur). It becomes possible. For example, when the plate thickness is 3.2 mm, the allowable curvature radius is, for example, 1600 mm (500 times the plate thickness). As shown in FIG. 3A, the allowable curvature radius is the limit (distance L2 between the R guides) and the loop 1b. When the plate thickness is 0.6 mm, the allowable curvature radius is 300 mm, for example, and as shown in FIG. 3B, this allowable curvature radius is the last (distance between R guides L1, L1 <L2) and the loop 1b. Can be formed. This has the following advantages. First, in the loop 1b, the belt-like material 1 can be given tension according to the plate thickness, and this tension gives the freedom of swinging of the loop 1b (the freedom of movement centered on the swinging fulcrum shown in FIG. 3). It is possible to limit the vibration of the loop 1b. Further, by utilizing the tension of the material, the kinetic energy supplied from the leveler feeder 5 (upstream side feed mechanism) is propagated, thereby absorbing or decelerating (inertia) pulled by the roll feeder 10 (downstream side feed mechanism). Can be offset. Furthermore, the contact area of the material with the R guides 5a and 10a is increased, the holdability is increased, and the degree of freedom in which the strip 1 is swayed by the loop 1b can be reduced. If the R guides 5a and 10a are unnecessarily separated, the contact area with the R guides 5a and 10a is reduced, and the degree of freedom of the material around the fulcrum of shaking as shown in FIG. It becomes easy.

The present invention is not limited to the above-described embodiments, and various modifications and applications are possible.
For example, the speed change pattern of the present invention may be a speed change pattern obtained by deforming the speed change patterns shown in FIGS. 8A to 8C as shown in FIGS. 10A to 10C, respectively. . That is, the trapezoidal or triangular speed change pattern is not limited to a pattern constituted by a complete straight line as shown in FIG. As a general technique for countermeasures against loop shaking, it is known to make the acceleration / deceleration slope S-shaped instead of a straight line. As shown in FIG. 10, if an S-shape is used instead of a straight line in the acceleration / deceleration portion of the trapezoidal or triangular speed change pattern in the present invention, the effect of further suppressing the shaking will be improved.
In the above-described embodiment, the leveler feeder 5 repeats the stop and feed operations in semi-synchronization with the roll feeder 10. However, in the leveler feeder, the roll mark is attached to the material if the roll drive is completely stopped. Therefore, at the timing of the stop described above, the slow speed operation is performed, and at the timing of the feed operation with the trapezoidal or triangular speed pattern described above, the feed length obtained by subtracting the minute feed length sent at the slow speed. It is also possible to apply such as sending a message.

Also, the difference in acceleration between the upstream feed mechanism and the downstream feed mechanism should be controlled to a value close to the gravitational acceleration (preferably below the gravitational acceleration), but it should not exceed the gravitational acceleration even slightly. Absent. This is because the loop may not be shaken even if the gravity acceleration is slightly exceeded.
Also, depending on the equipment, even if the loop is slightly shaken and some noise or material damage occurs, it may be allowed. When 2.5G acceleration is realized in the roll feeder (downstream side of the loop) in such equipment, if the acceleration upstream and downstream of the loop is 1.25G and 2.5G in the method of the present application, the relative acceleration is Although it may slightly exceed 1G (0.25G) and the vibration may occur, the vibration is greatly reduced compared with the case where 2.5G acceleration is concentrated in one loop in the conventional method. There can be cases that fall within the allowable range.

  Moreover, the structure as shown in FIG. 7 may be sufficient as the structure of the supply apparatus of the strip | belt-shaped material whole. In the example shown in FIG. 7, a normal leveler 55 having a correction roller 55 is disposed downstream of the uncoiler 2, and another roll feeder 60 is disposed between the leveler 55 and the most downstream roll feeder 10. The loop 1 c of the strip 1 is formed between the leveler 55 and the roll feeder 60, and the loop 1 b of the strip 1 is formed between the roll feeder 60 and the roll feeder 10. Reference numeral 53 denotes a motor of the leveler 55, and the motor 53 is subjected to the control described in FIG. 9B, that is, in this case, speed switching control corresponding to the loop amount of the loop 1c. Reference numerals 60a and 60b are R guides of the roll feeder 60, reference numerals 61a and 61b are feed rolls of the roll feeder 60, and reference numerals 68 and 69 are a motor and a position detector of the roll feeder 60. The motor 68 is controlled in the same manner as the motor 8 (FIG. 1) described above, and the vibration of the loop 1b is suppressed.

Further, for example, in the embodiment described above, the acceleration of the feeding operation of the leveler feeder 5 and the roll feeder 10 is not limited to 1G and 2G. The difference between the accelerations on both sides of the loop should always be about 1G or less, for example 0.5G and 1.5G, or 2G and 3G. However, since the acceleration of the leveler feeder 5 exceeds the gravitational acceleration 1G, the loop on the upstream side of the leveler feeder 5 (the loop 1c between the uncoiler 2) may be shaken. It is necessary to further increase the loop by further providing a feeding mechanism on the side or downstream side. That is, when the present invention is applied, the difference in acceleration between the feeding mechanisms on both sides of the loop is limited to approximately gravitational acceleration 1G. However, for example, two feed mechanisms are provided between the most upstream uncoiler and the most downstream roll feeder (three loops are provided), and the acceleration setting is set to 1G, 2G, 3G as the feed mechanism becomes downstream. If the configuration is increased, it becomes possible to finally feed at a high speed, for example, with an acceleration of 3G. In some cases, the unconiler 2 may be intermittently fed at a predetermined acceleration in principle. For example, in FIG. 1, the unconiler 2 is semi-synchronized with the roll feeder 10 and the leveler feeder 5, the acceleration of the uncoiler 2 is set to 1G, for example, and the leveler feeder 5 is 2G acceleration and the roll feeder 10 is 3G acceleration at a constant intermittent feed. There may be a configuration for driving.
As described above, the present application reduces the relative acceleration applied to each loop by increasing the number of loops between the feeding mechanisms to form two or more loops and dispersing the relative acceleration applied to the loops. The configuration is not limited by the layout of the device or the acceleration setting of each feeder.
In the embodiment described above, in the mechanism in which the distance between the R guides is variable, the downstream R guide is movable. However, the upstream R guide may be used instead. The upstream and downstream R guides may be movable.

It is a figure which shows the structure of a feeder. It is a figure which shows changes, such as a feed rate of an upstream feed mechanism and a downstream feed mechanism. It is a figure explaining the setting of the distance between R guides. It is a side view which shows the specific example of a roll feeder. It is a figure explaining the control system of a roll feeder. It is a figure explaining the shaking of a loop. It is a figure which shows the other example of a form. It is a figure which shows the various examples of a speed change pattern. It is a figure explaining the conventional feeder. It is a figure which shows the other example of a speed change pattern.

Explanation of symbols

1 Strip material 1b, 1c Loop 2 Uncoiler (Upstream side feed mechanism)
5 Leveler feeder (upstream feed mechanism, downstream feed mechanism)
5a R guide 10 Roll feeder (downstream feed mechanism)
10a R guide 40 Control device (control means)
55 Leveler (Upstream side feed mechanism)
60 roll feeder (upstream feed mechanism, downstream feed mechanism)

Claims (4)

An upstream feed mechanism that feeds the strip material on the upstream side of the line for supplying the strip material, and a downstream feed mechanism that feeds the strip material on the downstream side of the upstream feed mechanism, and the upstream feed mechanism; In order to absorb the difference in the feeding operation of the downstream feeding mechanism, a belt-like material feeding device in which a slack portion of the belt-like material is formed between the upstream feeding mechanism and the downstream feeding mechanism,
Control means for controlling the feed operation of the upstream feed mechanism and the downstream feed mechanism so that the difference in acceleration between the feed operation of the upstream feed mechanism and the feed operation of the downstream feed mechanism does not exceed the gravitational acceleration. A belt-shaped material feeding device characterized by comprising: The control means intermittently executes a feed operation that operates the downstream feed mechanism with a trapezoidal or triangular downstream speed change pattern in response to a request of a device to which the belt-shaped material is supplied, while the upstream The side feed mechanism also intermittently executes a feed operation that operates in a trapezoidal or triangular upstream speed change pattern so that the center positions of the tops of the downstream speed change pattern and the upstream speed change pattern coincide on the time axis. And the downstream speed change pattern and the upstream speed so that the difference in acceleration does not exceed substantially gravitational acceleration. A parameter that determines the inclination of the acceleration / deceleration part of the change pattern is set, and the feed amount by one feed operation is different between the upstream feed mechanism and the downstream feed mechanism. Feeder strip material according to claim 1, the area of the trapezoidal or triangular, characterized in that it is set equal the downstream speed change pattern and the upstream speed change pattern to be the Flip forms. On the downstream side of the upstream side feeding mechanism and the upstream side of the downstream side feeding mechanism, R guides that contact the lower surface of the end of the slack portion of the belt-like material are respectively provided, and the distance between these R guides is variable. The belt-like material feeding device according to claim 2, wherein An upstream feed mechanism that feeds the strip material on the upstream side of the line for supplying the strip material, and a downstream feed mechanism that feeds the strip material on the downstream side of the upstream feed mechanism, and the upstream feed mechanism; In order to absorb the difference in the feeding operation of the downstream feeding mechanism, a belt-like material feeding device in which a slack portion of the belt-like material is formed between the upstream feeding mechanism and the downstream feeding mechanism,
On the downstream side of the upstream side feed mechanism and the upstream side of the downstream side feed mechanism, R guides that contact the lower surface of the end of the slack portion of the belt-like material are provided, and the distance between the R guides is variable. A device for feeding a strip-shaped material.

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