JP7316014B1 - shearing device - Google Patents

Abstract

An object of the present invention is to provide a shearing device that structurally enables further rigidity improvement of the shearing head. A shearing device (1) includes a shearing head (2), and a fixed blade (3) and a movable blade (4) provided on the shearing head (2). The shearing head 2 includes a first side portion 2a and a second side portion 2b that extend parallel to each other, and a connecting portion that connects the first side portion 2a and the second side portion 2b at the base ends of the side portions 2a and 2b. 2c integrally. A first positioning hole 14 is provided on the tip side of the first side portion 2a, and the tip side of the second side portion 2b is configured to be retractable with respect to the second side portion 2b, and can be fitted into the first positioning hole 14. A first positioning member 15 is provided. A second positioning hole 16 is provided on the distal end side of the first positioning member 15 and is formed so as to be open in a direction perpendicular to the direction in which the first positioning member 15 appears and retracts. A second positioning member 17 is provided that can be fitted into the second positioning hole 16 while the first positioning member 15 is fitted into the first positioning hole 14 . [Selection drawing] Fig. 2

Description

The present invention relates to a shearing device, and more particularly to a shearing device for cutting metal sheets by shear.

Conventionally, in order to connect the preceding strip-shaped metal plate and the following strip-shaped metal plate, the preceding strip-shaped metal plate is sheared at its trailing edge, and the trailing strip-shaped metal plate is sheared at its leading edge to be cut. Welding devices are known for butting and welding the edges of each other (see Patent Literatures 1 and 2).

FIG. 9 shows an example of a conventional band-shaped metal plate welding device 100, which includes a welding torch 101 and a shearing device 102. As shown in FIG. From the stowed position shown in FIG. 9, the shearing device 102 can be moved in the direction indicated by arrow Y1. The welding torch 101 can perform welding by reciprocating in the direction indicated by the arrow Y2 from the standby position shown in FIG.

The shearing device 102 incorporated in this type of welding device is also called a shearing device, a shearing machine, etc. In general, as shown in the schematic structure of FIGS. A fixed blade 104 fixed to one side, a movable blade 105 provided on the second side of a shearing head 103 extending parallel to the first side, and a movable blade 105 provided on the shearing head 103 moving up and down. A movable blade 105 is provided with a hydraulic cylinder 106 for moving, and by moving the movable blade 105 in the vertical direction, the band-shaped metal plate can be sheared. 10 shows the standby position of the movable blade, and FIG. 11 shows the shearing position of the movable blade.

In the conventional shearing device, in order to improve the shearing force, a pressure increasing cylinder (also called a pressure increasing booster) is provided to increase the hydraulic pressure for operating the hydraulic cylinder for driving the movable blade (see Patent Document 2). ), and is designed to handle strip-shaped metal plates with large plate thickness. By increasing the driving force of the movable blade in this way, the shearing load on the shearing head that supports the fixed blade also increases, so the rigidity of the shearing head needs to be increased in order to shear the strip-shaped metal plate without backlash. However, if the rigidity of the shearing head is increased by, for example, increasing the plate thickness of the metal plate that constitutes the shearing head, the size of the shearing device increases and the weight of the shearing device increases. The increase in the weight of the shearing device necessitates the enlargement of the driving device of the shearing device, resulting in problems such as the enlargement of the welding device and the increase in the manufacturing cost.

Therefore, the present applicant has proposed a new technique for increasing the rigidity of the shearing head without enlarging it (see Patent Document 3). That is, in this patent document, a U-shaped shearing head integrally having a first side portion and a second side portion extending in parallel and a continuous portion connecting the first side portion and the second side portion , a positioning hole is provided on the tip side of the first side portion, and a piston rod that protrudes and retracts from the tip side of the second side portion and can be inserted into the positioning hole is provided, and the piston rod moves the movable blade. A shearing device is disclosed that is configured to operate synchronously with the piston rod of a hydraulic cylinder for driving.

JP 2018-86686 A JP 2018-39090 A Japanese Patent No. 7055505

In this way, by adopting a structure in which the piston rod protruding from the second side portion can be fitted into the positioning hole provided in the first side portion, a structure (beam structure) that is particularly susceptible to swinging in a direction orthogonal to the shearing direction can be achieved. It is possible to effectively suppress the looseness of the first side portion to increase the positional accuracy of the fixed blade attached to the first side portion. However, when aiming to expand the shearing target of the above-mentioned shearing device to a band-shaped metal plate with a larger plate thickness, assuming that a larger load than ever will act on the fixed blade during shearing, the shearing head It is necessary to further improve the rigidity of. Alternatively, when aiming to reduce the weight of the shearing head in order to reduce the size of the shearing device including the shearing head, a new measure is required to prevent the rigidity of the shearing head from decreasing.

In view of the above circumstances, it is an object of the present invention to provide a shearing device that can further improve the rigidity of the shearing head while avoiding an increase in size.

The solution to the above problem is achieved by a shearing device according to the present invention. That is, this shearing device includes a shearing head, a fixed blade and a movable blade provided on the shearing head, and a positioning mechanism including a part of the shearing head, the shearing head having a first side portion and a second side portion extending parallel to each other. A shearing device integrally having two side portions and a connection portion connecting the first side portion and the second side portion at the proximal end side of each side portion, wherein the positioning mechanism is located at the distal end side of the first side portion and a first positioning member provided so as to be retractable from the tip side of the second side portion and capable of being fitted into the first positioning hole, wherein the positioning mechanism comprises: a second positioning hole provided on the distal end side of the first positioning member and having an opening formed in a direction orthogonal to the direction of projection and retraction of the first positioning member; and a second positioning member that can be fitted into the second positioning hole in a state in which is fitted into the first positioning hole.

As described above, in the shearing device according to the present invention, as a component of the positioning mechanism, a new positioning hole is provided on the distal end side of the first positioning member, and the first positioning member is configured to be retractable with respect to the first positioning hole. A second positioning member is provided that can be fitted into the second positioning hole while the positioning member is fitted into the first positioning hole. According to this configuration, the first positioning member fitted in the first positioning hole can be fixed in a state of being positioned highly accurately and firmly by the second positioning member. Therefore, for example, when a large shear load acts, the state of being positioned by the fitting structure of the first positioning member and the first positioning hole is maintained by the fitting structure of the second positioning member and the second positioning hole, It is possible to suppress the occurrence of backlash. Alternatively, even if the fitting between the first positioning member and the first positioning hole is loosely set in order to achieve quick positioning, the first positioning member after fitting can be placed in an appropriate position by the second positioning member. can be fixed. As described above, according to the shearing device of the present invention, it is possible to accurately cut a metal plate having a large thickness along a desired cutting line.

Further, in the shearing device according to the present invention, the positioning mechanism includes a first fluid pressure cylinder capable of reciprocating the first positioning member along the retracting direction, and a second fluid pressure cylinder capable of reciprocating the second positioning member along the retracting direction. It may further comprise two fluid pressure cylinders and a fluid supply source capable of supplying working fluid to the first and second fluid pressure cylinders respectively.

With this configuration, only one device (fluid supply source) is required to drive each fluid pressure cylinder. Therefore, for example, these hydraulic cylinders and fluid supply sources can all be integrated into the shearing head, making it possible to further reduce the size of the shearing device.

Also, in the shearing device according to the present invention, switching valves are provided between each hydraulic cylinder and the fluid supply source and between each hydraulic cylinder and the fluid discharge path, the switching valves being connected to both hydraulic cylinders. a first switch position that configures the connection between each hydraulic cylinder and the fluid supply and the connection between each hydraulic cylinder and the fluid discharge path such that the pressure produces a pushing movement; and a second switching position that configures the connection state between each hydraulic cylinder and the fluid supply source and the connection state between each hydraulic cylinder and the fluid discharge path so as to produce

With this configuration, the two positioning members can be operated at once, so that the fixed blade can be positioned and released efficiently and quickly.

Further, in the shearing device according to the present invention, a meter-in type speed controller may be arranged between the fluid supply source and the second hydraulic cylinder at the first switching position.

Since the meter-in type speed controller is a device for adjusting the throttling of the fluid when supplying the fluid to the cylinder, the fluid supply source and the second fluid pressure cylinder are connected at the first switching position for pushing out the cylinder as described above. By arranging a meter-in type speed controller between , it is possible to suppress the pushing speed of the second positioning member connected to the piston of the second fluid pressure cylinder, or delay the movement of the second positioning member. Therefore, the second positioning member can start moving into the first positioning hole in a state where the first positioning member has been fitted into the first positioning hole to some extent, or in a state where the fitting has been completed. Therefore, even when the fluid is supplied from the common fluid supply source as described above, it is possible to fit the second positioning member into the second positioning hole provided in the first positioning member without difficulty.

Further, in the shearing device according to the present invention, the first fluid pressure cylinder may be a double-acting cylinder, and the second fluid pressure cylinder may be a single-acting cylinder in which a spring biases the piston toward the retraction side.

In this way, the second positioning member is pulled out of the second positioning hole before the first positioning member by pulling in the second fluid pressure cylinder with the elastic restoring force of the spring, which has excellent responsiveness compared to fluid pressure control. be able to. As a result, even when the reciprocating motion of both positioning members is controlled by a common fluid pressure, both positioning members can be pulled out from the corresponding positioning holes without difficulty and returned to the state before positioning.

Further, in the shearing device according to the present invention, a meter-out type speed controller may be arranged between the fluid discharge path and the base-side cylinder chamber of the first fluid pressure cylinder at the second switching position.

Since the meter-out type speed controller is a device for adjusting the throttling of the fluid when the fluid is discharged from the cylinder chamber, the fluid discharge path and the first switching position are arranged at the second switching position for the retraction operation of the fluid pressure cylinder as described above. By arranging a meter-out type speed controller between the hydraulic cylinder and the first positioning member, the retraction operation of the first positioning member is suppressed by suppressing the discharge of the fluid from the proximal side cylinder chamber where the working fluid is discharged at the time of retraction. can be delayed. Therefore, it is possible to more reliably pull out the second positioning member from the second positioning hole.

Further, in the shearing device according to the present invention, a meter-in type speed controller may be arranged between the fluid supply source and the tip side cylinder chamber of the first fluid pressure cylinder at the second switching position.

In this way, by delaying the supply of fluid to the distal end side cylinder chamber of the second fluid pressure cylinder, which is a double-acting cylinder, the pull-in operation of the first positioning member is also delayed, and the second positioning member can be moved more reliably. It becomes possible to pull out from the second positioning hole.

Further, the shearing device according to the present invention further includes a movable blade driving cylinder in which a piston is connected to the movable blade, and a booster cylinder capable of driving the movable blade driving cylinder to the pushing side by supplying hydraulic oil. You may prepare. Also, in this case, the first and second fluid pressure cylinders are driven by being supplied with working air from an air compressor as a fluid supply source, and the boosting cylinder is movable by being supplied with working air from the air compressor. It may be configured such that pressurized hydraulic oil can be supplied to the blade driving cylinder.

As described above, when a pressure increasing cylinder capable of driving the movable blade driving cylinder to the pushing side is further provided, the pressure increasing cylinder is driven using an air compressor for driving the first and second fluid pressure cylinders. Thereby, the production and supply of working air by the air compressor can be utilized more effectively. Further, with the above configuration, only one air compressor is required, so it is possible to achieve both strengthening of the shearing force and improvement of the rigidity of the shearing head while avoiding an increase in the size of the shearing device.

Further, in the shearing device according to the present invention, when the movable blade driving cylinder is a double-acting cylinder, and the pressure increasing cylinder is connected to the proximal side cylinder chamber, and the switching valve is in the second switching position, An air compressor may be connected to the tip side cylinder chamber.

With this configuration, the air compressors for driving the fluid pressure cylinders can also be used for the retraction operation of the movable blade driving cylinders. Of course, one air compressor is sufficient, so there is no need to worry about increasing the size of the shearing device.

As described above, according to the shearing device according to the present invention, it is possible to further improve the rigidity of the shearing head while avoiding an increase in size, so that it is possible to easily cope with an increase in the plate thickness of the strip-shaped metal plate. It becomes possible.

1 is a front view of a shearing device according to an embodiment of the present invention, which conceptually shows the configuration of a shearing mechanism of the shearing device. FIG. 2 is a cross-sectional view along AA conceptually showing the overall configuration of the positioning mechanism shown in FIG. 1; FIG. FIG. 2 is an enlarged view of the movable blade shown in FIG. 1; 2 is a front view of the shearing device shown in FIG. 1 with the movable blade in the cutting position; FIG. 2 is a front view of the shearing device shown in FIG. 1 with the movable blade in the shearing end position; FIG. FIG. 3 is a cross-sectional view taken along the line AA showing an example of the operation mode of the positioning mechanism shown in FIG. 2, and showing a state in which the first positioning member is fitted into the first positioning hole; FIG. 3 is a cross-sectional view taken along line AA showing an example of an operation mode of the positioning mechanism shown in FIG. 2, and a cross-sectional view taken along line AA showing a state in which a second positioning member is fitted into a second positioning hole; FIG. 3 is a cross-sectional view taken along line AA showing an example of an operation mode of the positioning mechanism shown in FIG. 2, and a cross-sectional view along line AA showing a state in which the second positioning member is pulled out from the second positioning hole; It is a perspective view which shows the conventional strip-shaped metal plate welding apparatus. 1 is a front view showing a schematic configuration of a conventional shearing device; FIG. FIG. 11 is a front view showing an operating state of the shearing device shown in FIG. 10;

Hereinafter, the contents of a shearing device according to an embodiment of the present invention will be described based on the drawings. In this embodiment, a case where the shearing device is arranged so as to be able to shear a metal plate in a horizontal posture, that is, to be able to shear in the vertical direction will be described as an example. Of course, the arrangement and usage of the shearing device are not limited to this. The shearing direction can be arbitrarily set depending on the shape of the object to be sheared or the location where the shearing work is performed.

1 and 2 show a shearing device 1 according to this embodiment. 1 is a plan view conceptually showing the main configuration of the shearing device 1, and FIG. 2 is a cross-sectional view along the line AA of the main part (positioning mechanism 7 described later) of the shearing device 1 shown in FIG. each shown. As shown in FIG. 1, this shearing device 1 includes a shearing head 2, a fixed blade 3, a movable blade 4, a first driving cylinder 5 and a second driving cylinder 6 as movable blade driving cylinders, and a positioning mechanism 7 . In this embodiment, the shearing device 1 further comprises an intensifying cylinder 8 . In the following, after first explaining each element constituting the shearing mechanism of the shearing device 1 and an example of the shearing mode, the details of the positioning mechanism 7 will be explained.

The shearing head 2 integrally has a first side portion 2a and a second side portion 2b that extend parallel to each other, and a connection portion 2c that connects the first side portion 2a and the second side portion 2b on the base end side. A fixed blade 3 is fixed to the first side 2 a of the shear head 2 . The movable blade 4 is attached to the second side portion 2b of the shearing head 2 so as to be vertically movable.

A first piston rod 9 of a first drive cylinder 5 is connected to one side of the movable blade 4 in the longitudinal direction, and a second piston rod 10 of a second drive cylinder 6 is connected to the other side of the movable blade 4 in the longitudinal direction. are connected. Here, the first piston rod 9 and the second piston rod 10 are provided parallel to each other.

The cutting edge of the fixed blade 3 is parallel to the first side portion 2a, and the cutting edge of the movable blade 4 is inclined with respect to the first side portion 2a. Of course, the cutting edge of the movable blade 4 may be formed horizontally.

As shown in FIG. 3, a first pivot shaft 9a is inserted through a first shaft hole 4a formed on one side of the movable blade 4 in the longitudinal direction. A second pivot shaft 10a is inserted through a second shaft hole 4b formed on the other side of the movable blade 4 in the longitudinal direction. In this illustrated example, as shown in FIG. 3, both the first shaft hole 4a and the second shaft hole 4b have an elongated hole shape with the longitudinal direction of the movable blade 4 as the major axis. With this configuration, a predetermined play, which will be described later, is provided between the first shaft hole 4a and the first pivot shaft 9a and between the second shaft hole 4b and the second pivot shaft 10a. The blade 4 is connected to the first piston rod 9 and the second piston rod 10 by loose joints.

A working oil passage 11 for supplying or discharging working oil as a working fluid is connected to the first driving cylinder 5 and the second driving cylinder 6 (see FIG. 1). In this embodiment, hydraulic fluid flows between the second driving cylinder 6 and the first hydraulic fluid passage 11a for circulating the hydraulic fluid between the hydraulic fluid passage 11 and the first driving cylinder 5. A second hydraulic fluid passage 11b is branched, and a speed controller 12 is arranged on the second hydraulic fluid passage 11b. The speed controller 12 is a meter-in type speed controller, and is capable of adjusting the speed of the hydraulic oil directed to the second driving cylinder 6 and the operation timing of the second driving cylinder 6 by means of a throttle 12a.

Further, in this embodiment, the pressure boosting cylinder 8 is connected to the upstream side of the hydraulic oil passage 11 . The boosting cylinder 8 has a large-diameter cylinder 8a, a small-diameter cylinder 8b, a large-diameter piston 8c that slides in the large-diameter cylinder 8a, and a small-diameter piston 8d that slides in the small-diameter cylinder 8b. The large-diameter piston 8c defines a working air pressure chamber 8e in the large-diameter cylinder 8a, and the small-diameter piston 8d defines a working oil pressure-increasing chamber 8f in the small-diameter cylinder 8b. A working oil passage 11 is connected to the pressure increasing chamber 8f, and a working gas passage 13 is connected to the pressurizing chamber 8e (details will be described later). The booster cylinder 8 configured as described above is accommodated, for example, in the connecting portion 2c of the shearing head 2 (see FIG. 1).

Next, an example of the operation mode of the shearing device 1 having the above configuration will be described. First, as shown in FIG. 1, from the state where the movable blade 4 is at the standby position (lower end position), hydraulic oil pressurized through the hydraulic oil passage 11 is supplied to the first driving cylinder 5 and the second driving cylinder 6. supply. At this time, a meter-in type speed controller 12 is arranged on the second hydraulic fluid passage 11b connected to the second driving cylinder 6. As shown in FIG. Therefore, the flow (supply speed) of hydraulic fluid supplied toward the second driving cylinder 6 through the second hydraulic fluid passage 11b is suppressed by the throttle 12a, and as shown in FIG. is restricted, the first piston rod 9 is pushed out first. The first piston rod 9 is pushed out to a position where the piston 5a of the first drive cylinder 5 reaches the stroke end on the cylinder head side, and stops at the stroke end position. At the position where the first piston rod 9 reaches the stroke end and stops, as shown in FIG. It is in the cutting position to shear the part.

When the first piston rod 9 is pushed out, the second pivot shaft 10a serves as a fulcrum and the first pivot shaft 9a serves as a force point, thereby actuating the movable blade 4 based on the second-class lever principle. To enable such operation, a predetermined play (see FIG. 3) is required between the first shaft hole 4a and the first pivot shaft 9a and between the second shaft hole 4b and the second pivot shaft 10a. ) is provided, and the movable blade 4, the first piston rod 9 and the second piston rod 10 are connected by loose joints. The amount of play is appropriately set according to the dimensions of the movable blade 4, the distance between the first shaft hole 4a and the second shaft hole 4b, the stroke lengths of the first piston rod 9 and the second piston rod 10, and the like.

By operating the movable blade 4 according to the principle of the second type lever as described above, a large shearing force can be generated with a small working oil pressure. Further, since the first piston rod 9 operates in the shearing direction before the second piston rod 10 and reaches the stroke end, the shear angle increases and the shearing force increases.

When the first piston rod 9 reaches the stroke end, the working oil can no longer be supplied to the first driving cylinder 5, so that amount of working oil is supplied to the second driving cylinder 6 through the second working oil passage 11b. Hydraulic oil is supplied. As a result, the second piston rod 10 substantially begins to operate, and the intersection between the fixed blade 3 and the movable blade 4 progresses, and the shearing action progresses. When the second piston rod 10 is pushed out, the first pivot shaft 9a serves as a fulcrum and the second pivot shaft 10a serves as a force point, thereby shearing the movable blade 4 by the second-class lever principle. Since the shear angle increases when the second piston rod 10 starts to operate, a large shearing force can be obtained.

When returning the movable blade 4 to the standby position after shearing, hydraulic oil is discharged from the first driving cylinder 5 and the second driving cylinder 6 . At this time, by providing the check valve 12b constituting the speed controller 12 on the second hydraulic fluid passage 11b, the hydraulic fluid is smoothly discharged from the second driving cylinder 6, and the movable blade 4 is moved. It is possible to quickly return to the standby position.

Details of the positioning mechanism 7, which is a characteristic configuration of the present invention, will be described below.

The positioning mechanism 7 is a mechanism for positioning the first side portion 2a relatively supported in a cantilever manner with respect to the second side portion 2b relatively supported on both sides. As shown in FIGS. 1 and 2, the positioning mechanism 7 includes a first positioning hole 14, a first positioning pin 15 as a first positioning member, a second positioning hole 16, and a second positioning member as a second positioning member. two locating pins 17; In this embodiment, the positioning mechanism 7 further has a first fluid pressure cylinder 18 , a second fluid pressure cylinder 19 , an air compressor 20 as a fluid supply source, and a working gas discharge path 21 .

As shown in FIG. 1, a first extension portion 22 that extends the first side portion 2a is attached to the tip of the first side portion 2a. A second extension portion 23 extending the second side portion 2b is attached to the tip of the second side portion 2b. The first positioning hole 14 is formed in the surface of the first extension portion 22 facing the second extension portion 23 of the second side portion 2b (here, the lower surface 22a). On the other hand, the first positioning pin 15 is provided so as to be able to protrude from the surface of the second extension portion 23 facing the first extension portion 22 (here, the upper surface 23a) of the first side portion 2a. The first positioning pin 15 is configured to be able to fit into the first positioning hole 14 in a state of protruding from the upper surface 23a by a predetermined distance (here, a stroke end state).

As shown in FIGS. 1 and 2 , the second positioning hole 16 is formed at a predetermined position in the axial direction of the first positioning pin 15 and in a direction perpendicular to the direction in which the first positioning pin 15 appears and retracts. In this embodiment, the second positioning hole 16 is formed so as to radially pass through the first positioning pin 15 (see FIG. 2). On the other hand, the second positioning pin 17 is provided on the first extension portion 22 so as to be retractable with respect to the first positioning hole 14 . Further, in a state where the first positioning pin 15 is fitted in the first positioning hole 14 , the second positioning pin 17 is configured to be fittable in the second positioning hole 16 provided in the first positioning pin 15 .

Further, in the present embodiment, the first positioning pin 15 has a reduced diameter surface 15a, such as a tapered surface, at its distal end, the outer diameter dimension of which decreases toward the distal end. Similarly, the second positioning pin 17 has a diameter-reduced surface 17a, such as a tapered surface, at its distal end, the outer diameter of which decreases toward the distal end. The diameter-reduced surface 15a can function as a guide surface when the first positioning pin 15 starts fitting into the first positioning hole 14 provided in the extension portion (first extension portion 22) of the first side portion 2a. Similarly, the diameter-reduced surface 17a functions as a guide surface when the second positioning pin 17 starts fitting into the second positioning hole 16 provided in the first positioning pin 15, and the second positioning pin 17 is inserted into the second positioning pin 17. It can also function as a guide surface when pulling out from the second positioning hole 16 is started.

The first fluid pressure cylinder 18 is configured to allow the first positioning pin 15 to reciprocate along the retracting direction. In this embodiment, as shown in FIG. 1 , the piston rod of the first fluid pressure cylinder 18 or its extension constitutes the first positioning pin 15 . Further, in the present embodiment, the first fluid pressure cylinder 18 is a double-acting cylinder, and the inner wall portion 23b of the second extension portion 23 and the piston 18a housed in the space surrounded by the inner wall portion 23b form the first hydraulic cylinder. A proximal side cylinder chamber 18b1 and a distal side cylinder chamber 18b2 of the one fluid pressure cylinder 18 are partitioned.

The second fluid pressure cylinder 19 is configured to allow the second positioning pin 17 to reciprocate along the retracting direction. In this embodiment, as shown in FIG. 2 , the piston rod of the second fluid pressure cylinder 19 or its extension constitutes the second positioning pin 17 . Further, in this embodiment, the second fluid pressure cylinder 19 is a single-acting cylinder, and the inner wall portion 22b of the first extension portion 22 and the piston 19a housed in the space surrounded by the inner wall portion 22b are used for the second fluid pressure cylinder. A base-side cylinder chamber 19b1 and a tip-side cylinder chamber 19b2 of the two-fluid pressure cylinder 19 are partitioned. In this case, the compression spring 24 is accommodated in the tip side cylinder chamber 19b2, and the elastic restoring force in the direction of pushing back the piston 19a can be accumulated in the compression spring 24 as the piston 19a is pushed out (see FIG. 7).

The first fluid pressure cylinder 18 and the second fluid pressure cylinder 19 configured as described above are connected to the air compressor 20 and the working gas discharge passage 21 through the working gas passage 13 having a predetermined structure. Switching valves for switching the flow of the working gas are provided between the fluid pressure cylinders 18 and 19 and the air compressor 20 in the working gas path 13 and between the fluid pressure cylinders 18 and 19 and the working gas discharge path 21. 25 are provided (see FIG. 2).

This switching valve 25 is, for example, a 5-port-2-position solenoid valve shown in FIG. A first switching position P1 (a position shown in FIG. 6) that constitutes a connection state with the compressor 20 or a connection state between the hydraulic cylinders 18 and 19 and the working gas discharge path 21, and the first and second hydraulic cylinders A second connecting state between the hydraulic cylinders 18 and 19 and the air compressor 20 or a connecting state between the hydraulic cylinders 18 and 19 and the working gas discharge path 21 so that both the hydraulic cylinders 18 and 19 produce a retraction operation. It is configured to be switchable between the switching position P2 (the position shown in FIG. 2).

Specifically, when the switching valve 25 is at the first switching position P1, as shown in FIG. It is connected to the air compressor 20 via 13a. Also, the base end cylinder chamber 19b1 of the second fluid pressure cylinder 19 is connected to the air compressor 20 via the first gas passage 13a and the second gas passage 13b branched from the first gas passage 13a.

Further, when the switching valve 25 is in the first switching position P1, the tip side cylinder chamber 18b2 of the first fluid pressure cylinder 18 is connected to the working gas discharge path 21 through the third gas path 13c constituting the working gas path 13. is connected with

On the other hand, when the switching valve 25 is in the second switching position P2, the tip side cylinder chamber 18b2 of the first fluid pressure cylinder 18 is connected to the air compressor 20 via the third gas passage 13c. In addition, the proximal side cylinder chamber 18b1 of the first fluid pressure cylinder 18 is connected to the working gas discharge path 21 via the first gas path 13a, and the proximal side cylinder chamber 19b1 of the second fluid pressure cylinder 19 is connected to the working gas discharge path 21 via the first gas path 13a and the second gas path 13b.

On the other hand, the tip side cylinder chamber 19b2 of the second fluid pressure cylinder 19 is always connected to any element for gas circulation (air compressor 20, working gas discharge path 21) regardless of the switching position of the switching valve 25. not.

Further, in this embodiment, a meter-in type speed controller 26 is arranged on the second gas passage 13b. Therefore, when the switching valve 25 is in the first switching position P1, the supply speed of the working gas to the proximal side cylinder chamber 19b1 of the second fluid pressure cylinder 19, and the operation timing related to the pushing operation of the second fluid pressure cylinder 19 is adjusted.

Further, in this embodiment, a meter-out type speed controller 27 is arranged on the first gas passage 13a. Therefore, when the switching valve 25 is in the first switching position P2, the discharge speed of the working gas from the base end side cylinder chamber 18b1 of the first fluid pressure cylinder 18, and the operation timing related to the retraction operation of the first fluid pressure cylinder 18 is adjusted.

Further, in this embodiment, a meter-in type speed controller 28 is arranged on the third gas passage 13c. Therefore, when the switching valve 25 is in the second switching position P2, the supply speed of the working gas to the tip end side cylinder chamber 18b2 of the first fluid pressure cylinder 18, and thus the operation timing related to the retraction operation of the first fluid pressure cylinder 18 is adjusted.

Further, in the present embodiment, when the switching valve 25 is in the first switching position P1, the pressurizing chamber 8e defined within the large-diameter cylinder 8a of the pressure-increasing cylinder 8 consists of the first gas passage 13a and the first gas. It is connected to an air compressor 20 via a fourth gas path 13d branched from the path 13a. Also, the retraction chamber 8g defined within the large-diameter cylinder 8a by the large-diameter piston 8c of the booster cylinder 8 passes through the third gas passage 13c and the fifth gas passage 13e branched from the third gas passage 13c. It is connected to the working gas discharge path 21 .

On the other hand, when the switching valve 25 is at the second switching position P2, the pressurizing chamber 8e of the boosting cylinder 8 is connected to the working gas discharge path 21 via the first gas path 13a and the fourth gas path 13d. In addition, the retraction chamber 8g is connected to the air compressor 20 via the third gas passage 13c and the fifth gas passage 13e.

Further, as shown in FIG. 1, when both the first driving cylinder 5 and the second driving cylinder 6 as movable blade driving cylinders are double-acting cylinders, the first and second driving cylinders 5 and 6 The tip side cylinder chamber may be connected to the air compressor 20 when the switching valve 25 is in the second switching position P2. In this case, working oil is supplied to or discharged from the proximal side cylinder chambers of the driving cylinders 5 and 6, and working gas is supplied to the distal side cylinder chambers thereof.

Next, an example of the mode of use of the shearing device 1 using the positioning mechanism 7 having the above configuration will be described together with the effects of the present invention.

First, from the state shown in FIGS. 1 and 2, the switching position of the switching valve 25 is switched from the second switching position P2 to the first switching position P1. As a result, the proximal side cylinder chamber 18b1 of the first fluid pressure cylinder 18 and the air compressor 20 are connected, and the proximal side cylinder chamber 19b1 of the second fluid pressure cylinder 19 and the air compressor 20 are connected ( See Figure 6). As a result, the working gas (here, working air) compressed by the air compressor 20 is supplied to the base-side cylinder chamber 18b1 of the first fluid pressure cylinder 18 through the first gas passage 13a to push up the piston 18a. Therefore, the first fluid pressure cylinder 18 starts pushing operation, the first positioning pin 15 connected to the piston 18a protrudes upward from the upper surface 23a of the second extension portion 23, and is provided on the first extension portion 22. It fits into the first positioning hole 14 (see FIG. 6). As a result, the first positioning hole 14 is positioned with respect to the first positioning pin 15 .

On the other hand, the working gas compressed by the air compressor 20 is also supplied to the proximal end cylinder chamber 19b1 of the second fluid pressure cylinder 19, and the second gas path connecting the second fluid pressure cylinder 19 and the switching valve 25 A meter-in type speed controller 26 is arranged on 13b. Therefore, the supply speed of the working gas supplied toward the second fluid pressure cylinder 19 through the second gas passage 13b is suppressed by the throttle of the speed controller 26 (see FIG. 6). As a result, as shown in FIG. 6, the pushing action of the second positioning pin 17 connected to the piston 19a of the second fluid pressure cylinder 19 is restricted, and the first positioning pin 15 is pushed out first. As a result, before the second positioning pin 17 enters the first positioning hole 14, the first positioning pin 15 reaches a predetermined position in the axial direction of the first value setting hole 14, here the stroke end of the first fluid pressure cylinder 18. It is fitted up to the corresponding position (see Figure 6).

After that, the second fluid pressure cylinder 19 starts pushing out, and the positioning pin 17 enters the first positioning hole 14 with a delay. At this time, the first positioning pin 15 has already been fitted into the first positioning hole 14, and the second positioning hole 16 is positioned in front of the second positioning pin 17 (see FIG. 6). Therefore, by advancing the second positioning pin 17, the second positioning pin 17 is fitted into the second positioning hole 16 (see FIG. 7).

It should be noted that there is a possibility that the second positioning pin 17 may start to enter the first positioning hole 14 slightly earlier due to some timing deviation (fluctuation). By providing the diameter-reduced surface 17 a at the tip of the positioning pin 17 , the diameter-reduced surface 17 a functions as a guide surface, and the second positioning pin 17 can be smoothly fitted into the second positioning hole 16 . By the above operation, the first extension portion 22 is firmly positioned and fixed by the double fitting of the first and second positioning pins 15 and 17 (see FIG. 7).

Further, in the present embodiment, the air compressor 20 and the pressure increasing cylinder 8 are connected via the fourth gas passage 13d when the switching valve 25 is switched to the first switching position P1. Therefore, the compressed working gas is supplied to the pressure chamber 8 e of the pressure increasing cylinder 8 when the positioning operation by the first positioning pin 15 is started. As a result, according to the outer diameter ratio of the large-diameter piston 8c and the small-diameter piston 8d, the pressure of the hydraulic oil in the pressure-increasing chamber 8f defined by the small-diameter piston 8d is increased, and the hydraulic oil flows through the hydraulic oil passage 11 into the first drive cylinder. 5 and the second drive cylinder 6 . Therefore, it is possible to increase the shearing force generated between the fixed blade and the movable blade 4 . Further, according to the above configuration, since the shearing operation of the movable blade 4 occurs in a state in which (the first extension 22 of) the first side 2a is positioned with respect to the second extension 23, the common drive While simultaneously starting to supply the working fluid to the shearing mechanism and the positioning mechanism 7 using the source (here, the air compressor 20), the shearing is performed in a state where the first side portion 2a is first reliably and firmly positioned and fixed. It is possible to take action.

After completing the shearing operation as described above, the movable blade 4 is lowered as described above, and the positioning pins 15 and 17 are released from the positioning state. Specifically, the switching valve 25 is switched from the first switching position P1 to the second switching position P2 from the state shown in FIG. 19 are connected to the working gas discharge path 21. As shown in FIG. Also, the tip end side cylinder chamber 18b2 of the first fluid pressure cylinder 18 is connected to the air compressor 20 . As a result, the working gas is discharged through the first gas passage 13a from the base end cylinder chamber 18b1 on the extension side of the first fluid pressure cylinder 18, and the distal end cylinder chamber 18b2 on the retraction side is discharged from the first cylinder chamber 18b1. A working gas is supplied through the three gas passages 13c. Further, the working gas is discharged through the second gas passage 13b from the proximal side cylinder chamber 19b1 on the pushing side of the second fluid pressure cylinder 19 .

Here, the second fluid pressure cylinder 19 is a single-acting cylinder, and by switching to the second switching position P2, the elastic restoring force of the compression spring 24 mechanically and quickly retracts the second positioning pin 17. will be On the other hand, a meter-out speed controller 27 is arranged on the first gas passage 13a connecting the first fluid pressure cylinder 18 and the working gas discharge passage 21 at the second switching position P2. Therefore, the discharge speed of the working gas discharged from the proximal end cylinder chamber 18b1 of the first fluid pressure cylinder 18 through the first gas passage 13a is suppressed by the throttle of the speed controller 27 (see FIG. 8). As a result, the retraction operation of the first fluid pressure cylinder 18 is restricted, and the first positioning pin 15 starts the extraction operation from the first positioning hole 14 after the second positioning pin 17 . As a result, after the second positioning pin 17 is pulled out from the second positioning hole 16, the pulling operation of the first positioning pin 15 from the first positioning hole 14 is substantially started. The respective positioning pins 15 and 17 can be pulled out from the corresponding positioning holes 14 and 16 without the positioning pins 17 interfering with each other.

Further, in the present embodiment, a meter-in type speed controller 28 is arranged on the third gas passage 13c connecting the tip side cylinder chamber 18b2 of the first fluid pressure cylinder 18 and the air compressor 20 at the second switching position P2. It is Therefore, the supply speed of the working gas flowing through the third gas passage 13c to the tip side cylinder chamber 18b2 of the first fluid pressure cylinder 18 is suppressed by the throttle of the speed controller 28 (see FIG. 8). This also restricts the retracting operation of the first fluid pressure cylinder 18 , thereby more reliably preventing interference with the second positioning pin 17 and moving the first positioning pin 15 into the first positioning hole 14 . It is possible to extract from

Further, in the present embodiment, at the second switching position P2, the pressure chamber 8e of the pressure increasing cylinder 8 and the working gas discharge passage 21 are connected, and the retraction valve adjacent to the pressure chamber 8e is connected via the large-diameter piston 8c. Since the chamber 8g and the air compressor 20 are connected, the large-diameter piston 8c can be smoothly slid toward the retraction side, and the movable blade 4 can be quickly lowered.

Although one embodiment of the present invention has been described above, the shearing device according to the present invention is not limited to the configuration illustrated above, and various modifications are possible within the scope of the present invention.

For example, in the above-described embodiment, the first positioning member is pin-shaped (the first positioning pin 15), and the second positioning member having the same pin shape is fitted into the second positioning hole 16 penetrating the first positioning pin 15 in the radial direction. Although the structure for positioning and fixing by joining is exemplified, it is of course possible to adopt a structure other than this. For example, although illustration is omitted, if space constraints permit, the first positioning member is plate-shaped, and one or more second positioning holes are provided through the plate-shaped first positioning member in the plate thickness direction. Alternatively, a structure may be employed in which a second positioning pin corresponding to one or a plurality of second positioning holes can be fitted.

1 Shearing Device 2 Shearing Head 2a First Side 2b Second Side 2c Connecting Part 3 Fixed Blade 4 Movable Blade 4a First Shaft Hole 4b Second Shaft Hole 5 First Drive Cylinder 6 Second Drive Cylinder 7 Positioning Mechanism 8 Pressure boosting cylinder 8e Pressure chamber 8f Pressure boosting chamber 9 First piston rod 9a First pivot shaft 10 Second piston rod 10a Second pivot shaft 11 Hydraulic oil passages 12, 26, 27, 28 Speed controller 12a Throttle 12b Non-return Valve 13 Working gas path 14 First positioning hole 15 First positioning pin 15a Reduced diameter surface 16 Second positioning hole 17 Second positioning pin 17a Reduced diameter surface 18 First fluid pressure cylinder 18b1 Proximal side cylinder chamber 18b2 Distal side cylinder chamber 19 Second fluid pressure cylinder 19b1 Base end cylinder chamber 19b2 Tip end cylinder chamber 20 Air compressor 21 Working gas discharge path 22 First extension 23 Second extension 24 Compression spring 25 Switching valve 101 Welding torch P1 First switching position ( during extrusion)
P2 second switching position (when retracted)

Claims (9)

a shearing head; a fixed blade and a movable blade provided on the shearing head; A shearing device integrally having a connecting portion that connects the side portion and the second side portion on the base end side of each side portion,
The positioning mechanism includes a first positioning hole provided on the tip side of the first side portion, and a first positioning member that is protrusible and retractable with respect to the tip side of the second side portion and that can be fitted into the first positioning hole. In a shearing device having
The positioning mechanism includes a second positioning hole provided on the tip side of the first positioning member and having an opening formed in a direction perpendicular to the direction of emergence and retraction of the first positioning member;
a second positioning member provided so as to be retractable with respect to the first positioning hole, and capable of being fitted into the second positioning hole in a state where the first positioning member is fitted into the first positioning hole ;
a first fluid pressure cylinder capable of reciprocating the first positioning member along the direction of emergence;
a second fluid pressure cylinder capable of reciprocating the second positioning member along the direction of emergence;
and a fluid supply capable of supplying hydraulic fluid to the first and second hydraulic cylinders, respectively . A switching valve is provided between each hydraulic cylinder and the fluid supply source and between each hydraulic cylinder and the fluid discharge path,
The switching valve has a first switching position that configures the connection between each hydraulic cylinder and the fluid supply source and the connection between each hydraulic cylinder and the fluid discharge path such that both hydraulic cylinders produce a pushing motion. ,
switchable to a second switching position configuring the connection between each hydraulic cylinder and the fluid supply and the connection between each hydraulic cylinder and the fluid discharge path such that both hydraulic cylinders produce a retraction motion; A shearing device according to claim 1 . 3. A shearing device according to claim 2 , wherein a meter-in speed controller is disposed between the fluid supply and the second hydraulic cylinder in the first shift position. 3. A shearing device according to claim 2 , wherein the first hydraulic cylinder is a double-acting cylinder, and the second hydraulic cylinder is a single-acting cylinder in which a spring biases the piston toward the retraction side. 5. A shearing device according to claim 4, further comprising a meter-out speed controller disposed between the fluid discharge passage and the proximal cylinder chamber of the first hydraulic cylinder in the second switching position. 6. A shearing device according to claim 4 or 5 , wherein a meter-in type speed controller is arranged between the fluid supply source and the distal cylinder chamber of the first hydraulic cylinder in the second switching position. a movable blade driving cylinder in which a piston is connected to the movable blade;
The first and second fluid pressure cylinders are driven by being supplied with working air from an air compressor as a fluid supply source,
2. The shearing device according to claim 1 , wherein the pressure boosting cylinder is configured to be able to receive supply of working air from the air compressor and supply pressurized working oil to the movable blade driving cylinder. The movable blade driving cylinder is a double-acting cylinder,
8. A shearing device according to claim 7 , wherein the proximal cylinder chamber is connected to an intensifying cylinder and the distal cylinder chamber is connected to the air compressor when the switching valve is in the second switching position. A butt welding apparatus for strip-shaped metal plates, comprising: the shearing device according to claim 1; and a welding torch capable of welding the edges of the strip-shaped metal plates sheared by the shearing device.

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