JPS6232047B2 - - Google Patents

Description

DETAILED DESCRIPTION OF THE INVENTION The present invention relates to a pendulum-type running shear machine, and particularly to a pendulum-type running shear machine that reduces the swinging force generated by a swinging frame that swings in synchronization with the conveyance speed of the material to be sheared. Regarding shears.

In general, various types of shearing machines are available for cutting moving materials such as steel slabs, but recently, shearing machines that perform shearing while swinging the shear body in synchronization with the conveyance speed of the material to be sheared. Patent application 1977-88096
A pendulum-type running shear machine has been proposed as shown in No.

The conventional pendulum type running shearing machine is shown in Figure 1~
As shown in FIG. 2, the main crankshaft 1 is equipped with a drive device consisting of an electric motor 2 and a speed reducer 3 with the main crankshaft 1 as an output shaft, and the main crankshaft 1 is equipped with a shear body 4 rotatably. This shear body 4 has a swing frame 7 which is rotatably attached to an eccentric part 5 (eccentric distance R ₂ ) of the main crankshaft 1 and has a lower cutter 6 fixed thereto, and has a swing frame 7 which is rotatably mounted on an eccentric part 5 (an eccentric distance R 2 ) of the main crankshaft 1 and has a swing frame 7 to which a lower cutter 6 is fixed. (eccentric distance
A connecting rod 9 is rotatably attached to R ₃ ), and the upper cutter 10 is attached so as to be able to slide within the swing frame 7 via this connecting rod 9. . Further, a swinging device 11 is connected to the swinging frame 7 for imparting a swinging motion to the swinging frame 7 . A speed tuning device 13 for swinging the swing frame 7 in synchronization with the transport speed of the material 12 to be sheared is connected to the swing device 11 .

However, in such a conventional pendulum-type running shearing machine, during normal operation when no shearing work is performed, the torque due to the inertial force of the swinging frame 7 is input to the speed synchronization device 13 via the swinging device 11. However, during the shearing operation, torque due to the transmission force in the opposite direction to the movement direction of the swing frame 7 generated by the shearing reaction force is also input to the speed tuning device 13. That is, as shown in FIG. 3, the swing frame 7 and the connecting rod 9 are
A shearing torque T _c is generated on the main crankshaft 1 due to the shearing reaction forces F and F' generated at . This shearing torque _Tc can be roughly expressed by the following equation.

T _c = F × _{R 2} × sin _{θ c} + _{F ′ M}
torque is given. Due to this torque T _M , the swing frame 7 receives a swinging force that causes it to rotate in the same direction as the rotation of the main crankshaft 1 . This swinging force becomes a force F _D that attempts to move the swing frame 7 in the opposite direction to the direction of movement thereof, and becomes a torque input to the speed tuning device 13. This F _D
The acting force is determined by the equilibrium condition of each acting force shown in FIG. 3, and is roughly expressed by the following equation.

F _D = T _M /l _D …(2) Here, l _D ; Moment arm about the main crank axis T _M = T _c As can be understood from equations (1) and (2), the run-out force F
_D increases as the shear forces F and F' increase. That is, if the sheared material 12 is large and a high-load shearing machine is to be supplied, the speed tuning device 13 must be made stronger as the swinging force F _D increases. Graphs of this state are shown in FIGS. 4 and 5. These figures show the relationship between the crank rotation angle, the cutting edge speed V _P and the input torque T _G to the speed tuning device 13.
shows the relationship between That is, when no shearing operation is performed, the input torque is due to the inertial force of the swing frame 7, so it is shown by curve b, and the maximum torque is given by T _nax1 . However, at the time of shearing, the torque generated by the above-mentioned run-out force F _D is added only to the shearing area W, resulting in a curve a, and the maximum torque is T _nax2 . When the shearing force becomes large, T _nax2 >T _nax1 , and the input torque T _G of the speed tuning device 13 is determined by T _nax2 , so that the speed tuning device 13 needs to be strengthened. In this way, in conventional pendulum-type running shears, the scale of the speed tuning device, which accounts for about one-third of the total cost of the shearing machine, is determined by the oscillating force F _D that occurs only during shearing. The problem is that the higher the capacity, the larger the device must be.

In view of the above-mentioned conventional problems, it is an object of the present invention to provide a pendulum-type running shear machine that can reduce the oscillating force only for a short period of time during shearing, thereby reducing the torque input to the speed tuning device. purpose.

In order to achieve the above object, the pendulum-type running shearing machine according to the present invention detects the time of shearing and is connected to a swinging device that is activated by the detection means and swings a swinging frame of the shear body. The structure includes an actuator that applies a pushing force in the speed direction of the material to be sheared, so as to apply an acting force that opposes the swinging force during shearing.

DESCRIPTION OF THE PREFERRED EMBODIMENTS Preferred embodiments of a pendulum-type running shearing machine according to the present invention will be described in detail below with reference to the drawings.

As shown in FIG. 5, in the pendulum-type running shearing machine according to this embodiment, the main crankshaft 1 is rotated counterclockwise via a drive device similar to that of the conventional shearing machine (FIG. 1). It's becoming like that. A pair of eccentric parts 5 having an eccentric distance R ₂ of this main crankshaft 1
A swing frame 7 is rotatably suspended from the frame.
A lower cutter 6 is fixed to the swing frame 7 with its cutting edge facing the main crankshaft 1 side. Further, an eccentric part 8 having an eccentric distance R ₂ having a phase difference of 180 degrees from the eccentric part 5 of the main crankshaft 1 is formed, and a connecting rod 9 is rotatably attached to this eccentric part 8. . A tool rest 14 is rotatably attached to the tip of the connecting rod 9, and an upper cutter 10 with its cutting edge directed toward the lower cutter 6 is fixed to this tool rest 14.
The upper cutter 10 can slide within the swing frame 7. Therefore, by rotating the main crankshaft 1, the upper knife 10 and the lower knife 6 move relative to each other in the shearing direction, and the material to be sheared 12 existing between the two knives can be cut. On the other hand, reducer 3
(See Figure 1) Speed tuning device 13
has a structure in which an eccentric portion 15 (eccentric distance R ₁ ) formed on its output shaft can be rotated, and the cutting edge speeds of the material to be sheared 12 and the swinging frame 7 are matched. That is, the eccentric portion 15 is
1, and its swinging device 11 is connected to the swinging frame 7 to swing the swinging frame 7. The rocking device 11 is the speed tuning device 1
A link 16 connected to the eccentric portion 15 of No. 3, and a lever 17 that is connected to one end of this link 16 and swings.
and a tuning shaft 18 that is rotated by the operation of the lever 17, and a link 19 that provides a rocking motion to the swing frame 7 by the rotation of the tuning shaft 18, and a link 19 that connects the link and the tuning shaft 18. and a lever 20 that provides reciprocating motion to the link 19.

In contrast to such a device, the present invention particularly applies a pushing force to the swinging frame 7 in the speed direction (arrow A) of the material to be sheared 12 during shearing. That is, an arm 22 provided with rollers 21 is installed at one end of the main crankshaft 1, and this arm 2
2, the rollers 21 are adjusted to perform circular motion with the rotation of the main crankshaft 1 with an eccentric distance R ₄ . On the other hand, a guide 23 is attached to the base frame (not shown).
A cam 24 that is slidable is inserted into the guide 23. The cam 24 is provided protrudingly close to a part of the circular locus of the roller 21, and the roller 21 and the cam 24 are selected to have a positional relationship in which they come into contact only during shearing. This cam 24
A hydraulic cylinder 25 is provided at the rear end, and the cam 2
4, the hydraulic cylinder 25 is activated.

Further, the hydraulic cylinder 25 and a separate hydraulic cylinder 26 are connected in series to a lever 20 that connects the link 19 connected to the swing frame 7 described above and the rotating synchronized shaft 18. This hydraulic cylinder 26 can respond to the reciprocating motion of the link 19 connected to the swing frame 7. This hydraulic cylinder 26 and the hydraulic cylinder 25 are connected to each other through piping 2.
7, and there is an accumulator 2 on the way.
8 is provided. Further, a pump 29 is provided branching off from the pipe 27, and a switching valve 30 is interposed between the pump 29 and the pipe 27.
This switching valve 30 is electromagnetically operated, and the coil of the switching valve 30 is connected to an angle detector 31 that is attached to the main crankshaft 1 and outputs a signal when detecting shearing. It is designed to be activated by a signal from That is, the output signal causes the switching valve 30 to open and both hydraulic cylinders 2 to open.
The piping 27 between 5 and 26 serves as a containment circuit.

The pendulum-type running shearing machine according to this embodiment configured as described above operates as follows. That is,
In the shear standby position, the switching valve 30 is set to the position shown in FIG. 6, and the hydraulic cylinder 26 on the swinging device 11 side operates at low pressure, so that no large force is generated with respect to the movement of the swinging frame 7. However, when the shearing position is reached, the shearing position is detected by the angle detector 31, and the detection signal gives a command to the switching valve 30 to connect the pump 29 and the pipe 27. As a result, the distance between the hydraulic cylinders 25 and 26 is It becomes a containment circuit. Further, in the shearing position, the rollers 21 of the arm 22 provided on the main crankshaft 1 and the cam 24 come into contact, so that the hydraulic oil in the hydraulic cylinder 25 is released. At this time, as mentioned above, since the piping 27 is a containment circuit, the operating shaft is connected to the other hydraulic cylinder 26.
This reduces the swinging force that is generated by shearing reaction force and places a high load on the speed tuning device 13. Since the hydraulic cylinder 26 operates only during the shearing period due to the positional relationship between the roller 21 and the cam 24, the pushing force by the hydraulic cylinder 26 acts only during the shearing period. When the shearing is completed, a command is given from the angle detector 31 to turn off the switching valve 30, and at the same time the containment circuit of the piping 27 is released, the roller 21 and the cam 24 are separated, and the hydraulic cylinder 25 does not operate. .

In addition, since an accumulator 28 is interposed in the piping 27, an abnormal pressure increase in the containment circuit is prevented, and the pressure in the circuit is increased by the operation of the hydraulic cylinder 25, and the pressure in the circuit is increased by the operation of the hydraulic cylinder 25.
can increase the acting force of

Further, FIG. 7 shows another embodiment. In this embodiment, instead of using the hydraulic cylinders 25 and 26 to reduce the swinging force, an air clutch 33 is provided on the output shaft of the drive motor 32, and a gear 34 is attached to the synchronizing shaft 18 via the clutch 33.
An operating gear 35 that meshes with is attached. Also, the air clutch 33 has an air tank 3.
6 with the air piping 37, and the air piping 37
A switching valve 30 operated by an angle detector 31 similar to that of the previous embodiment is interposed therein.

In this embodiment, the switching valve 30 operates during shearing, and air is supplied from the air tank 36 to the air clutch 33.
and actuates the air clutch 33. Before approaching the shear position, the drive motor 32 is driven to substantially equal the rotation of the synchronized shaft 18 and the air clutch 33
The rotational force is transmitted to the synchronized shaft 18, and acts to reduce the whirling force. In such an embodiment, in particular, a simple structure is adopted in which only the angle detector 31 is attached to the main crankshaft 1 side, and an actuator such as a drive motor 32 is attached to the side of the tuned shaft 18, as shown in FIG. All you need to do is place the .

As explained above, in the pendulum-type running shearing machine according to the present invention, it is possible to reduce the swinging force that occurs only during shearing, and as a result, the input torque to the speed tuning device is reduced, and the tuning device This has the effect of reducing the size of the device.

[Brief explanation of the drawing]

Figure 1 is a skeleton diagram showing the mechanism of a conventional pendulum-type running shear, Figure 2 is a side skeleton diagram of Figure 1, Figure 3 is a skeleton diagram showing the mechanical relationship of the shear body, and Figure 4. is the crank rotation angle -
A graph showing the relationship between the cutting edge speed, FIG. 5 a graph showing the relationship between the crank rotation angle and the input torque of the speed synchronizer, and FIG. 6 showing the mechanism of an embodiment of the pendulum-type running shearing machine according to the present invention. skeleton diagram,
FIG. 7 is a skeleton diagram showing the mechanism of another embodiment, and FIG. 8 is a plan view showing the structure of the same embodiment. 1... Main crankshaft, 4... Shear body, 7...
... Rocking frame, 11 ... Rocking device, 12 ... Sheared material, 13 ... Speed tuning device, 18 ... Tuning shaft, 21 ... Roller, 22 ... Arm, 24 ... Cam, 25, 26 ... Hydraulic cylinder, 28 ... Accumulator, 29 ... Pump, 30 ... Switching valve,
31... Angle detector, 33... Air clutch, 3
6...Air tank.

Claims (1)

[Scope of Claims] 1. A drive device that operates a main crankshaft, a shear body rotatably suspended on an eccentric portion of the main crankshaft, and a rocker that swings this shear body in the direction of the speed of the material to be sheared. Detection means for detecting the time of shearing in a pendulum-type running shear machine comprising a moving device and a speed synchronizing device that is connected to the swinging device and synchronizes the swinging motion of the shear body to the speed of the material to be sheared. and an actuator connected to the swinging device that is activated by the detection means and applies a pushing force in the speed direction of the material to be sheared only during shearing. 2. The pendulum-type running shearing machine according to claim 1, wherein the actuator is a hydraulic cylinder operated by a cam mechanism connected to the main crankshaft. 3. The pendulum-type running shearing machine according to claim 1, wherein the actuator is a drive motor having an air clutch, and the air clutch is actuated by the detection means.