JPS6336884B2 - - Google Patents

Description

DETAILED DESCRIPTION OF THE INVENTION The present invention relates to an oscillating type shear, and more specifically, the present invention relates to an oscillating type shear, and more specifically, it applies shearing force to the material by upper and lower blades in synchronization with the moving speed of the material to be cut, such as a steel plate being conveyed. This invention relates to an oscillating running shear configured to be able to cut.

Conventionally, an oscillating running shear has been known that applies shearing force to the material while moving the upper and lower blades in the direction of movement of the material in accordance with the moving speed of the material to be cut, cutting the material without stopping it. There is.

Conventional rocking type running shears of this type employ a crank mechanism as the rocking mechanism of the rocking frame, and this crank mechanism is driven by a variable speed electric motor.
Since the swinging speed of the swinging frame is adjusted in accordance with the moving speed of the material by controlling the rotational speed of the motor, a large-capacity motor is required. Furthermore, with the conventional swing type running shear, it was not possible to stop the swing frame to cut the material.

The present invention has been made in order to eliminate the above-mentioned drawbacks of the conventional art, and allows the swinging frame to move steplessly within the range from 0 to a desired speed without requiring a large-capacity electric motor or a complicated structure. It is an object of the present invention to provide an oscillating type running shear configured so that the oscillating speed can be adjusted.

In order to achieve the above object, the present invention provides a swing speed adjusting device for the swing frame separately from the cutting mechanism, and adjusts the swing speed of the swing frame steplessly within a predetermined range from 0. Adopts a structure that can be adjusted.

In the present invention, one tool rest attached to the swinging frame and the other tool rest guided by the swinging frame are connected to a tool rest drive shaft so that they can move up and down in opposite directions to each other, and the tool rest drive shaft and a swinging frame are connected by a link mechanism, and the length of some of the links forming the link mechanism is provided to be freely variable in accordance with the rotation of the turret drive shaft, and the fluctuation range of the length of this link is This swing type running shear is equipped with a swing speed adjustment mechanism that can adjust the swing speed of the swing frame to change the swing speed of the swing frame. In the swinging speed adjustment mechanism, for example, a planetary gear mechanism is used, and the swinging speed of the swinging frame is adjusted to the moving speed of the material by using the locus of movement of the shaft provided at the shaft end of the planetary gear. I was able to match it well.

Hereinafter, the present invention will be explained in detail based on embodiments shown in the drawings.

FIG. 1 and the following illustrate one embodiment of the present invention, and FIG. 1 shows the entire swing type running shear.

In the figure, numerals 1 and 2 indicate side plates of the device, both of which are fixed to a frame (not shown). 2
A beam 3 is horizontally suspended between the upper ends of the two side plates 1 and 2. A bracket 4 is provided in the middle of the beam 3 and projects downward.
A crankshaft 5 is rotatably supported between the left and right side plates 1 and 2. This crankshaft 5 is connected to a motor via a reduction gear.

The upper ends of lower blade frames 6 and 7, which constitute swing frames on the left and right sides with the bracket 4 in between, are rotatably supported on the crankshaft 5 via an eccentric disk 8. 8 is the crankshaft 5
It is fixed with a predetermined eccentricity with respect to.
Therefore, as the crankshaft 5 rotates, the lower blade frames 6 and 7 move up and down in accordance with the amount of eccentricity.

The lower ends of the lower blade frames 6, 7 are connected by a beam 9, and above the beam 9, an elongated opening 10 is formed in the vertical direction in the middle of each lower blade frame 6, 7. These openings 1
A lower tool rest 11 is horizontally mounted and fixed between the lower ends of the blades 0 and 10. A lower cutter 12 is fixed to the lower tool rest 11 over its entire length.

Crank arms 13 and 14 are rotatably supported at their upper ends on the left and right sides of the crankshaft 5 with the bracket 4 in between. crank arm 1
3 and 14 are mounted in the same phase, but are mounted eccentrically with respect to the crankshaft 5, and 180 degrees out of phase with the eccentric disk 8.

The lower ends of these two crank arms 13 and 14 are rotatably supported on an upper tool rest 16 via a shaft 15. Both ends of the upper tool post 16 are fitted into openings 10, 10 of the lower blade frames 6, 7 so as to be able to move up and down. An upper cutter 17 is fixed to the upper tool rest 16 in correspondence with the lower cutter 12.

Since the lower cutter 12 and the upper cutter 17 are attached as described above, the lower cutter 12 rises together with the lower cutter frames 6 and 7 due to the rotation of the eccentric disk 8 as the crankshaft 5 rotates. The upper cutter 17 is lowered by the rotation of the crank arms 13 and 14, and a shearing force can be applied to the material 18 introduced between the two to cut it.

On the other hand, a swing speed adjusting device 19 is connected to the other end of the crankshaft 5 on the outside of the side plate 1 .

This swing speed adjusting device 19 will be described in detail later, but the tip of a link lever 20 that is moved forward and backward and swings by this device is rotatably connected to one end of a swing arm 21. Rotating arm 21
The other end is fixed to the rotating shaft 22, and the rotating shaft 2
2 has the upper ends of arms 23 and 24 fixed at positions corresponding to the lower blade frames 6 and 7, and one ends of link levers 25 and 26 are rotatably connected to the lower ends of these arms. 25,
The other end of 26 is rotatably connected to the middle of the lower blade frames 6, 7.

The swing speed adjusting device 19 has a structure as shown in FIG. Note that FIG. 2 shows the basic structure as viewed from the opposite side to the state shown in FIG. 1, with a part cut away.

This swing speed adjustment device 19 has a casing 27 that is fixedly provided, and within this casing 27, left and right bearing discs 28, 29 are rotatably supported on a sleeve 30 via bearings 31. The crankshaft 5 is connected to the bearing disk 28 side. The sleeve 30 is rotatably supported on the casing 27 via a bearing 30a. However, the crankshaft 5, bearing discs 28, 29, and sleeve 30 are arranged concentrically.

A worm foil 32 is provided on the outer peripheral surface of the sleeve 30.
A worm gear 33 that can be operated from the outside meshes with the worm wheel 32.

Furthermore, an internal gear 34 is formed at the center of the inner circumferential surface of the sleeve 30 over the entire circumference, and a planetary gear 35 is formed on this internal gear 34.
are meshing. A shaft 36 to which the planetary gear 35 is fixed is rotatably supported by the bearing discs 28 and 29. This shaft 36 has bearing discs 28, 2
9, the rotation center position of the sleeve 30, and the planetary gear 3
5 is provided at a position half way between the point on the pitch circle where 5 meshes with the internal gear 34.

One side of the shaft 36 serves as an output shaft, and one end of a lever 37 is fixed to the side opposite to the crankshaft 5. A shaft 38 is provided protruding from the other end of the lever 37, and a slider 39 is rotatably attached to this shaft 38. The slider 39 is slidably fitted into a guide frame 40, and one end of the link lever 20 is fixed at right angles to one end of the guide frame 40. The length between the centers of the shafts 36 and 38 was set to be half the pitch circle of the planetary gear 35.

Further, a link lever 20 is provided on the other end side of the guide frame 40.
A lever 41 is protruded on the same axis as the lever 41, and the lever 41 is slidably fitted into a guide 42, and the guide 42 is rotatably supported on a fixed part of the device via a shaft 43. ing.

Rocking speed adjustment device 19 configured as above
Now, when the crankshaft 5 is rotated, the bearing disc 28
is rotated, and the planetary gear 35 rotates while meshing with the internal gear 34 provided on the sleeve 30. As a result, the center of the shaft 38 and slider 39 is
It always moves on a straight line passing through the center position 0 of the shaft 5 and sleeve 30.

At this time, the movement trajectory A of the planetary gear 35 and the movement trajectory B of the shaft 38 are in a state as shown in FIG.

FIG. 3 shows a skeleton movement locus, and the same parts as in FIG. 2 are denoted by the same reference numerals.

First, the crankshaft 5 is stopped so that it does not rotate, and the worm gear 33 is operated from the outside to rotate the sleeve 30.
5 rotates, the planetary gear 35 moves together with the bearing discs 28 and 29, and the starting position of the shaft 38 is moved to a position corresponding to the meshing position of the planetary gear 35 and the internal gear 34 on the X-axis, which is the horizontal axis. can be located in

The position of the shaft 38 at this time is indicated by the reference numeral 38a in FIG. In this state, the lever 37 is
The axis 36 is located on the X axis as shown by 36.
It is located on the X axis as shown by a. The planetary gear 35 at that time is indicated by the reference numeral 35a.

With this state as a starting state, when the crankshaft 5 is rotated without rotating the sleeve 30, the shaft 36 starts to move via the bearing discs 28 and 29, so it engages with the internal gear 34 which is in a fixed state. The planetary gear 35 begins to revolve while rotating. As a result, the lever 37 is rotated, and the shaft 38 reciprocates on the X-axis with a stroke equal to the diameter of the pitch circle of the internal gear 34, as shown by symbols 38b to 38d. At this time, one revolution of the planetary gear 35 corresponds to one reciprocation. This state is the state in which the maximum stroke of the link lever 20 can be obtained.

In addition, in FIG. 3, the shaft 38 is located at each position 38b.
~38d, the positions of the planetary gear 35, shaft 36, and lever 37 are indicated by b, b, after each number, respectively.
It is shown with c and d attached.

At the start under the above conditions, the third
As shown in FIG. 5 and FIG. 4, the maximum stroke S of the shaft 38 is obtained, but the position of the shaft 38 at the start after rotating the sleeve 30 is indicated by reference numeral 38e in FIG. In this case, the movement of the shaft 38 will pass on the diagonal straight line _X1 . If the diameter of the internal gear 34 is D and the angle of intersection of the straight line _{X 1 with} the straight line
The stroke S becomes smaller.

Furthermore, when the starting position of the shaft 38 is positioned on the Y axis perpendicular to the straight line X, as shown by reference numeral 38f in FIG. This results in a reciprocating motion along the Y-axis. As a result, Dcosθ is 0
Therefore, the movement stroke S of the shaft 38 and the link lever 20 becomes 0.

In this way, by externally operating the worm gear 33 to turn the sleeve 30 and adjust the start position of the shaft 38, the forward and backward stroke of the link lever 20 is stepless from the diameter D of the pitch circle of the internal gear 34 to 0. can be adjusted to

That is, being able to arbitrarily set the stroke of the link lever 20 means that the rotation angle of the shaft 22 can be adjusted. The swing angle of 7 will be changed. Furthermore, when the swinging angle of the lower blade frames 6 and 7 having a certain length changes, the swinging period is always constant, so the swinging speed changes. This means that it can be synchronized with the speed.

In other words, the swing speed of the lower blade frames 6, 7 can be adjusted from a state where the material 18 is stopped to a state where the material 18 is moving at various speeds.

Next, the operation of this embodiment configured as above will be explained.

First, with the crankshaft 5 stopped, the material 1 is
The worm gear 33 is rotated according to the moving speed of the shaft 38 and the sleeve 30 is rotated by an appropriate angle to set the starting position and horizontal movement stroke of the shaft 38 and the slider 39. Once the settings are completed, the sleeve 30 should not be rotated.

When the crankshaft 5 is rotated in this state, the lower blade frames 6 and 7 move up and down via the eccentric disc 8, and the upper tool rest 16 starts moving up and down via the crank arms 13 and 14. The vertical movement of the lower blade frames 6, 7 and the vertical movement of the upper tool rest 16 are performed with a phase shift of 180 degrees, and the upper and lower blades 12, 17 reach the shearing position at the position of the pass line of the material 18, respectively. Cut the material 18.

At this time, the swing speed adjustment device 19
Since the lower blade frames 6 and 7 swing at a speed synchronized with the moving speed of the material 18, the material 18 is cut while traveling at a predetermined speed.

Of course, as mentioned above, since the swing speed of the lower blade frames 6 and 7 can be set to 0, it is also possible to stop cutting the material 18.

As is clear from the above description, according to the present invention, since the swing speed adjustment device for the lower blade frame, that is, the swing frame is provided, the swing speed of the swing frame can be adjusted to match the running speed of the material. It can be adjusted steplessly over a wide range from 0 to a constant speed,
There is no need for a special motor such as a variable speed motor, and the electric capacity can be significantly reduced.

In addition, since the cutting mechanism and the swing speed adjustment device are separate structures, regardless of the speed of the material,
The cutting speed is always constant, and most of the cutting torque can be covered by inertial torque.

Since the cutting mechanism is a so-called guillotine cut, the cutting is reliable, and the cut surface is approximately perpendicular to the material and smooth.

In addition, in the device of the present invention, the high-load portion has a relatively low rotational speed and can be made structurally strong, so that the pressure value of the crank metal etc. can be suppressed and it can cope with high-speed shearing. Although it can be made to have low rigidity in order to receive a low load, it also has a function that can buffer the overload even if an emergency overload occurs during asynchronous cutting with the finishing mill.

[Brief explanation of drawings]

The figure explains one embodiment of the present invention.
FIG. 2 is a perspective view of the entire device, FIG. 2 is a partially cutaway perspective view of the swing speed adjusting device, and FIGS. 3 to 6 are explanatory diagrams showing the operating principle. 5... Crank shaft, 6, 7... Lower blade frame (swinging frame), 8... Eccentric disk, 11... Lower tool rest, 12... Lower blade, 13, 14... Crank arm, 16...Upper tool post, 17...Upper cutter, 18...Material, 19...Rocking speed adjustment device, 20, 25, 26...Link lever, 21...
...Rotating arm, 22...Rotating shaft, 23, 24...
Arm, 28, 29...Bearing disc, 30...Sleeve, 32...Worm wheel, 33...Worm gear, 34...Internal gear, 35...Planetary gear, 37...Lever, 38...Shaft, 39 ……
Slider, 40...Guide frame, 42...Guide.

Claims (1)

[Claims] 1. A lower tool rest attached to the swinging frame and an upper tool rest guided by the swinging frame are connected to the tool rest drive shaft via a crankshaft and an eccentric disk so that they can move up and down in opposite directions, In a swing-type running shear in which the tool post drive shaft and the swing frame are connected by a link mechanism and the swing frame swings in response to the rotation of the tool post drive shaft, the tool is attached concentrically to the tool post drive shaft. A bearing disc is rotatably mounted coaxially to a sleeve that has an internal gear and can be rotated from the outside by a sleeve rotation device, and a planetary gear is mounted eccentrically and rotatably on the bearing disc. , a slider that engages with the internal gear and is mounted eccentrically on the planetary gear shaft is slidably mounted within a guide frame provided in a part of a link lever that can slide in a predetermined position and move forward and backward. An oscillating running shear equipped with a oscillating speed adjustment mechanism that can change the oscillating speed of the oscillating frame by adjusting the length of the link with the guide frame of the link mechanism.