KR830002242B1 - Oscillating day shear - Google Patents

Abstract

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Description

Oscillating day shear

1 is a diagram for explaining the equivalent plate thickness of the shear material.

2 is a front view of the swing type weekly shearing machine according to the first embodiment of the present invention.

3 is a side view of FIG.

4 shows a device for adjusting the phase between the eccentric portion of the main crankshaft and the eccentric portion of the swinging crank.

5 is a cross-sectional view taken along the line I-I of FIG.

6 is a diagram schematically showing a swing-type weekly shear.

7 shows the principle of speed change.

8 is a diagram showing the relationship between the main crankshaft rotation angle and the cutting blade horizontal speed and the vertical cutting blade gap.

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a swinging type shearing machine, and more particularly to a swinging type shearing machine for shearing a shearing material to a predetermined length by repetition of starting and stopping of the shearing machine.

In the swing type weekly shearing machine, it is required to match the speed of the cutting blade with the speed of the cutting material in order to prevent the wound on the cutting machine. However, since the horizontal speed Vs of the cutting blade changes as the cosine function of the rotational angle wt of the main crankshaft, as shown by the following equation, the horizontal speed Vs of the cutting blade and the shear material are always in shear. Cannot match the speed (Vm).

Vs = πDNs cos wt (1) Ns: Rotational speed of main crankshaft

L : 전단 길이Where Ns =

L: Shear length

When the shearing starts now, i.e., when the cutting blades are entangled with the shear material, the speeds of both are not coincident, the shear material is wound by the cutting blade.

On the other hand, if there is a large difference between the speed of the cutting blade after the cutting edge is engaged with the material to be sheared and the peripheral speed of a device such as a pitch roller for conveying the material to the front end, It is easy to produce imaging by friction. However, among the two wounds applied to the above-described material to be sheared, the scratched side is made larger by the sharp edge, which is a serious problem. In practice, the horizontal speed and the width of the cutting edge at the position where the cutting edge is fed into the material to be sheared. The speed of cutting is adjusted to match.

And generally, as shown in FIG. 1, in order to alleviate the impact at the time of shearing and to reduce shear force, the inclination angle (alpha) is provided in one of the upper and lower cutting blades (not shown), but The interval between the upper and lower cutting edges in which the upper and lower cutting edges are in contact with the shear material 1 varies not only with the thickness but also with the width of the sheet. If the upper and lower cutting edges are in contact with the material to be sheared and the change of the gap between the upper and lower cutting edges until the shear is completely completed is called the equivalent thickness (T), then T is expressed as follows. appear.

tanα+t_m T = t _B + t _m =

tanα + t _m

Where B is the width of the plate

t _m : actual plate thickness

That is, in the swing type weekly shearing machine, it is necessary to adjust the blade edge horizontal speed in accordance with the equivalent plate thickness of the blade material so that the horizontal speeds of the blade material and the blade edge coincide with each other at the time of inheritance.

Therefore, when shearing the shearing material to a certain length with a swinging weekly shear, there are a type of continuously rotating the shear and a type of repeating start and stop.

The former shearing device is equipped with the apparatus which synchronizes the speed | rate when the blade tip and the to-be-transfer material are passed in by changing the swing amplitude of a cutting blade.

This tuning device cannot be miniaturized because the mechanism is complicated and the strength is restricted.

For this reason, since the swing amplitude of a cutting blade cannot be made small, the minimum shear length cannot be made small and the change width of a shear length cannot be made large.

On the other hand, there is one disclosed in Japanese Laid-Open Patent Publication No. 53-72281 as the latter shearing machine. This shearing device has the advantage that the swinging amplitude of the cutting blade is constant, so that the swinging device can be miniaturized and the shearing length can be changed extensively only by changing the interval between starting and stopping of the shearing machine. There is a drawback that the adjustment of the blade tip speed is difficult.

That is, the shearing machine described in the above publication transmits the rotation of the crankshaft to the oscillation crank via the gear device, and transmits the eccentric rotational movement of the oscillation crank to the frame via the link, thereby oscillating the speed of the frame, The speed adjustment is made by changing the mounting position of the link frame.

Therefore, in the previous stage, since the part to be adjusted is disposed in the swinging frame, there is a drawback in that it cannot be controlled during shearing.

In addition, there is a disadvantage that the adjustment workability is bad because the part to be adjusted is located in a narrow space between the gear and the frame.

SUMMARY OF THE INVENTION An object of the present invention is to provide a swing type weekly shearer having a constant blade tip oscillation amplitude that can be easily adjusted so that the blade tip horizontal speed matches the speed of the material to be sheared even when the frame swings during shearing.

According to the present invention, the main crankshaft rotated by the drive device, the frame supported by the rotating material on the first eccentric portion of the main crankshaft, the cutting blade fixed to the frame, and the rotating material on the second eccentric portion of the main crankshaft A lower cutting edge support fixed to the frame while being supported by a sliding material, a lower cutting edge fixed to the lower cutting edge support, and a gear for transmitting the rotational force of the driving device to the swinging crank mounted on the eccentric portion of the rotating shaft. And a means for adjusting the interlocking position of the gear of the gear device, comprising a link for transmitting the eccentric motion of the rocking crank to the frame as the rocking motion, and the gear of the gear device as a helical gear. At the same time, at least one of the helical gears can be moved in the axial direction so that the axial position of the helical gear is determined by the adjustment means described above. An oscillating weekly cutter is obtained, which is characterized in that it is locked.

Hereinafter, an embodiment of the present invention will be described with reference to the drawings.

2 is a front view showing a part of the swinging weekly shearing machine in cross section,

3 is a side view of FIG. 2.

The main crankshaft 4 is driven by the DC motor 2 via the speed reducer 3.

The main crankshaft 4 has a first eccentric part (eccentric amount R ₂ ) and a second eccentric part (eccentric amount R ₃ ) which are 180 degrees out of phase with each other, and the frame 5 rotates in this first eccentric part. It is supported by materials.

On the other hand, the connecting rod 6 is supported by the 2nd eccentric part with the rotating material similar to the frame 5. As shown in FIG.

The lower cutting edge support 7 which slides in the frame 5 is connected to the upper part of the connecting rod 6.

The upper cutting edge 8 and the lower cutting edge 9 are fixed to the lower portion of the frame 5 and the upper portion of the lower cutting edge support 7, respectively.

Under such a configuration, the upper and lower cutting blades 8 and 9 are attached and detached once in one rotation of the main crankshaft 4.

A helical gear 10 is attached to both ends of the main crankshaft 4 so that the rotational force of the main crankshaft 4 is equal to the helical gear 10 of the helical gear 10 via the intermediate gear 11. To be delivered).

15 represents a rotation axis of the swing crank 16 having a constant eccentricity R ₁ , and a link 17 is connected between the swing crank 16 and the frame 5. With this structure, the frame 5 oscillates once with respect to one rotation of the main crankshaft 4.

4 and 5 are detailed views of the adjustment device of the helical gears 11 and 12 in engagement positions. FIG. 4 is a front view and FIG. 5 is a sectional view taken along the line I-I of FIG.

20 is a DC motor, 21 is a shaft connected to the DC motor 20, 22 is a two-branch rotary arm that is integrally rotated by pin coupling to the shaft 21, 23 is a rotary material at the tip of the rotary arm 22 And a cam follower fitted to the groove 24 provided in the helical gear 12.

The spline processed on the shaft 15 of the swinging crank 16 is fitted into the spline groove of the helical tooth 12.

As a result, when the DC motor 20 is driven, the helical gear 12 moves in the axial direction while rotating along the tooth surface of the intermediate gear 11.

Therefore, the phases of the rotation angles of the eccentric portion of the swinging crank and the eccentric portion of the main crank shaft can be offset. If γ is the amount of phase out now, γ appears as follows.

(3) β : 헬리컬 치차(12)의 비틀림각γ =

(3) β: torsion angle of helical gear 12

Where Y is the axial movement amount of the helical gear 12 Dp is the diameter of the pitch circle of the helical gear 12

6 is a view schematically showing a swing-type weekly electric motor,

A seventh respective speed _{(V A), (V B} ) of the eccentric position of the parts (B) and the position (C) of the blade tip of the main crankshaft first eccentric position of the parts (A), the swing crank turn, (V _S Is a diagram showing the relationship between

In FIG. 7, a solid line shows the case of (gamma) = 0.

The velocity V _{A in} the first eccentric portion A is represented by V _A = 2πR ₂ cosωt regardless of γ.

In contrast, the speed V _B at the position B of the eccentric portion of the swinging crank becomes a function of γ and is expressed by the following equation.

V _B = 2πR ₁ cos (ωt + γ) (4)

Therefore, by changing the value of γ, V _B can be changed like a dotted line, so that the blade tip horizontal speed V _S can also be changed.

By adjusting γ in this way, the blade tip speed V _S can be changed with respect to the rotation angle ωt of the main crankshaft, so that the blade tip horizontal speed and the speed of the material to be fed when the plate thickness of the material to be cut change. Can be matched.

This shape is explained using FIG. That is, as shown in the same figure, the amount of eccentricity R ₁ of the swinging crank is determined in advance so that the blade tip speed and the speed of the shear material coincide at the point E with respect to the shear material having the maximum equivalent plate thickness Tmax. .

In this state, if the shear material with the minimum equivalent thickness (Tmin) is sheared, the shear starting point becomes the point (F), and the speed at which it is fed does not coincide.However, by adjusting γ, the rotation angle of the main crankshaft is adjusted as in the dotted line. By changing the horizontal speed of the blade tip, it is possible to match the speed at the time of inheriting at the point G. According to the Example of this invention demonstrated above, the following effects are acquired.

(1) The blade tip speed can be adjusted by changing the gear engagement of the gear that does not oscillate during shearing, so the speed at the time of inheriting during shearing can be easily adjusted.

(2) The gear engaging position adjusting device is provided on the shaft surface of the shaft which does not face the frame of the main frame of the gear unit, so that the adjustment work can be performed in a large space.

(3) As the gear is used to adjust the meshing position by moving the helical gear in the axial direction by using the helical gear, the blade tip speed can be changed regardless of the swing of the frame.

As described above, according to the present invention, in the swing type weekly shearing machine, the shearing material is sheared to a constant length by repeating the movement and stop of the shearing machine, and the blade tip swing amplitude is constant. Excellent effects are obtained that can be easily adjusted to match.

Claims (1)

The main crankshaft rotated by the drive device, the frame supported by the rotational material on the first eccentric part of the main crankshaft, the phase cutting blade fixed to the frame, and the rotational material supported by the second eccentric part of the main crankshaft, A lower cutting blade support mounted to the frame with a sliding material, a lower cutting blade fixed to the lower cutting blade support, a gear for transmitting the rotational force of the driving device to the swinging crank mounted on the eccentric portion of the rotating shaft, A shearing machine comprising a link for transmitting an eccentric motion of a crank to a frame as a rocking motion, comprising a device for adjusting the engagement position of a plurality of gears constituting the gear, and the gear of the gear At the same time as the helical gear, at least one of the helical gears is movable in the axial direction so that the axial position of the helical gear is determined by the adjustment device described above. Rocking type short weeks ago that the so characterized.

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