JPS5929398B2 - round blade tools - Google Patents

Description

[Detailed description of the invention] The present invention can be used for shearing various raw materials such as paper.

This relates to round-blade tools for use. BACKGROUND ART Conventionally, a round-blade tool as shown in FIG. 1 has been used to shear various materials such as paper.

That is, the lower blade 1 is fixed to the drive shaft 3 of the motor 2,
Further, the upper blade 4 is fixed to a holder TVC rotatably and movably in the axial direction via a shaft 5vc bearing 6 installed substantially parallel to the drive shaft 3. The upper blade 4 is pressed toward the lower blade 1 by the spring 8, and the upper blade rotates due to the frictional force generated at the contact area between the lower blade 1 and the upper blade 4 when the motor 2 is driven to rotate. Now, the workpiece is fed between the lower blade 1 and the upper blade 4, which rotate while in contact with each other, and is sheared. By the way, the lower blade 1 is connected to the motor 2Vc.
Therefore, when the motor 2 is driven to rotate, the drive shaft 3 of the motor 2 vibrates slightly, causing lateral runout.
Since it is energized to the side, it is able to follow the lower blade IVC.

However, the lower blade 1 and the upper blade 4 have a diameter of 2,500 μm.
It is rotated and driven at a high rotation speed of 3,000 μm,
Along with this, when the lateral runout period of the lower blade 1 becomes faster, the upper blade 4 becomes unable to follow the lower blade IVC, and finally the vibration with a value larger than the maximum amplitude value of the lateral runout of the lower blade 1 is applied to the upper blade 4. As a result, the upper blade 4 and the lower blade 1 come into contact with and separate from each other.

During this contact and separation, the upper blade 4 moves in parallel in the axial direction, as shown in FIGS. 2 and 3, but there is no lateral runout in which the radius line of the upper blade 4 is inclined with respect to the central axis of the shaft 5. Therefore, when the upper blade 4 and the lower blade 1 are once separated and brought into contact again, the upper blade 4 and the lower blade 1 come into point contact. The impact force generated when this point contacts is proportional to the elastic force of the spring 8, and in order to maintain the appropriate contact pressure between the upper blade 4 and the lower blade 1, a spring with a relatively high spring coefficient is used. Due to the usage, the impact force must be relatively large, which causes the disadvantage that the cutting edges of the upper blade 4 and the lower blade 1 are damaged and their lifespan is significantly reduced. In particular, when the upper blade 4 and lower blade 1 are made of cemented carbide, which has been widely used recently, the wear of each cutting edge due to shearing is small due to its high hardness, but on the other hand,
Because of the brittleness, the cutting edge easily breaks, resulting in a significant reduction in service life.As a result, the upper blade 4 or lower blade 1 must be replaced more frequently, reducing work efficiency, which in turn causes a rise in the manufacturing cost of the product. There were some shortcomings. Therefore, in order to improve the above-mentioned drawbacks, the present applicant has proposed
In No. 6, we proposed a round-blade tool with an upper blade that can follow the lateral runout of the lower blade.

To explain this with reference to FIG. 4, a shaft 11 is installed substantially parallel to the drive shaft (not shown) of the motor to which the lower blade 10 is attached, and a flange 12 is provided protruding from a predetermined position on the outer circumferential surface. A generally annular bush 13 is rotatably fitted, and a holder 14 is fitted to the bush 13 so as to be movable in the axial direction.
An elastic body 15 is interposed between the holder 14 and the flange 12, and a blade edge adjustment screw 16 is screwed into the bush 13, which abuts the other side of the holder 14 and faces the flange 12. . An upper blade 19 is elastically displaceably mounted in an annular recess 17 formed along the circumferential direction on the outer periphery of the holder 14 via an elastic body 18. According to the above-mentioned round blade tool, the contact pressure of the upper blade 19 against the lower blade 10 is adjusted by appropriately setting the screwing amount of the blade edge adjustment screw 16, and the elastic body 18 that clamps the upper blade 19 is By setting the coefficient to an appropriate value, even if the lower blade 10 rotates at high speed and causes lateral runout at a fast cycle, the upper blade 19 can be moved to the lower blade 1.
0 can be made to follow.

In addition, if the upper blade 19 and the lower blade 10 come into contact with each other and separate from each other, the upper blade 19 undergoes two elastic displacements: parallel movement in the axial direction and lateral runout in which the radius line is inclined with respect to the central axis. Therefore, when the upper blade 19 and the lower blade 10 are once separated and come into contact again, the upper blade 19 and the lower blade 10
As shown in the figure and FIG. 6, they come into surface contact with each other. Therefore, when the upper cutter 19 and the lower cutter 10 are once separated and come into contact again, the impact load per unit area is small, the risk of each cutting edge breaking is significantly reduced, and the tool life is extended. becomes possible. However, if the lateral runout of the lower blade 10 is large, even if the elastic modulus of the elastic body 18 is set to an appropriate value, there is a drawback that the upper blade 19 cannot follow the lower blade 10. .

Furthermore, when fitting the bush 13 with the upper blade 19 fixed to the shaft 11VC, it is necessary that the side surface of the upper blade 19 be parallel to the side surface of the lower blade 10 and in contact without creating a gap. Bush 13 is the axis 11VC. After fitting,
Although the side surface of the upper blade 19 is brought into pressure contact with the side surface of the lower blade 10 by adjusting the screwing amount of the blade edge adjustment screw 16, the side surface of the Hato blade 19 and the side surface of the lower blade 10 cannot be aligned accurately in parallel. As a result, the lower blade 10 causes side vibration, and the upper blade 1
There is a risk that the cutting edge will break when the blade 9 becomes unable to follow.

Furthermore, since the positioning of the upper blade 19 in the axial direction cannot be finely adjusted, it becomes difficult to adjust the contact pressure between the upper blade 19 and the lower blade 10, and there is a drawback that the workpiece cannot be sheared smoothly.

The present invention has been made in view of the above-mentioned circumstances, and its purpose is to enable the upper blade to follow the lateral runout of the lower blade without causing it to come into contact with or separate from the upper blade, and to allow the lateral vibration of the lower blade and the upper blade to The object of the present invention is to provide a round-edged tool that can be easily parallel-aligned and that does not cause chipping of the cutting edge.

An embodiment of the present invention will be described below with reference to the drawings.

FIG. 7 shows a partially cut away round-blade tool of the present invention, in which reference numeral 20 denotes a support shaft onto which a sleeve 21 is extrapolated so as to be movable in the axial direction.
A 11C holder 22 is rotatably inserted via a bearing 23. Therefore, the holder 22 is supported by the support shaft 20 so as to be rotatable and movable in the thread direction. The holder 22 is constructed by overlapping two disc-shaped members 22a and 22b and fixing these members 22a and 22b together using a set screw 24, and the outer peripheral surface of one member 22a is notched in a step-like manner all around the circumference, and a groove 2 having a substantially U-shaped cross section is formed on the side surface of the step.
5 is formed, and a groove 26 having a substantially U-shaped cross section is similarly formed on the side surface of the other member 22b facing this groove 25. A mounting recess 27 is formed along the circumferential direction.

A cushion ring 28 is fitted into the mounting recess 27, and an upper blade 30 made of cemented carbide and having a cutting edge 29 formed on the outer peripheral edge of one side is held between the cushion ring 28 and inserted into the mounting recess. 27 so as to be elastically displaceable in the axial direction of the support shaft 20 and tilted relative to the axis. The upper blade 30 has its one side peripheral edge in contact with the one side peripheral edge of a lower blade 31 fixed to a drive shaft (not shown) of a motor installed in the round blade tool body, and lowers when the motor is driven. It is adapted to rotate together with the blade 31. On the other hand, the support shaft 20 has a fitting part 32 eccentrically protruding from its one end flange 20a, and the fitting part 32 is inserted into a fitting hole 34 formed in a vertical part 33a of a frame 33. At the same time, by tightening the tightening nut 36 with the washer 35 interposed on the threaded portion 32a formed on the outer peripheral surface of the fitting portion 32 protruding from the fitting hole 34, the frame 33 is vertically fixed. The portion 33aVC is supported horizontally.

Therefore, when the tightening nut 36 is loosened to adjust the rotation of the fitting part 32 within the fitting hole 34, since the fitting part 32 is eccentric with respect to the support shaft 20, the upper blade 30 is rotated in the vertical direction. The engagement amount δ1 between the upper blade 30 and the lower blade 31 is adjusted. A hole 3 is provided in the horizontal portion 33b of the frame 33.
7 is formed so that its axis is perpendicular to the axis of the support shaft 20, and this hole 37f1C. The lower end of a frame holding shaft 38, which is vertically installed on a round blade tool body (not shown), is fitted through a bearing 39, and the frame 33
is designed to be able to swing around this frame holding shaft 38.

Therefore, when replacing the upper blade 30, the frame 33
can be rotated to separate the upper blade 30 from the lower blade 31,
Furthermore, when the upper blade 30 is used with the opposite hand, the position of the upper blade 30 can be changed simply by rotating the frame 33 1800 turns. Further, one end flange portion 20 of the support shaft 20
A coil spring 40 is interposed between a and the sleeper 21. This coil spring 40 presses the sleeve 21 and maintains the state of contact between the clay blade 30 and the lower blade 31. Furthermore, on the other end side of the support shaft 20,
A sleep-shaped positioning knob 41 for positioning the upper blade 30 in the axial direction is inserted. A guide groove 42 is formed on the outer circumferential surface of the positioning knob 41, and a pin 43 protruding from the outer circumferential surface of the support shaft 20 is engaged with the guide groove 42. When the pin 43 engages with the one end engaging portion 42aVc of the guide groove 42,
(See FIG. 7) The upper blade 30 is moved to the other end of the shaft 20 (supported by the positioning knob 41) and the lower blade 31VC is moved by the elastic force of the coil spring 40. Even if the positional error in the axial direction is large, contact is made with appropriate contact pressure.

Therefore, the workpiece fed between the upper blade 30 and the lower blade 31 is reliably sheared. Note that when the pin 43 engages with the other end engaging portion 42bVC of the guide groove 42, the positioning knob 41 moves toward one end of the support shaft 20, and the upper blade 30 separates from the lower blade 31. In the figure, 44 is a lever piece fixed to the tightening nut 36.

Next, a case will be described in which the above-mentioned apparatus is used to shear various types of material such as paper.

First, after lowering the lever piece 44 and loosening the tightening nut 36, the support shaft 20 is rotated to move the upper blade 30 to the uppermost position.
Then, tighten the tightening nut 36 again to fix the support shaft 20.

Next, the positioning knob 41 is rotated relative to the support shaft 20 to engage the pin 43 with the other end engaging portion 42b of the guide groove 42, thereby moving the upper blade 30 toward one end of the support shaft 20.
Thereafter, the frame 33 is attached via a bearing 39 to the lower end of a frame holding shaft 38 vertically disposed on a round-blade tool body (not shown), and the upper blade 30 is opposed to the lower blade 31. (At this time, the distance between the upper blade 30 and the lower blade 31 is approximately 5 mm.) After the upper blade 30 is opposed to the lower blade 31 in this way, the lever piece 44 is pushed down and the tightening nut 36 is loosened. , by rotating the support shaft 20 and moving the upper blade 30 in the vertical direction.
0 and the lower blade 31 is adjusted, and the tightening nut 36 is tightened again to fix the support shaft 20. Thereafter, the positioning knob 41 is rotated relative to the support shaft 20 to remove the pin 43 from the other end engaging portion 42b of the guide groove 42 and engage the one end engaging portion 42aVc. Then, the upper blade 30 moves toward the lower blade 31 due to the elastic force of the coil spring 40 and comes into contact with the lower blade 31 with appropriate contact pressure. At this time, the upper blade 30
Even if the side surface of the upper blade 30 is not parallel to the side surface of the lower blade 31, the frame 33 rotates due to the elastic force of the coil spring 40, so that the side surface of the upper blade 30 becomes parallel to the side surface of the lower blade 31. In other words, when the lower blade 31VC side shake occurs and the upper blade 30 and the lower blade 31 come into contact at a position deviated from the line connecting their centers in the direction of the front and back of the paper in FIG. There is a difference in the pressing force exerted by the coil spring 40VC on the rear side and the rear side. This difference in pressing force creates a moment that rotates the upper blade 30 around the contact point, and this moment causes the frame 33 to rotate, so that the upper blade 30 becomes parallel to the lower blade 31. Therefore, without having to adjust the side surface of the upper blade 30 parallel to the side surface of the lower blade 31, the parallel alignment is automatically performed simply by bringing the upper blade 30 into contact with the lower blade 31. . After setting the upper blade 30 as described above, the motor is driven to rotate the soil blade 30 and the lower blade 31 while bringing them into contact with each other, and feed the workpiece between the upper blade 30 and the lower blade 31. Then perform shearing.

During the above-mentioned shearing process, even if the lower blade 31 causes lateral vibration, the upper blade 30 can be elastically displaced by the cushion ring 28, and in addition to this, the support shaft 20 supporting the upper blade 30 can be moved within the same plane. Rotate and further coil spring 4
0, the upper blade 30 can be largely elastically displaced in the axial direction by compensating for the insufficient movement of the direction ring 28.
0 can sufficiently follow the lower blade 31VC, and the lower blade 31
It is possible to follow even when the side runout is very large.

Furthermore, even if the upper blade 30 approaches and separates from the lower blade 31VC, the upper blade 30 makes surface contact with the lower blade 31.
Therefore, there is no danger of the cutting edge breaking, and the life of the upper blade 30 is extended. In addition, as shown in the above embodiment, when the supporting shaft 20VC fitting part 32 is provided eccentrically and protrudingly, the amount of engagement δ1 between the upper blade 30 and the lower blade 31 can be easily adjusted. This is convenient when the upper blade 30 and the lower blade 31 are worn out and their diameter becomes small.

As explained above, according to the round blade tool of the present invention, the support shaft is fixed to a frame rotatably provided around an axis substantially perpendicular to the axis of the support shaft, and the support shaft A holder is inserted rotatably and movably in the axial direction, and an upper blade is inserted into a mounting recess formed along the circumferential direction on the outer periphery of the holder, and between this upper blade and each side wall surface of the mounting recess. They are attached so that they can be elastically displaced in the axial direction of the support shaft and tilted with respect to this axis via the respective elastic bodies, and the holder is further biased to the support shaft to bring the upper blade into contact with the lower blade. Since the elastic member is attached, the upper blade can sufficiently follow the lower blade even when the side runout of the lower blade is small or large. Also, since the support shaft rotates in the same plane as the frame rotates, the upper blade can be aligned parallel to the lower blade, so the upper and lower blades are not parallel to each other. No damage to the cutting edge occurs. Therefore, the life of the upper blade is significantly improved compared to conventional ones, and the frequency of replacing the upper blade is thereby reduced, making it possible to improve the efficiency of shearing work. Furthermore, the mounting position of the upper blade in the axial direction can be adjusted using the positioning member (positioning knob) Vc, and the contact pressure of the upper blade with respect to the lower blade can be set to an appropriate value. Therefore, the workpiece can be sheared smoothly, and no shearing defects occur.

[Brief explanation of the drawing]

Figure 1 is a schematic configuration diagram of a conventional device, Figures 2 and 3 are explanatory diagrams for explaining the state in which the upper blade and lower blade are in contact with and away from each other, and Figure 4 is the same as Figure 1. 5 and 6 are explanatory diagrams for explaining the state of contact and separation between the soil blade and the lower blade in the device shown in FIG. 4, FIG. 7 is a partially sectional side view showing an embodiment of the present invention, and FIG. 8 is a plan view thereof. 20...Support shaft, 22...Holder, 2
7...Mounting recess, 28...Elastic body (cushion ring), 30...Upper blade, 31...
...Lower blade, 33...Frame, 38...
... Frame holding shaft, 40 ... Elastic member (coil spring), 41 ... Positioning member (positioning knob).

Claims (1)

[Claims] 1. A round-blade tool equipped with an upper blade attached to the outer periphery of a support shaft, and a lower blade that is rotationally driven with the outer periphery of one side in contact with the outer periphery of one side of the upper blade. The shaft is fixed to a frame rotatably provided around an axis substantially orthogonal to the axis of the support shaft, a holder is rotatably and movably movable in the axial direction attached to the support shaft, and the outer circumference of the holder is The upper blade is attached to a mounting recess formed along the circumferential direction of the support shaft in the axial direction of the support shaft via elastic bodies provided between the upper blade and each side wall surface of the mounting recess. The holder is mounted so as to be elastically displaceable so as to be inclined with respect to the axis, and an elastic member is further mounted on the support shaft to urge the holder and bring the upper blade into contact with the lower blade. Round blade tool.