JP2001105229A - Disc rotating device and its control method, and circular saw device using it - Google Patents

Abstract

PROBLEM TO BE SOLVED: To provide a disc rotating device for ensuring stability of a thin disc, when rotated at a high speed, without requiring experience and perception for saw levelling. SOLUTION: For a disc rotating device, a mounting hole 4 is formed in the center of a thin disc 2 and passed through a rotation supporting shaft 11 for rotating the disc 2 with the rotation of the rotation supporting shaft 11 Stress generating means 17, 19, 20 are provided between the inner periphery of the mounting hole 4 and the rotation supporting shaft 11 for generating stress in the disc 2 by giving a load F (in inner pressure Pi) to the disc 2 in the direction of the outer periphery thereof.

Description

DETAILED DESCRIPTION OF THE INVENTION

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a disk rotating apparatus which suppresses vibration (lateral vibration) in the thickness direction of a disk by changing the tension of the disk made of a thin steel plate or the like due to stress. The present invention relates to a method and a circular saw device using the same.

[0002]

2. Description of the Related Art Circular saws have been widely used for cutting wood, and more recently, for cutting metal materials and gypsum materials for construction. The circular saw has a structure in which a peripheral edge of a base metal 2 made of a circular thin steel plate (a disk-shaped steel plate) is cut off, and a sharp tip portion is used as a blade, or a chip of a tool material is brazed. Is also used as a cutting blade. The circular saw is mounted on a rotating shaft and rotated to be used as a cutting tool.

In recent years, a high-speed cutting technique of a metal material member using a circular saw (tip saw) has played an important role in many industrial fields such as the automobile industry. In high-speed cutting using a circular saw in recent years, cutting speeds used in ordinary machining, such as turning and milling, are 1 to 10
Cutting speeds of about 20 to 80 m / sec, far exceeding m / sec, are becoming commonplace.

[0004] The circular saw technology for realizing such high-speed cutting is supported by both the technology relating to the blade edge device and the technology relating to the insertion of a base metal called a master plate.

For example, in order to perform high-speed cutting using a circular saw having a low rigidity structure, dynamic stability derived from vibration in the thickness direction when the circular saw is rotated at a high speed plays the most important role. This improvement is required.

When a circular saw that has not been subjected to the waist-in process is used for high-speed cutting as it is, as the rotational speed of the circular saw is increased, the base metal becomes thinner, and the peripheral part of the base metal vibrates in the thickness direction. Its dynamic stability is reduced and becomes unstable, so that no cutting can be performed at all.

[0007] On the other hand, in a circular saw that has been subjected to an appropriate squatting process, it is known that the dynamic stability of the circular saw is maintained even when the number of revolutions is increased, thereby dramatically extending the life of the device. Have been. Here, in this waist-in process, a residual stress is generated by subjecting the parent plate to a small plastic working with a press or the like. This stress results in high-speed stability of the parent plate, and as a result, high-speed and high-precision cutting process in the production line,
Cost reduction can be realized.

[0008] This squatting process can be compared with that corresponding to the air pressure of an automobile tire. In an automobile, if the vehicle runs at high speed with insufficient air pressure, the tires resonate and puncture. However, if the air pressure is sufficiently increased, comfortable traveling becomes possible even at high speed traveling. Even in a circular saw, a stable high-speed rotation state can be maintained if a force for spreading the entire master plate is left so as to increase the air pressure of the tire.

As shown in FIG. 1, this squat-in process is performed by pressing a base 2 of a rotating circular saw 1 at a desired position (a stress generating area 2a indicated by oblique lines) with a pair of rollers 3 and 3 vertically. External force to give permanent distortion inside.
The base metal 2 is further subjected to hammering, if desired, so that residual stress is generated in the radial direction σr and the circumferential direction σt (see FIG. 2).

The dynamic stability of the circular saw 1 is caused by the application of residual stresses such as the radial direction σr and the circumferential direction σt inside the circular saw due to squatting and an increase in the critical rotation speed due to the application of the residual stress. It is explained that it is.

Here, the critical rotation speed is defined as follows. That is, the natural vibration (lateral vibration) with respect to the rotation plane at the coordinates fixed to the disk is observed as two vibrations of a forward wave and a backward wave by an observer fixed in space. The natural frequency of this backward wave decreases as the rotation speed of the disk increases, but when the natural frequency becomes zero, the rotation of the disk and the natural vibration resonate in synchronization, and this rotation speed becomes critical. It is defined as the number of revolutions.

The critical rotation speed differs depending on the vibration mode, and the smallest critical rotation speed becomes the critical rotation speed, and this critical rotation speed generally matches the critical rotation speed in the vibration mode (0, 2). . The rotation becomes unstable in the rotation speed region higher than the critical rotation speed.

[0013]

However, such a squatting process, which has been performed for a relatively long time, still depends on the experience of a skilled technician. Only the skilled worker can engage in the lowering process. Moreover, even this skilled worker requires 30 minutes to 1 hour per circular saw. Therefore, the cost of this process is about 20% of the total cost of the circular saw.
And automation seems technically quite difficult.

[0014] In addition, although it takes about three years of experience to perform this squatting process, it is an operation that requires much patience because it is almost a manual operation, and has hindered training in recent years.

An object of the present invention is to provide a disk rotating device which can secure the stability of a thin disk even if the thin disk is rotated at a high speed, instead of squatting based on experience and intuition. is there.

[0016]

According to the first aspect of the present invention, a mounting hole is formed at the center of a thin disk, and the mounting hole is inserted into a rotating shaft to rotate the rotating shaft. In a disk rotating device for rotating the disk, the disk has a stress generating means for directly or indirectly receiving a load to generate stress on the disk. is there.

According to this structure, since the disk has the stress generating means for directly or indirectly receiving a load to generate stress on the disk, the disk can be inserted into the disk which has not been subjected to the stiffening process. The same stress is generated. If the disk is rotated in a state where the stress is generated, even if the thin disk which has not been subjected to the waist-in process is rotated at a high speed, the disk is subjected to the stress generated by the stress generating means. , The natural frequency of the disk can be increased, and the critical rotation speed of the thin disk can be increased.

According to a second aspect of the present invention, the stress generating means comprises a thin annular cylindrical portion containing a pressure medium annularly interposed between the inner periphery of the mounting hole and the outer periphery of the rotary support shaft. The disk rotation device according to claim 1, wherein the rotation support shaft has sufficient hardness to support the annular cylindrical portion from an inner surface.

According to this structure, a uniform load can be applied from the thin annular cylindrical portion to the outer circumference over the entire inner circumference of the mounting hole of the disk by the action of the pressure medium. Thereby, a stress against this load can be generated in the disk.

According to a third aspect of the present invention, the stress generating means is perpendicular to the plane direction of the disk interposed between the inner periphery of the mounting hole and the outer periphery of the rotation support shaft, and is provided on the disk. And a press-fitting means for press-fitting the inclined annular member between the disk and the rotating shaft. A disk rotating device according to claim 1.

According to this structure, the disk rotating device according to the first aspect of the present invention press-fits the inclined annular member between the inner periphery of the mounting hole of the disk and the rotation support shaft, so that the disk is rotated. A load is applied from the periphery to the outer periphery, and stress against the load is generated on the disk.

According to a fourth aspect of the present invention, the stress generating means includes an inclined surface which is orthogonal to a plane direction of the disk fixed to the rotation support shaft and whose radius gradually decreases toward the disk. The disk rotating device according to claim 1, wherein the rotating device comprises a slanted annular portion provided.

According to this structure, the disk rotating device according to the first aspect press-fits the inner periphery of the mounting hole of the disk toward the inclined annular portion, whereby the disk moves from the inner periphery to the outer periphery. The applied load causes a stress against the load.

According to a fifth aspect of the present invention, the stress generating means is formed by an elastically deformable member having a mountain-shaped cross section of a flange portion interposed between the inner periphery of the mounting hole and the outer periphery of the rotary support shaft. 2. The ring-shaped chevron member according to claim 1, further comprising: a load generating means for generating a load toward a top portion or a skirt portion of the ring-shaped chevron member and deforming the ring-shaped chevron member. It is a disk rotating device.

According to this structure, in the disk rotating device according to the first aspect, a compressive load for deforming the annular chevron with the top or bottom of the annular chevron as a fulcrum is applied by the load generating means, and the annular chevron is formed. The member is expanded in diameter by elastic deformation. As a result, the load applied parallel to the rotation axis is converted into a radial direction orthogonal to the rotation support axis, and the load can be applied from the inner circumference to the outer circumference of the disk. According to this load direction changing means, since a load parallel to the rotating shaft can be applied to generate a stress on the disk, fine adjustment of the stress becomes easy. Further, thereby, it is possible to provide a disk rotating device that applies a load from the inner circumference to the outer circumference of the disk without largely changing the specifications of the disk and the disk rotating device.

6. The disk rotating device according to claim 5, wherein said load generating means is supported so as to be able to apply a compressive load toward a vertex or a skirt of said annular chevron, and said outer periphery of said annular chevron is compressed by said compression. The disk rotating device according to claim 5, wherein the diameter is increased by receiving the load, and the load is applied toward the inner periphery of the disk.

According to this structure, the disk rotating device according to claim 5 can apply a load from the inner circumference to the outer circumference of the disk by mechanical means and with a configuration having a small frictional portion. . This makes it possible to finely increase or decrease the internal pressure, further increasing the practicality.

The invention according to claim 6 is the disk rotating device according to claim 5, wherein the annular angled member comprises a pair of annular disc springs formed of a spring steel material formed in an angled shape.

With this configuration, in the disk rotating device according to the fifth aspect, it is easy to obtain the annular chevron member as the stress converting means.

According to a seventh aspect of the present invention, the load generating means includes a deformable portion formed on the rotating disk and deformed in a direction orthogonal to a plane direction of the rotating disk. Item 10. A disk rotating device according to Item 1.

According to this structure, by applying a compressive stress in the axial direction of the disk toward the deformed portion, the deformed portion is expanded in diameter and generates the same stress as when the disk is inserted. Can be. Such a configuration is integral with the disk and the configuration is simplified. Such a deformed portion can be obtained by press-forming a disk.

According to an eighth aspect of the present invention, the stress generating means includes a load direction converting means for converting the load in the direction of the rotating shaft into a load in an outer circumferential direction orthogonal to the rotating shaft, and the stress generating means is directed to the load direction converting means. 2. The disk rotating device according to claim 1, further comprising: a load generating unit configured to generate a load in a direction of a rotating shaft.

With this configuration, the disk rotating device according to the first aspect of the invention can generate a desired stress on the disk by applying a load in the axial direction, so that the adjusting operation is easy. Such a stress generating means may be integrated with the disk, or may be provided independently of the disk. If it is integrated with the disk, the configuration is simplified, and if it is independent of the disk, fine adjustment of the stress becomes easy.

According to a ninth aspect of the present invention, the load direction changing means is based on a pressure medium interposed between an inner periphery of a mounting hole of the rotary disk and the rotary support shaft. 8. A disk rotating device according to item 8.

With this configuration, in the disk rotating device according to the eighth aspect, the generation of the desired stress on the disk can be easily adjusted by changing the pressure of the pressure medium.

According to a tenth aspect of the present invention, the load direction changing means is based on press-fitting of an inclined member interposed between an inner periphery of a mounting hole of the rotating disk and the rotation support shaft. A disk rotating device according to claim 8.

With this configuration, in the disk rotating device according to the eighth aspect, the desired stress can be generated on the disk by press-fitting the inclined member.

According to an eleventh aspect of the present invention, in the disk rotating device according to the eighth aspect, the load direction changing means is based on a deformation of the elastic member caused by a compressive load applied to the elastic member. is there.

According to this structure, in the disk rotating device according to the eighth aspect, the desired stress on the disk can be generated by the compressive load on the elastic member.

According to a twelfth aspect of the present invention, in the disk rotating device according to the eighth aspect, the load generating means is based on a single screwing mechanism.

According to this structure, the disk rotating device according to the eighth aspect can generate a desired stress on the disk by a single screwing mechanism, so that the operation is simple and the device is simple. Is simplified.

According to a thirteenth aspect of the present invention, the load generating means is based on a plurality of screwing mechanisms arranged at equal intervals in a circumferential direction of the rotating disk. It is a rotating device.

With this configuration, in the disk rotating device according to the eighth aspect, a desired stress on the disk can be generated by a plurality of screwing mechanisms, and fine adjustment can be performed. Further, the stress applied to the disk can be increased.

According to a fourteenth aspect of the present invention, in the disk rotating device according to the first aspect, the stress generating means can be controlled according to an operation state of the disk rotating device. .

According to this structure, in the disk rotating device according to the first aspect, since the stress generating means can be controlled according to the operating state of the disk rotating device, the optimum stress can be controlled according to the operating state. Can be generated on the disk.

According to a fifteenth aspect of the present invention, using the disk rotating device according to the fourteenth aspect, the stress generation of the stress generating means is increased as the rotational speed of the disk rotating device is increased. A method for controlling a disk rotating device characterized by the following.

With this configuration, when the disk is rotated at a low speed, such as at the start of rotation or at the end of rotation, no stress is generated, or the disk rotates smoothly due to small stress, and the rotation speed is reduced. By increasing the amount of stress generated in accordance with the rise of the rotation speed, the motor can be smoothly rotated even at high speed rotation.

According to a sixteenth aspect of the present invention, the disk rotating device is applied to a circular saw, a disk brake, and a hard disk. It is a rotating device.

According to this structure, the disk rotating device according to any one of claims 1 to 13 can stabilize the high-speed rotation of the disk by generating stress on the disk. Since it can be used, it can be applied to rotating devices such as circular saws, disk breaks, and hard disks that require high-speed rotation.

According to a seventeenth aspect of the present invention, a mounting hole is formed at the center of a thin base metal, the mounting hole is inserted into a rotation support shaft, and the rotation support shaft is rotated to thereby fix the base metal. In the circular saw device to be rotated, a slit is provided radially outward on the periphery of the mounting hole as the base, and between the inner circumference of the mounting hole and the rotation support shaft, in the outer circumferential direction of the base. A circular saw device provided with a stress generating means for generating a stress at a peripheral portion of the base metal by applying a load toward the circular saw.

According to this structure, although a stress is generated in the disk due to the load from the inner periphery to the outer periphery, the slits are provided radially toward the outer periphery at the periphery of the attachment hole, so that the periphery of the attachment hole is provided. Then, the generated circumferential stress is released by the slit. Thereby, the stress in the circumferential direction at the outer peripheral edge portion is relatively increased.

The invention according to claim 18 is the circular saw according to claim 17, wherein the stress generating means is the stress generating means according to any one of claims 2 to 13. Device.

According to this structure, the stress generating means according to any one of claims 2 to 13 can be applied to the circular saw device according to claim 17.

[0054]

DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENTS Hereinafter, a disc rotating device 1 applicable to a circular saw device according to a specific embodiment 1 of the present invention will be described.
0 will be described with reference to the drawings.

This disk rotating device has an HRC hardness of about 38 used for a general circular saw as shown in FIG.
It is a circular thin steel plate (disc) 2 that has been quenched so as to be ~ 45. This peripheral edge is cut off and its sharp tip is used as a blade, or a chip of a tool material is brazed and used as a cutting blade to be used as a circular saw.

A mounting hole 4 is provided at the center of the disk 2, and a rotating support shaft 11 penetrates the mounting hole 4 as shown in FIGS. 3 and 4. Both sides of the disk 2 are held on contact surfaces 12a, 13a of a pair of flanges 12, 13.

One flange 12 has a groove 12 near the center.
b is formed. The other flange 13 has an annular projection 14 fitted with play in the groove 12b.
And a holding portion 16 for holding the disk 2. The protrusion 14 has an annular pressure medium storage space 17, and the periphery of the pressure medium storage space 17 is joined by welding 15 a, 15 b or the like.
Further, a thin portion 20 is formed along the outer periphery of the pressure medium storage space 17, and an outer peripheral surface 14 a of the thin portion 20 is a contact surface with which the inner peripheral surface 4 a of the disk 2 contacts.

As shown in FIG. 5, the mounting hole 4 is inserted into the outer peripheral surface 14a of the projection 14, and the projection 14 is fitted into the groove 12b. 2 and the flange 12 is fixed by an appropriate fixing means such as a lock nut N. As a result, the disk 2 is fixed to the rotating shaft 11 while being held by the flanges 12 and 13, and is rotated by a drive motor (not shown) housed in the main body case H to form a disk rotating device.

The pressure medium storage space 17 is
A pressure screw 19 is screwed into a screw hole of the shaft hole, and a sealing shaft 18 is slidably sealed in an intermediate portion of the shaft hole. Have been.

With this configuration, when the pressure screw 19 is tightened, the pressure medium in the pressure medium storage space 17 is compressed, and the thin portion 20 expands. As a result, as shown in FIG. 6A, a load F (internal pressure Pi) from the inner peripheral surface 4a of the mounting hole 4 to the outer periphery is given, and a stress σ ( σr, σt) occur. At this time, the radial stress σr is such that the compressive stress is gradually reduced from the inner circumference to the outer circumference, and the circumferential stress σr is
At t, the tensile stress is gradually reduced from the inner circumference to the outer circumference. If the disk 2 is rotated in a state where the stress σ is generated, the stress is generated in the disk 2 even if the thin disk 2 not subjected to the waist-in process is rotated at a high speed. ,
The natural frequency NF of the disk 2 can be increased,
Therefore, the critical rotation speed of the disk 2 can be increased.

Here, as shown in FIG. 6B, if the inner diameter d4 is made larger, the stress distribution acts more on the outer peripheral portion. This stress distribution is represented by a disk 2 having a small inner diameter (FIG. 6A).
), The stress distribution becomes closer to that of the base metal that has been subjected to the squatting process, whereby the critical rotation speed of the disk 2 can be further increased.

Further, even when the disk 2 having a small inner diameter d4 is used, as shown in FIG. 7, slits 41 and 42 are provided radially near the inner diameter. These radial slits 4
Since Nos. 1 and 42 are not provided on the outer peripheral edge, only the circumferential stress σr near the inner circumference is released, and the same effect as when the inner diameter is widened is expected. Here, FIG.
The slit 41 shown in (a) is open in the mounting hole 4, but the slit 42 shown in FIG. 7 (b) is provided independently on the disk 2. Similar effects are expected in both cases.

Hereinafter, the effects of the present invention will be specifically described with reference to specific examples. [Example 1] [Calculation of stress] As the disk 2, an outer diameter of 560 mm and an inner diameter of 10
A circular steel plate having a thickness of 0 mm and a thickness of 2.6 mm was assumed. This steel sheet is quenched and has a hardness of 38 to 43. This steel plate is a base metal suitable for use in cutting metal or the like by brazing a hard tip as a cutting edge and performing an appropriate crimping treatment.

Next, assuming the apparatus shown in FIG. 3, the stress σ at the position of the radius r (the stress σr in the radial direction and the stress σt in the circumferential direction) can be obtained by the following equation.

[0065]

(Equation 1)

Here, Pi is the distance between the flange 13 and the disc 2.
The applied internal pressure, a is the outer radius of the disk, and b is the inner radius of the mounting hole 4.

FIG. 8 shows the calculation results. from this result,
In the radial stress σr of the disk 2, the compressive stress is gradually reduced from the inner circumference to the outer circumference, and the circumferential stress σt is
The tensile stress is gradually reduced from the inner circumference toward the outer circumference. If the disk is rotated in a state in which the stress σ is generated, even if a thin disk that has not been subjected to the waist-in process is rotated at a high speed, the disk is subjected to stress. The natural frequency NF of the plate can be increased, and therefore, the critical rotation speed of the disk can be increased.

On the other hand, assuming a circular saw having the same dimensions and quenched and stiffened, the stress distribution generated in the disc as a Gaussian distribution function is used as the isotropic additional stress used for calculating the residual stress of the stiffened disc. FIG. 9 shows the result of the calculation. The tendency of the stress in the vicinity of the outer periphery outside the range of about 60 to 70% (outside the vicinity of the radius of 0.2 m) with respect to the entire outer diameter was similar to the calculated value of the stress distribution according to the first embodiment. [Calculation of Natural Frequency NF] Using the same disk used in the measurement of stress, the internal pressure and the natural frequency N in each vibration mode
The relationship of F was obtained by calculation using the energy method that the maximum value of the kinetic energy during vibration was equal to the maximum value of the work energy, and the results are shown in FIG.

From FIG. 10, it was confirmed that, in the vibration mode larger than the mode (0, 2), the natural frequency NF is increased by increasing the internal pressure.

On the other hand, it is known that the dangerous rotation speed is increased by increasing the natural frequency NF. Therefore, in the vibration mode larger than the mode (0, 2), the dangerous rotation speed is increased. It is understood that the number is increased (for example, Transactions of the Japan Society of Mechanical Engineers (C), Vol. 58, No. 54)
7, No. 7 (1992-3), pp. 684-689. ). Example 2 As the disk 2, a circular steel plate having an outer diameter of 304 mm, an inner diameter of a mounting hole of 38 mm, and a thickness of 2.6 mm was used. This steel sheet is quenched and has a hardness of 43. This steel plate is a base metal suitable for use in cutting metal or the like by brazing a hard tip as a cutting edge and performing an appropriate crimping treatment.

Using the natural frequency measuring device shown in FIG. 11, the change in the natural frequency NF when the pressure applied from the inside was changed was determined. In this device, the disk 2 is fixed by a pair of flanges 12 and 13, and the disk 2 receives stress from the flanges 12 and 13 and receives an internal pressure by hydraulic pressure to generate stress.

In the state where the stress is generated, the outer peripheral portion of the disk 2 is hit with an impulse hammer to detect the vibration displacement. The displacement sensor is connected to an FFT analyzer via an amplifier, and the natural frequency NF is obtained by performing frequency analysis with the FFT analyzer. The results of plotting are shown in FIG. 12, and the relationship between the natural frequency NF and the pressure is shown in Table 1. FIG. 13 shows the results together with separately calculated values.

[0073]

[Table 1]

FIG. 13 shows that the natural frequency NF was increased by increasing the internal pressure in any of the vibration modes (0, 2) and (0, 3). It was confirmed that they matched well.

With this configuration, the natural frequency NF of the disk is increased by a simple structure in which a load is applied from the inner diameter to the outer diameter of the rotating disk, and as a result, the same effect as that of a seat can be obtained. Was confirmed. As a result, the tensioning adjustment at the time of re-polishing of the circular saw, which has been impossible so far, can be performed by anyone without requiring skill.

[0076]

Second Embodiment In the first embodiment described above, the disk 2 receives a hydraulic pressure from the flange 13 to generate stress distortion. As long as a load is applied from the inner diameter to the outer diameter while the plate is rotating, any means may be used as long as a stress is generated, and various modifications are conceivable.

Hereinafter, a modification will be described as a second embodiment of the present invention. Parts and members that are the same as or equivalent to those of the first embodiment will be described with the same reference numerals. [Modification 1] In the disk rotating device of Modification 1, FIG.
As shown in FIG.
3 are held on the contact surfaces 112a and 113a. The pressure medium storage space 17 is formed on the protrusion 114 of the flange 112, and the outer periphery of the pressure medium storage space 17 has a thin wall 2.
0 is formed. The pressure medium storage space 17
A through hole 115 is formed with the protrusion 114 facing the core shaft 11, and a hole 111 that receives the through hole 115 and communicates with the pressure medium storage space 17 is formed in the main body case H (not shown). ). Flange 113
The joint surface between the shaft 11 and the shaft 11 is connected by welding 11a, 11b or the like. The hole 111 is provided in the main body case H
It is connected to a pressure adjusting mechanism that adjusts the pressure of the pressure medium stored in (not shown).

According to this structure, by providing the pressure medium control section for controlling the pressure of the pressure medium in the main body case H, it is possible to control the pressure of the pressure medium even during the rotation of the disk. Thereby, the thin portion 20 is formed.
, The load F applied to the disk 2 can be freely controlled. Thereby, the pressure of the pressure medium can be controlled according to the operation state such as the rotation speed of the disk 2 or the cutting state as a circular saw, so that an optimum stress is generated in the disk 2 according to the operation state. it can.

In particular, as the rotational speed of the disk 2 is increased, it is generally considered advantageous that the amount of squatting applied to the disk is larger. However, if the amount of stiffening is too large, trouble at low speed rotation is hindered. May occur. According to the rotating disk device provided with such a control device, as the rotation speed is increased, an optimum stress according to the rotation speed can be generated. In addition, it is possible to always rotate stably. As a result, when rotating at a low speed, such as at the start of rotation or at the end of rotation,
The disk is smoothly rotated by generating no stress or small stress, and by increasing the stress as the rotation speed increases, the disk can be smoothly rotated even at high speed rotation. [Modification 2] In the disk rotating device of Modification 2, FIG.
As shown in FIG. 7, instead of the disk 2, a disk 202 in which the radius of the mounting hole is gradually reduced and the inner surface 204a is slightly inclined is used. The disk 202 is provided with a pair of flanges 212, 2
13 are held on the contact surfaces 212a and 213a. One of the flanges 212 has an annular groove 212b on the inner surface, and the other flange 213 has a protrusion 214 fitted into the groove 212b with play. This projection 21
4 has an inclined surface 2 along the inner surface 204a which is gradually reduced in radius toward the flange 212 and inclined toward the core shaft 11 side.
14a. In the state shown, the flange 21
When the disc 2 is urged in the direction of arrow a, the disc 202 is pressed against the contact surface 212 a of the flange 212. As a result, the inner surface 204a becomes inclined surface 214 as it moves in the direction of arrow a.
a, and a load F (internal pressure Pi) is radially applied from the inner circumference to the outer circumference of the disk 202.

As a result, a stress is generated in the same manner as when the disk 202 is seated, and the critical rotation speed is increased. Further, such a stress generating means has an advantage that it can be manufactured at a lower cost as compared with a device for sealing a pressure medium. [Modification 3] In the disk rotating device of Modification 3, FIG.
6. As shown in FIG. 17, the disc 2 is
12 and 313 are held on the contact surfaces 312a and 313a. Both flanges 312, 313 have annular grooves 312b, 313b on the inner surface.
Eight screw grooves 313c are provided at equal intervals in the circumferential direction. Inside slope 317b and outside slope 318a
Are joined to each other so that the outer peripheral surface 3
A pair of annular press-fitting members 317, 318, whose inner peripheral surfaces 318b and 17a are parallel, are provided with a plurality of adjusting screws 3 in this groove 313b.
19 are screwed into the screw groove 313c and fixed. As shown in FIG. 17, the outer press-fitting member 317 is provided with a notch 317c at an appropriate position.

According to such a configuration, the adjusting screw 319
Is screwed into the inner press-fitting member 318 to expand the outer press-fitting member 317. This allows
The outer peripheral surface 317a of the outer press-fitting member 317 pushes up the inner surface 4a of the disk 2 to apply a radial load F to the disk 2. As a result, the same stress is generated in the disk 2 as when the disk 2 is subjected to the waist-in process, and the critical rotation speed of the disk 2 can be increased. The generation of stress using such a gradient
There is an advantage that it can be manufactured at low cost as in the second modification. [Modification 4] In the disk rotating device of Modification 4, FIG.
As shown in the figure, the disk 2 has a pair of inner and outer flanges 412,
413 are held on contact surfaces 412a and 413a.
Each of the flanges 412 and 413 has a recess, and an annular stress generating means 40 is fixed to the recess by four pairs of bolts (not shown).

This stress generating means 40 is shown in FIGS.
As shown in FIG. 5, an annular chevron member 41 formed from an annular spring steel material and provided with a crest 41a at its annular center portion, and a pair of annular holding members 42 for holding the annular chevron member 41 from both sides and holding the same. 43 and a pressing member 44 provided with a male screw portion 441 for pressing these members 41 to 43
And an adjusting nut 45.

As shown in FIG. 20, the annular chevron member 41 is formed by forming a pair of annular coned disc springs having different directions in a chevron shape.
and an outer peripheral side surface 41b and an inner peripheral side surface 41c which are parallel to each other, and twelve insertion holes 411 for inserting the male screw portion 441 along the crest portion 41a. Also,
The outer diameter of the outer peripheral surface 41b of the annular chevron 41 is
Is designed to be equal to the inner diameter of the inner peripheral surface 4a.

As shown in FIG. 21, one annular holding member 42 has an abutting surface 42a in contact with a ridge 41a of the annular chevron member as an annular projection, and the abutting surface 42a
Are provided with twelve insertion holes 421 arranged corresponding to the insertion holes 411 and four female screw portions 4 annularly arranged at equal intervals.
22. Here, the female screw portion 422 is
This is for fixing the outer flange 412 with four bolts not shown in FIG.

Further, the other annular holding member 43 is
As shown in FIG. 12, twelve insertion holes 431 for similarly inserting the male screw portions 441 at positions corresponding to the insertion holes 421, and an annular support provided on the inner surface side as an annular projection on the inner peripheral side of the insertion hole 431. Surface 43a. The annular support surface 43a is provided on the inner peripheral surface 41c of the annular
It is supported from the side.

As a result, the annular angled member 41 inserts the male screw portion 441 inserted into the insertion hole 431 into the insertion hole 411 and further through the insertion hole 422 of the annular holding member 42 to thereby form a pair of annular holding members 42. , 43, and the adjustment nut 45 is screwed into the male screw portion 441 (FIG. 19). Also, at this time, the outer peripheral surface 41b has
As shown in FIG. 8, the inner peripheral surface 4a of the disk 2 is fitted, and the disk 2 is brought into contact with the contact surface 412 of the pair of flanges 412, 413.
a, 413a.

When the adjusting nut 45 is tightened, the contact surface 42a comes into contact with the peak 41a (FIG. 2).
2). When the adjusting nut 45 is further tightened to apply a load in the axial direction in parallel, the outer peripheral surface 41b and the inner peripheral surface 41c which are both ends (both hem) of the annular chevron member 41 are strong against the inner peripheral surface 43b of the annular holding member 43. The annular chevron 41 is abutted and deformed to be crushed by the compressive load.

Here, since the annular chevron member 41 is formed of a spring steel material, the vicinity of the crest 41 is deformed toward the inner peripheral surface 43b of the annular holding member.
As the height of the crest of the annular chevron member 41 decreases, the width of the annular chevron member 41 increases (diameter expansion), and an urging force acts on the support surface 43a and the inner peripheral surface 4a. This urging force acts like a link due to the shape of the annular chevron 41, and the urging force can be increased by a boosting mechanism (a boosting mechanism).

The urging force directed to the support surface 43a is cooperated with the annular holding member 43 itself or the support shaft 11 to form the annular chevron member 4.
Support 1 and fix. On the other hand, the urging force (load F) toward the inner peripheral surface 4a acts on the disk 2 as an internal pressure Pi. By adjusting the screwing strength of the nut 45, either the increase or decrease of the internal pressure Pi can be adjusted.

By changing the tightening position of the adjusting nut 45, the circumferential strength distribution of the internal pressure Pi applied in the circumferential direction can be adjusted.

The adjustment of the load is smaller than that in the case of using the inclined disk 202 of the second modification, so that the fine adjustment can be performed more easily because the frictional portion is small, and the mounting and dismounting become easier.

As a result, a stress is generated in the same manner as when the disk 2 is set down, and the critical rotation speed is increased. Further, such a stress generating means 40 is provided by rotating the adjustment nut.
Subtle increases and decreases are possible, and this is considered a practical method. [Modification 5] In the disk rotating device of Modification 5, FIG.
3. As shown in FIG. 24, FIG. 24 shows an example in which the respective annular holding members 42 and 43 and the respective flanges 413 and 412 in Modification 4 are integrated to simplify the example.

In FIGS. 22 and 23, the annular chevron member 41 and the pressing member 44 are members substantially equivalent to those of the fourth modification, and a detailed description is omitted. 441 is a bolt fixed to the holding member 44 body which has been cut so as not to be moved by a screw lock. The annular chevron member 41 was machined so that there was no gap in the crest portion 41a by cutting a coned disc spring, and both end edges 41b and 41c were parallel to each other in the axial direction.

As a result, the disk 2 is connected to the pair of flanges 51.
2, 513 are held on the contact surfaces 512a, 513a. The inner flange 513 is provided with an annular recess 514 toward the outside.
Twelve annular legs 515 protrude. This leg 5
The annular angled member 41 and the pressing member 44 are incorporated into the outer peripheral surface 515a of the annular angled member 15.
1a is arranged toward the pressing member 44 (the front and back of the annular chevron member 41 with respect to the pressing member 44 are reversed from the modification 4).

The flange 512 is provided with through holes 516 formed at equal intervals in the circumferential direction. The through holes 516 allow the male screw portion 441 to pass therethrough. The inner surface of the through hole 516 is a support surface 512b that supports the skirt portion (inner and outer ends 41b, 41c) of the annular chevron 41,
On the outer surface, an adjusting nut 4 screwed with the male screw portion 441
A concave groove 517 is formed for burying 5 so that its rotation can be adjusted.

The annular chevron 41 is inserted into the leg 515 of the flange 512, and the disk 2 is inserted into the outer periphery thereof, and the disk 2 is held in contact with the contact surface 512a. Next, the male screw portion 441 of the holding member 44 is inserted into the through holes 411 and 516.
Through. The holding member 44 is pulled by screwing the adjustment nut 45 into the male screw portion 441.

By tightening the adjusting nut 45, the annular chevron 41 is brought into contact with the contact surface 44a and the contact surface 512.
b compressively deforms in the axial direction. This adjustment nut 4
When a strong load is applied parallel to the axial direction by further tightening the outer peripheral surface 4,
1b and the inner peripheral surface 41c are in contact with the contact surface 51 of the peripheral edge of the through hole 516.
2b, the vicinity of the ridge 41a of the annular chevron member 41 abuts on the inner peripheral surface 44a of the holding member, and the annular chevron member 41 is deformed so as to be crushed by receiving an axial compressive load.

Here, since the annular angle member 41 is formed of a spring steel material, the outer diameter or the inner diameter tends to increase or decrease due to the compressive load, whereby the inner peripheral surface of the disc 2 is increased. An urging force acts on the disk 2 and the support surface 515a to act as an internal pressure Pi on the disk 2.

The internal pressure Pi applied to the inner peripheral surface 4a can be adjusted by adjusting the screwing strength of the nut 45. The adjustment of the internal pressure Pi can be finely adjusted since the frictional portion is small similarly to the fourth modification, and attachment and detachment are easy. In addition, this configuration may have a smaller number of components than in the fourth modification.

As a result, a stress is generated in the disk 2 in the same manner as when the disk 2 is put down, and the critical rotation speed is increased. Further, such a stress generating means can be finely increased or decreased by rotating the adjusting nut, and is considered to be the most practical method.

Although the annular chevron member is formed by joining a pair of disc springs having different directions, the present invention is not limited to this, and the annular chevron member may be integrally formed by stamping or pressing a spring steel material. Of course, this chevron shape is not limited to a shape having a ridge line, and may be variously deformed as shown in FIG.
In this figure, a cross section of the flange of the annular chevron member is shown,
The arcs (a), the trapezoids (b), and the chevrons are stacked in different directions (c), and a plurality (two in the figure) of the chevrons are stacked and stacked (d). . In any case, it is preferable to arrange and design the annular chevron 41 so that friction does not occur between the circumferential surface 4a and the outer circumferential surface 41b. [Modification 6] In each of the above modifications, a plurality of screw members (adjustment nut 45 and male screw portion 441) are used. However, this screw member is formed by a screwing member whose rotation center and rotation center coincide with each other. It may be simple and simplified.

For example, as shown in FIG. 26, a female screw portion 644a is engraved on the inner peripheral surface in place of the pressing member 44, and an annular pressing member 644 whose inner side surface 644b (the back surface in the drawing) is flat is used. Was. In addition, the outer flange portion 612
Has an annular leg 615 protruding inward in the axial direction,
A male screw portion 616 that is screwed into the female screw portion 644a is engraved on the outer periphery of the tip.

The annular holding member 644 and the flange 6
When the assembly is performed with the annular chevron member 41 interposed between the rotary disc 12 and the rotary disc 12, a rotary disk device as shown in FIG. 27 is assembled. According to this configuration, the annular chevron member 41 does not need to be formed because the through hole 411 is unnecessary.

In FIG. 27, the disk 2 is held on contact surfaces 612a and 613a of a pair of flanges 612 and 613. The inner flange 613 has an annular recess 614 facing outward, into which an annular leg 615 of the outer flange 612 is fitted, and an outer peripheral surface 615a of the leg 615 has an annular chevron. A member 41 is incorporated. The male screw 6 at the tip of the leg 615
A holding member 644 is screwed into 16.

When the holding member 644 is tightened, the inner side surface 644b comes into contact with the crest 41a of the annular chevron 41,
The skirts (41b, 41c) are in contact with the contact surface 612a. Then, when the pressing member 644 is strongly tightened, the annular chevron member 41 is compressed and deformed, the diameter thereof is uniformly expanded along the outer peripheral surface 41b, and a load (internal pressure) is applied to the inner peripheral surface 4a of the disk 2 so that the disk 2 generates stress.

Thus, as compared with the other modified examples, there is an advantage that the stress can be generated over the entire disk by a single screwing. In addition, the adjustment of the load is similar to that of the fourth modified example, so that the frictional portion is small, so that it is easy to make fine adjustments, and it is easy to mount and remove. In this configuration, the shape of the annular chevron member 41 is simpler than that of the fourth modification, and the number of parts may be small.

As a result, a stress is generated in the disk 2 in the same manner as when the disk 2 is set down, and the critical rotation speed is increased. Further, such a stress generating means 40 is provided by rotating the adjustment nut.
It can be finely increased or decreased, and is considered to be practical as a simple method.

In this modification, an annular chevron member is interposed therebetween. However, even when an inclined member is interposed therebetween, a single screw can similarly apply a stress to the disk. is there. Further, it is preferable that a precision screw is engraved on the female screw portion 644a and the male screw portion 616. [Modification 7] In the disk rotating device of Modification 7, FIG.
Is formed integrally with the angled annular member 41 shown in FIG.
As shown in FIG. 33, an annular chevron portion 241 is formed near the inner periphery of the disk 2. Such a chevron 24
1 can be easily obtained by pressing the inner periphery of the disk in a ring shape.

When the pressing member 644 is tightened, the inner side surface 644b comes into contact with the peak 241a of the peak 241.
The skirts (241b, 241c) are in contact with the contact surface 612a. Next, when the holding member 644 is strongly tightened, the angled portion 241 is compressed and deformed with these contact portions (241a to 241c) as fulcrums, and an internal pressure is generated in the disk 2, and the disk 2
The same stress can be generated as in the case of squatting.

Thus, similarly to the sixth modification, the critical rotation speed is increased. Further, since the disc 2 and the angled portion 241 as the stress generating means are integrated, the configuration is simple and mass production can be performed. Further, as described above, the stress can be generated by providing the stress generating means on the disk itself and directly applying a load to the disk. [Modification 8] The pressing member 644 of Modification 7 can be shared by a flange 813 as shown in FIG. According to such a configuration, a pair of flanges 812 and 813 is provided by a flange fastening nut N (not shown).
Is tightened to support the disk 2. The annular chevron portion 241 of the disk 2 has two hem portions 241b, 24b.
1c is in contact with the contact surface 612a, and the peak 241a is in contact with the contact surface 813a.
13 by tightening the two hem portions and the mountain portions (241
An internal pressure is generated in the disk 2 by receiving an axial compressive load with the points a to c) as fulcrums. Thereby, substantially the same operation and effect as the modification 7 are achieved. The inner peripheral surface 4a of the disk 2 is, as shown in FIG.
It is preferable to be supported by an appropriate support in the axial direction by 15a or the like.

In the eighth modification, the chevron 2
As shown in FIG. 35, 41 may be a deformed portion 242 deformed in a direction orthogonal to the plane direction of the disk 2. In any case, for example, when an external compressive load is applied by a flat surface such as a flange surface, the top or bottom 2
Each of the deformed portions 242 is compressed and deformed, and the diameter thereof is expanded. Thereby, an internal pressure can be generated in the disk 2.

The position of the deformed portion 242 is not limited to the vicinity of the inner periphery of the disk 2, but is provided at a desired position in the radial direction of the disk 2 to generate a stress at a desired position of the disk 2 in the radial direction. It is expected that the stress distribution of the disk 2 can be adjusted.

[Modification 9] The stress converting means described above may have a shape in which a disc spring is integrally fixed to the inner peripheral surface of the disk as shown in FIG. Also in this case, a conical spring-shaped deformed portion 2
42 is a flange 912, as shown in FIG.
913 and the like, it is compressed and deformed by receiving a plane load from the contact surfaces 912a and 913a. The inner peripheral surface 4a of the disk 2 abuts against the abutting surface 915a of the annular leg 915 of the flange 913, and the conical spring-shaped deformed portion 242 is expanded in diameter, so that a stress is generated in the disk 2. Since such a configuration is a very simple configuration, it is considered suitable for mass production.

Other structures, functions and effects are described in Embodiment 1.
Therefore, detailed description is omitted.

Hereinafter, the effects of the present invention will be specifically described with reference to specific examples. [Embodiment 3] The disk 2 has an outer diameter of 300 mm and an inner diameter of 80 m.
m, using a circular steel plate having a thickness of 2.0 mm and a hardness of 38 to 43,
Similarly to the first embodiment, using [calculation of natural frequency NF], the relationship between the internal pressure and the natural frequency NF in each vibration mode is determined to be equal to the maximum value of kinetic energy during vibration and the maximum value of work energy. It was determined by calculation using the energy method. In addition, the natural frequency in each vibration mode when the internal pressure Pi was changed using the taper type flange manufactured according to Modification 2 and the disc spring type flange manufactured according to Modification 5 was determined, and the results were obtained. Is shown in FIG.

As shown in FIG. 28, in the vibration mode larger than the mode (0, 2) as in the first embodiment, the natural frequency NF is increased by increasing the internal pressure in any of the taper type flange and the disc spring type flange. Was confirmed to be increased.

FIGS. 29 and 30 show changes in the natural frequency applied to the rotating disk when the internal pressure is applied and when the internal pressure is not applied. From the comparison of these figures, it can be confirmed that each mode is separated into a forward wave and a backward wave by the Doppler effect together with the rotation. According to FIG. 29 in which no internal pressure is applied, in mode (0, 2), it was confirmed that the backward wave decreases with the rotation speed and approaches 0 Hz. On the other hand, according to FIG. 30 in which the internal pressure was applied, the mode (0, 2) was clearly confirmed even when the spindle speed was increased.

As a result, in the vibration mode larger than the mode (0, 2), it was confirmed that the internal pressure was increased and the frequency was increased, and this tendency substantially coincided between the calculated value and the actually measured value. . [Embodiment 4] This embodiment 4 compares the internal pressure tensioning method according to the present invention with the conventional high-speed cutting performance of a tip saw according to the conventional tensioning (normal tensioning) method according to a specific embodiment. This demonstrates the effects of the invention.

Table 2 shows the shape of the used tip saw and the tool specifications.
And the cutting conditions are shown in Table 3. The workpiece was made of carbon steel S45C for machine structural use having a width of 100 mm and a thickness of 9 mm, and was 73.3 mm higher than the main shaft. Under these cutting conditions, a tip saw that has not been subjected to the waist-in process cannot be cut at an increased rotation speed, and a high-speed cutting experiment cannot be performed.

[0120]

[Table 2]

[0121]

[Table 3]

The natural frequencies of the master plates of mode (0,2) and mode (0,3) used here are 196.22 Hz and 330.64 Hz in the conventional waist-down method. In the internal pressure method according to the present invention, they were 198.12 Hz and 323.97 Hz. Note that the natural frequency of the master plate before the application of the internal pressure is 184.80 Hz and 295.8.
Since it is 0 Hz, it can be seen that squatting is slight tensioning.

Since the cutting is a high-speed cutting, the processing progressed with sparks like the grinding processing. The tool damage during repeated cutting appeared due to crater wear as well as flank wear of the front and side cutting edges. At the same time, the occurrence of thermal cracks was also confirmed.

FIG. 31 shows the wear curves of the front flank and the lateral flank when cut up to 50 times. As a result, there was no significant difference in the wear rate between the conventional squat method and the internal pressure method according to the present invention, but the former was slightly faster with the front cutting edge, and the latter was slightly faster with the lateral cutting edge.

Next, FIG. 32 shows the surface roughness (Roufhness) of the work to be measured, which was measured almost perpendicularly to the cutting direction. As in the case of a normal high-speed cutting tip saw, the surface roughness of any tip saw tended to decrease with the number of cuts when the number of cuts was repeated. Although there is no difference between the two methods in the initial stage of cutting, in this example, it was confirmed that the surface roughness of the workpiece according to the internal pressure method according to the present invention was small when the number of cuts exceeded 10. The reason why the surface roughness is improved by the internal pressure method is not clear, but it is considered that the cutter mark is reduced due to a large lateral cutting edge wear. In any case, it has been confirmed that, according to the internal pressure method of the present invention, a tip saw capable of performing high-speed cutting can be obtained in the same manner as a conventional tip-in saw.

Next, the change in vibration frequency during high-speed cutting was measured by an FFT analyzer when cutting with a tip saw. The largest frequency of the vibration spectrum was 33 Hz due to the rotation of the main shaft, and was mostly occupied by forward waves and backward waves of each vibration mode of the master plate. Although the spectrum (dB) according to the internal pressure method was slightly larger than the spectrum (dB) according to the conventional squat method, the spectrum was almost the same.

Next, a high-speed cutting of a steel material basically involves severe tool wear due to thermal factors, but a test was conducted to examine the application of the internal pressure method to high-speed cutting.

It can be said that there is no problem with respect to the wear rate, surface roughness and vibration performance. Therefore, application to other materials that can be cut at high speed, such as aluminum alloys, is not limited to steel sheets, and can be expected to be sufficient.

From the above, it is understood that the internal pressure method according to the present invention has a performance equivalent to that of the conventional stiffening, whereby the load F (the internal pressure Pi) is increased from the inner diameter to the outer diameter of the rotating disk. ), The natural frequency NF of the circular saw was increased, and as a result, it was confirmed that the same effect as that of the circular saw was obtained. Thus, it was confirmed by an experiment that anyone could adjust the tensioning of the circular saw and adjust the tension at the time of re-polishing, which could not be performed before, without requiring skill.

Although the embodiment of the present invention has been described using a circular saw as an example, the load F from the inner periphery to the outer periphery of the disk is described.
By applying the (internal pressure Pi), the critical rotation speed of the disk can be increased. Therefore, the present invention provides not only circular saws, but also high-speed rotation devices used for polishing devices such as rotary grindstones, hard disks, and various vehicles Applications to such applications are expected.

Further, in the above embodiment, a circular saw is used as an example, and a steel plate is used as the material of the disk, but this material is not limited to a steel plate. For example, it can be widely applied to general isotropic homogeneous materials.

[0132]

According to the present invention, there is provided a disk rotating device capable of securing the stability of a thin disk even if the thin disk is rotated at a high speed, instead of the squatting based on experience and intuition. Can be.

[Brief description of the drawings]

FIG. 1 is a view for explaining a situation of sitting on a disc 2;

FIG. 2 is a diagram illustrating a disk 2;

FIG. 3 is a side view illustrating the disk rotating device according to the embodiment of the present invention.

FIG. 4 is a cross-sectional view taken along line AA of FIG.

5 is an exploded view illustrating an assembled state of the disk rotating device of FIG. 3;

FIGS. 6A and 6B are diagrams illustrating a state of a load on a disk and a state of stress generated thereby.

FIGS. 7A and 7B are diagrams illustrating a disk provided with slits. FIGS.

FIG. 8 is a diagram illustrating stress generated in the disk according to the first embodiment.

FIG. 9 is a diagram showing residual stress of a disc subjected to a waist-in process;

FIG. 10 is a diagram showing the relationship between the internal pressure of the disk and the natural frequency according to the first embodiment.

FIG. 11 is a diagram schematically showing an apparatus for measuring a natural frequency.

FIG. 12 is a view showing a result of measuring a relationship between a vibration frequency and an amplitude of a disk according to the second embodiment.

FIG. 13 is a diagram illustrating the relationship between the internal pressure of the disk and the natural frequency.

FIG. 14 is a diagram illustrating a disk rotating device according to a modification.

FIG. 15 is a diagram illustrating a disk rotating device according to a modification.

FIG. 16 is a diagram illustrating a disk rotating device according to a modification.

FIG. 17 is a side view of the disk rotating device of FIG. 16, with a flange 312 removed.

FIG. 18 is a diagram illustrating a disk rotating device according to a modification.

FIG. 19 is an exploded perspective view illustrating an assembled state of an annular chevron member 41, an annular holding member 43, and a pressing member 44 as one component of the stress generating means 40 of FIG.

FIG. 20 is a partial cross-sectional perspective view illustrating the shape of an annular chevron member 41 of FIG.

21 is an annular holding member 42 as the member configuration of FIG.
FIG. 4 is a perspective view of the device viewed from the inside.

FIG. 22 is a view for explaining the principle of applying a load to a disk according to a modification.

FIG. 23 is a diagram illustrating a disk rotating device according to a modification.

FIG. 24 is an exploded view of parts of the disk rotating device of FIG. 23;

FIG. 25 is a partial cross-sectional view illustrating a modification of the annular chevron member.

FIG. 26 is an exploded view of parts of a disk rotating device according to a modification.

FIG. 27 is a diagram illustrating a disk rotating device using the components of FIG. 26;

FIG. 28 is a diagram illustrating a relationship between an internal pressure applied to a disk and a natural frequency according to the third embodiment, showing a comparison between a calculated value and an actually measured value for each vibration mode.

FIG. 29 is a diagram illustrating a transition of a natural frequency applied to a rotating disk when no internal pressure is applied according to the third embodiment.

FIG. 30 is a diagram showing a transition of a natural frequency given to a rotating disk when an internal pressure of 85 MPa is applied according to the third embodiment.

FIG. 31 is a diagram showing the degree of wear of the cutting edge when repeatedly cutting according to Example 4, in which (a) is a front cutting edge (front flank);
(B) shows the degree of wear of the lateral cutting edge (lateral flank).

FIG. 32 is a view showing the surface roughness of a cut surface when repeatedly cut according to Example 4.

FIG. 33 is a diagram illustrating a disk rotating device according to a modification.

FIG. 34 is a diagram illustrating a disk rotating device according to a modification.

FIG. 35 is a diagram illustrating a disk according to a modification.

FIG. 36 is a diagram illustrating a disk rotating device according to a modification.

[Explanation of symbols]

 2 Disc (base metal) 4 Mounting hole 11 Rotating spindle 17 Pressure medium storage space 19 Pressure screw (pressure adjusting screw) 20 Thin part Pi Internal pressure (load F)

 ──────────────────────────────────────────────────続 き Continued on front page F-term (reference) 3C034 BB52 3C040 AA01 GG37

Claims (18)

[Claims] 1. A disk rotating device for forming a mounting hole in the center of a thin disk, inserting the mounting hole into a rotation support shaft, and rotating the rotation support shaft to rotate the disk. The disk rotating device according to claim 1, wherein the disk has a stress generating means for generating a stress on the disk by receiving a load directly or indirectly. 2. The stress generating means comprises a thin annular cylindrical portion which accommodates a pressure medium annularly interposed between the inner periphery of the mounting hole and the outer periphery of the rotary support shaft. The disk rotating device according to claim 1, wherein the disk rotating device has sufficient hardness to support the annular cylindrical portion from an inner surface. 3. The stress generating means is orthogonal to a plane direction of the disk interposed between the inner periphery of the mounting hole and the outer periphery of the rotary support shaft, and has a radius gradually reduced toward the disk. 2. The circle according to claim 1, comprising: a slanted annular member having a slanted surface; and press-fitting means for press-fitting the slanted annular member between the disk and the rotary support shaft. Plate rotating device. 4. The stress generating means comprises an inclined annular portion having an inclined surface orthogonal to a plane direction of the disk fixed to the rotating shaft and having a gradually decreasing radius toward the disk. The disk rotating device according to claim 1, wherein the rotation is performed. 5. The stress-generating means includes an annular mountain-shaped member formed by an elastically deformable member having a mountain-shaped cross-section of a flange portion interposed between the inner periphery of the mounting hole and the outer periphery of the rotary support shaft. 2. The disk rotating device according to claim 1, further comprising: load generating means for generating a load toward a top or a skirt of said annular chevron member to deform said annular chevron member. 6. The disk rotating device according to claim 5, wherein the annular angled member is formed by forming a pair of annular disc springs formed of a spring steel material into an angled shape. 7. The disk according to claim 1, wherein the load generating means includes a deformed portion formed on the rotary disk and deformed in a direction orthogonal to a plane direction of the rotary disk. Rotating device. 8. The load generating means for converting a load in the direction of the rotating shaft into a load in an outer circumferential direction orthogonal to the rotating shaft, and a load in the direction of the rotating shaft toward the load direction converting means. 2. The disk rotating device according to claim 1, further comprising: a load generating means for generating a force. 9. The disk rotation according to claim 8, wherein said load direction changing means is based on a pressure medium interposed between an inner periphery of a mounting hole of said rotary disk and said rotary support shaft. apparatus. 10. The circle according to claim 8, wherein said load direction changing means is based on press-fitting of an inclined member interposed between an inner periphery of a mounting hole of said rotary disk and said rotary support shaft. Plate rotating device. 11. The disk rotating device according to claim 8, wherein said load direction changing means is based on a deformation of said elastic member caused by a compressive load applied to said elastic member. 12. The disk rotating device according to claim 8, wherein said load generating means is based on a single screwing mechanism. 13. The disk rotating device according to claim 8, wherein the load generating means is based on a plurality of screwing mechanisms arranged at equal intervals in a circumferential direction of the rotating disk. 14. The disk rotating device according to claim 1, wherein said stress generating means is controllable in accordance with an operation state of said disk rotating device. 15. Using the disk rotating device according to claim 14, as the rotational speed of the disk rotating device increases,
A method for controlling a disk rotating device, wherein the stress generation means increases the stress generation. 16. The disk rotating device according to claim 1, wherein the disk rotating device is applied to a circular saw, a rotary grinder, a disk brake, and a hard disk. 17. A mounting hole is formed at the center of the thin base metal,
In the circular saw device, in which the mounting hole is inserted into a rotation support shaft and the base is rotated by rotating the rotation support shaft, a slit radially outwardly extending around a periphery of the mounting hole as the base. Wherein, between the inner circumference of the mounting hole and the rotation support shaft, a stress generating means for generating a stress at a peripheral edge of the base metal by applying a load in an outer circumferential direction of the base metal is provided. Characteristic circular saw device. 18. A circular saw device according to claim 17, wherein said stress generating means is the stress generating means according to any one of claims 2 to 13.