JP6339253B1 - Rotating body damping mechanism, damping flange, and damping method - Google Patents

Abstract

PROBLEM TO BE SOLVED: To provide a damping mechanism capable of reducing chatter vibration of a rotating shaft. A vibration control mechanism incorporated in a rotating body having a rotating shaft, wherein the rotating body includes a plurality of space portions arranged rotationally symmetrically on a predetermined circumference around the rotating shaft. In each of the plurality of space portions of the one or more space groups, the rotation axis direction parallel to the rotation axis, the radial direction perpendicular to the rotation axis, and the rotation direction of the rotating body It has a weight group that includes a plurality of weight parts that are accommodated with a gap and are movable with respect to the rotating body. [Selection] Figure 1

Description

  The present invention relates to a vibration damping mechanism, a vibration damping flange, and a vibration damping method capable of suppressing chatter vibration of a rotating body.

  The polishing quality evaluated by the surface roughness is affected by the vibration of the rotating grindstone and the rotating shaft that rotates integrally with the grindstone. Abrasive grains are considered to be cutting blades with a short pitch, and when the uneven surface of the processed surface is cut, the rotating shaft is shaken due to a high-frequency impact force. This vibration is considered to be the source of chatter vibration, which is not a forced force of rotational torque but a rotational resistance reaction force, which causes self-excited vibration determined by the material and structure of the rotating body.

  The rotating body causes an eccentricity in which the rotation center line and the center of gravity line (the line with the smallest moment of inertia of the rotating surface) are separated from the driving torque by the impact reaction force from the machining surface or road surface, and the centrifugal force acting on the rotation center due to the eccentricity Becomes unbalanced, centrifugal force is generated, and further eccentricity increases. This eccentric centrifugal force causes chatter vibration due to the resonance phenomenon of the rotating body. It is necessary to suppress the excitation force before resonance.

  As such an apparatus for suppressing vibration of the rotating shaft, for example, there are a plurality of weights having the same mass and shape, and a plurality of storage chambers capable of swinging the plurality of weights in an arbitrary direction. There is a balancer that includes a weight holder that is drilled (see, for example, Patent Document 1).

JP 2011-169431 A

  However, it is necessary to consider how to mitigate the impact reaction force received from the processing surface and road surface that causes chatter vibration of the rotating body as well as balancing the center of gravity position.

  Further, the impact reaction force that causes chatter vibration of the rotating shaft is assumed to be a vector resultant force that dynamically fluctuates in three directions of the circumferential direction, the radial direction perpendicular to the rotating grindstone, and the rotating shaft direction. There is a need.

  The present invention has been made to solve such a conventional problem. The radial direction causes the deflection of the rotating shaft, the circumferential direction causes the twist of the rotating shaft, and the expansion and contraction of the rotating shaft. It is an object of the present invention to provide a damping flange capable of relieving the impact force in the direction of the rotating shaft and suppressing the rotating shaft chatter vibration.

The present invention is a vibration damping mechanism incorporated in a rotating body having a rotating shaft, and the rotating body includes a plurality of spherical space portions arranged rotationally symmetrically on a predetermined circumference around the rotating shaft. In each of the plurality of spherical space portions of the one or more space groups, the rotation axis direction parallel to the rotation axis, the radial direction perpendicular to the rotation axis, and the rotation direction of the rotating body are provided. , With a predetermined gap for collision with the rotating body, with respect to the rotating body, in the direction of the rotation axis parallel to the rotation axis, the radial direction perpendicular to the rotation axis, and the rotation direction of the rotation body , possible floating of collision in all directions, the shape will have a weight groups each containing one weight part of the sphere, parallel to the rotation axis direction to the rotation axis, perpendicular radial to the rotation axis, and the rotation of the The predetermined gap in the rotation direction is due to the fact that the weight part is not integrated with the rotating body and the weight part collides with the rotating body. Gap for transmitting the impact force, i.e., the inner diameter of the spherical space, the difference between the outer diameter of the weight of the shaped sphere is 0.5mm from 0.1 mm.

Further, the present invention is a vibration damping flange attached to a rotating body having a rotating shaft, and includes a fixed portion to the rotating body and a plurality of spherical space portions arranged rotationally symmetrically on a predetermined circumference. In each of the flange main body having one or more groups and a plurality of spherical spaces in the one or more space groups, a rotation axis direction parallel to the rotation axis, a radial direction perpendicular to the rotation axis, and a rotation body Rotation direction is accommodated with a predetermined gap for collision with the flange main body, and with respect to the flange main body, a rotation axis direction parallel to the rotation axis, a radial direction perpendicular to the rotation axis, and rotation the rotational direction of the body, which can be floating impinging in all directions, the shape will have a weight groups each containing one weight part of the sphere, parallel to the rotation axis direction to the rotation axis, perpendicular radial to the rotation axis, In addition, the predetermined gap in the rotation direction of the rotating body is such that the weight portion is not integrated with the rotating body. Therefore, a predetermined gap for transmitting impact force due to the collision of the weight portion with the rotating body, that is, the difference between the inner diameter of the spherical space portion and the outer diameter of the weight portion of the spherical shape is 0.1 mm to 0.5 mm.

  In the vibration damping method of the present invention, vibration damping flanges are respectively attached to a plurality of locations separated along the rotation axis of the rotating body.

  According to the vibration damping mechanism of the present invention, the circumferential direction that causes twisting of the rotating shaft, the radial direction that causes deflection of the rotating shaft, and the direction of the rotating shaft that causes expansion and contraction of the rotating shaft. A weight provided in a space in which the impact force freely floats in the rotary flange collides with the flange by the inertial force, so that the dynamic impact force of any direction and size is relieved and the rotation shaft vibration is reduced. Thereby, the origin of chatter vibration can be cut off to improve the polishing quality, and the fuel consumption can be improved by reducing the rolling resistance received from the road surface.

FIG. 5 is a diagram showing a configuration of a vibration damping flange of the present embodiment having first and second circumferences. It is sectional drawing of the damping flange of this embodiment. It is a figure which shows the effect | action of the damping flange of this embodiment when the impact force of the radial direction perpendicular | vertical to the rotating shaft of a rotary body is added. It is a figure which shows the effect | action of the damping flange of this embodiment when the impact force of the rotating shaft direction parallel to the rotating shaft of a rotary body is added. It is a figure which shows the effect | action of the damping flange of this embodiment when the impact force of the circumferential direction (rotation direction) of a rotary body is added. It is a figure which shows the state which each attached the damping flange of this embodiment to the both ends separated along the rotating shaft of the rotary body. It is a figure which shows an effect | action at the time of attaching the damping flange of this embodiment to the both ends separated along the rotating shaft of a rotary body, respectively.

  Hereinafter, the damping flange which is an embodiment of the present invention will be described in detail with reference to the drawings.

  FIG. 1 is a diagram illustrating a configuration of a vibration damping flange according to the present embodiment. As shown in FIG. 1, the damping flange 1 of the present embodiment includes an inner peripheral weight group 201 including a plurality of inner peripheral weight parts 201 a to 201 h (first weight parts) having the same shape as the flange main body part 100. (A first weight group) and one or more weight groups including a plurality of outer peripheral weight portions 202a to 202l (second weight portions) each having the same shape and a peripheral weight group 202 (second weight group). .

  The flange main body 100 of the present embodiment has a disk shape. The flange main body 100 has a through-hole 103 at the center of the main body, into which the rotating body X is inserted and which serves as a fixing portion to the rotating body X. In addition, what is necessary is just to use the well-known method for fixation to the rotary body X of the flange main-body part 100. FIG. In this way, when the damping flange 1 is fixed to the rotating body X, the damping flange 1 and the rotating body X rotate on the same rotation axis l.

  In the case of a machine tool, a grindstone and a cutting blade are attached to the rotating body X, and these are rotated. An impact force from a grindstone or a cutting blade due to the unevenness of the workpiece surface is transmitted to the rotating body X. In the case of an automobile, a tire is attached to the rotating body X, and the tire is rotated. An impact force from the road surface, commonly referred to as rolling resistance, due to road surface irregularities is transmitted to the rotator X. Due to this impact force and eccentricity, the resultant vector force of centrifugal force causes chatter vibration of the rotating shaft.

  FIG. 2 is a cross-sectional view of the vibration damping flange of the present embodiment. 2A is a cross-sectional view taken along the line BB in FIG. 1B, and FIG. 2B is a cross-sectional view taken along the line AA in FIG.

  As shown in FIGS. 1 and 2, the flange main body 100 is arranged rotationally symmetrically on the circumference (on the first circumference) having a radius r1 centered on the center (rotation axis l) of the main body. An inner circumferential space group 101 (first space group) composed of a plurality of inner circumferential space portions 101a to 101h (first space portions) each having the same shape, and a circumference having a radius r2 centered on the rotation axis l ( One round with the outer peripheral space group 102 (second space group) composed of a plurality of outer peripheral space portions 102a to 102l (second space portions) having the same shape and arranged rotationally symmetrically on the second circumference) It has the above space group.

  The inner circumferential space portions 101a to 101h and the outer circumferential space portions 102a to 102l of the present embodiment are cylindrical spaces having a central axis parallel to the rotation axis l. Corresponding inner peripheral weight portions 201a to 201h and outer peripheral weight portions 202a to 202l are accommodated in the inner peripheral space portions 101a to 101h and the outer peripheral space portions 102a to 102l, respectively. Note that the shapes of the inner peripheral space portions 101a to 101h and the outer peripheral space portions 102a to 102l of the present embodiment are not limited to this, and the corresponding inner peripheral weight portions 201a to 201h and outer peripheral weight portions 202a to 202l are housed inside. In such a case, the shape may be a shape in which a gap is generated around the entire weight.

  Since the inertia force of the flange itself that resists the impact force is also effective, the flange body 100 preferably has a certain amount of mass. Moreover, it is preferable that the mass of the weight is less than the mass of the entire rotating body including the flange.

  The inner peripheral weight parts 201a to 201h and the outer peripheral weight parts 202a to 202l have a sphere or columnar shape. Note that the shapes of the inner peripheral weight portions 201a to 201h and the outer peripheral weight portions 202a to 202l are not limited to this, and when the inner peripheral weight portions 201a to 201l are accommodated in the corresponding inner peripheral space portions 101a to 101h and outer peripheral space portions 102a to 102l, Any shape that creates a gap around the entire circumference of the weight may be used.

  As shown in FIG. 2, when the outer peripheral weight portion 202 is accommodated in the outer peripheral space portion 102, there is a gap between the inner surface of the outer peripheral space portion 102 and the surface of the outer peripheral weight portion 202 in the axial direction l. There are g1 and g2, and there are gaps g3 and g4 in the radial direction (and circumferential direction) of the flange main body 100.

  In addition, as shown in FIG. 2, when the inner peripheral weight portion 201 is accommodated in the inner peripheral space portion 101, a shaft is provided between the inner surface of the inner peripheral space portion 101 and the surface of the inner peripheral weight portion 201. In the direction l, there are gaps g5 and g6, and there are gaps g7 and g8 in the radial direction (and circumferential direction) of the flange main body 100.

  The gaps g1, g2, g3, and g4 should have dimensions that are sufficient for the outer peripheral weight portion 202 to move freely inside the outer peripheral space portion 102 but have an instantaneous collision time. The gaps g1, g2, g3, and g4 change instantaneously, but the sum of g1 and g2 and the sum of g3 and g4 are constant.

  Similarly, the gaps g5, g6, g7, and g8 should have dimensions that are sufficient for the inner circumferential weight 201 to move freely inside the inner circumferential space 101 but have an instantaneous collision time. The gaps g5, g6, g7, and g8 change instantaneously, but the sum of g5 and g6 and the sum of g7 and g8 are constant.

  In addition, in order for the impact force due to the collision to be transmitted, it is necessary that the flange main body portion 100, the inner peripheral weight portion 201, and the outer peripheral weight portion 202 are not integrated with each other. The sum of the gaps g1 and g2, the gaps g3 and g4, so that the collision time is instantaneous and the flange main body 100 and the inner peripheral weight part 201 and the outer peripheral weight part 202 are not integrated due to thermal expansion or rust. , The sum of gaps g5 and g6, and the sum of gaps g7 and g8 (predetermined gap) are preferably 0.1 mm or more and 0.5 mm or less. If it is smaller than 0.1 mm, there is a risk of integration due to expansion or rust, and if it is larger than 0.5 mm, the impact force is difficult to be transmitted instantly. However, depending on the size of the flange diameter, a suitable value for the gap may be outside the above range.

  Next, the operation of the vibration damping flange 1 of this embodiment will be described. The impact force applied to the rotating body X includes forces in three directions: a circumferential direction D3, a radial direction D1 perpendicular to the circumferential direction D3, and a rotational axis direction D2. The vibration damping flange 1 of the present embodiment reduces the impact force of the dynamic composite vector in the circumferential direction D3, the radial direction D1, and the rotation axis direction D2.

  FIG. 3 is a diagram showing the action of the vibration damping flange 1 of the present embodiment when an impact force in the radial direction D1 perpendicular to the rotation axis l is applied to the rotating body X. 3 to 7, only the outer peripheral space portion 102b and the outer peripheral weight portion 202b are described as representative examples, and combinations between the other inner peripheral space portion 101 and the inner peripheral weight portion 201, and other outer peripheral space portions. The combination between the outer peripheral weight portion 202 and the outer peripheral weight portion 202 is omitted, but the combination between the other inner peripheral space portion 101 and the inner peripheral weight portion 201, and the other outer peripheral space portion 102 and the outer peripheral weight portion 202. The same operation / action occurs in the combination of the two. Moreover, in FIG. 3-7, the magnitude | size and clearance gap of the outer periphery space part 102b and the outer periphery weight part 202b are exaggerated and described from FIG.

  As shown in the drawing, when an impact force in a radial direction (direction D1 in the figure) perpendicular to the rotating shaft 1 is applied to the rotating member X, the rotating member X is supported even if the rotating shaft 1 is supported by a bearing. Is elastically deformed by a short distance in the direction of D1, and the flange main body 100 fixed to the rotating body X is momentarily elastically deformed by a short distance in the direction of D1. In this case, since the outer peripheral weight portion 202b is not fixed to the flange main body portion 100, the outer peripheral weight portion 202b moves within the outer peripheral space portion 102b by a minute distance elastic deformation, and the outer peripheral weight portion 202b and the flange main body portion 100 are illustrated. It collides with A part inside.

  Thereby, the flange main-body part 100 receives reaction force in the D1 'direction in a figure opposite to D1 direction. The impact force in the D1 direction and the reaction force in the D1 ′ direction cancel each other to some extent, and the impact force in the D1 direction is relaxed. Note that the reaction force in the D1 ′ direction is an inertial force obtained by multiplying the acceleration of the impact force by the mass of the inner peripheral weight part 201 and the outer peripheral weight part 202, and thereby the minute elasticity of the inner peripheral weight part 201 and the outer peripheral weight part 202. This is the instantaneous resultant force of the elastic force due to deformation.

  Further, the mass of the flange main body 100 becomes an inertial force, and the impact force in the D1 direction is suppressed. The principle of impact force suppression in a minute gap is the same as the phenomenon that when an impact force is applied to one end of a plurality of continuously contacting spheres, the other sphere moves and the middle sphere hardly moves. . In the middle ball, the received impact cancels out the inertial reaction force from the opposite side.

  FIG. 4 is a diagram showing the action of the vibration damping flange 1 of the present embodiment when an impact force in the direction D2 parallel to the rotation axis 1 of the rotating body X is applied.

  As shown in the figure, when an impact force in a direction parallel to the rotating shaft l (direction D2 in the figure) is applied to the rotating body X, the rotating body X is fixed to the rotating body X even if it is supported by a bearing. The flange body 100 thus made is elastically deformed by a short distance in the direction D2. In this case, since the outer peripheral weight portion 202b is not fixed to the flange main body portion 100, the outer peripheral weight portion 202b moves within the outer peripheral space portion 102b by a minute distance elastic deformation, and the outer peripheral weight portion 202b and the flange main body portion 100 are illustrated. It collides with A part inside.

  As a result, the flange main body 100 receives a reaction force in the direction D2 'in the drawing opposite to the direction D2. The impact force in the D2 direction and the reaction force in the D2 'direction cancel each other to some extent, and the impact force in the D2 direction is relaxed. Note that the reaction force in the D2 ′ direction is the inertial force obtained by multiplying the acceleration of the impact force by the mass of the inner peripheral weight part 201 and the outer peripheral weight part 202, and thereby the minute elasticity of the inner peripheral weight part 201 and the outer peripheral weight part 202. This is the instantaneous resultant force of the elastic force due to deformation.

  Further, the mass of the flange main body 100 becomes an inertial force, and the impact force in the D2 direction is suppressed. The principle of impact force suppression in a minute gap is the same as the phenomenon that when an impact force is applied to one end of a plurality of continuously contacting spheres, the other sphere moves and the middle sphere hardly moves. . In the middle ball, the received impact cancels out the inertial reaction force from the opposite side.

  FIG. 5 is a diagram showing the action of the vibration damping flange of the present embodiment when an impact force in the circumferential direction (rotation direction) D3 of the rotating body X is applied.

  As shown in the figure, when an impact force is applied in the circumferential (rotation) direction (D3 direction in the figure) of the rotary body X, the rotary body X is D3 even if the rotary shaft l is supported by the bearing. The flange main body 100 twisted in the direction and fixed to the rotating body X is elastically deformed by a short distance in the D3 direction. In this case, since the outer peripheral weight portion 202b is not fixed to the flange main body portion 100, the outer peripheral weight portion 202b moves within the outer peripheral space portion 102b by a minute distance elastic deformation, and the outer peripheral weight portion 202b and the flange main body portion 100 are illustrated. It collides with A part inside. The impact force in the D3 direction and the reaction force in the D3 ′ direction cancel each other to some extent, and the impact force in the D3 direction is relaxed.

  Further, the mass of the flange main body 100 becomes a rotational moment of inertia, and the impact force in the D3 direction is suppressed by the so-called flywheel effect.

  In the above-described embodiment, the impact force in the three directions is individually described. However, since the impact is actually received in any three-dimensional direction, the reaction force for the impact relaxation is also synthesized. In addition, the weight which received the impact force moves through the gaps in the space portion, and is repeatedly converted into impact energy and kinetic energy and accompanying heat energy and absorbed by repeating elastic collisions randomly on the walls around the space portion. It is considered that the energy due to the original impact force is relatively small as compared with the energy loss due to the chatter vibration of the rotating body due to the centrifugal force due to the increased eccentricity.

  In the above embodiment, the number of weights included in the outer periphery weight group 202 is 12 and the number of weights included in the inner periphery weight group 201 is eight. However, the number is not limited to this, and may be two or more. As for the number of spaces included in the inner space group 101 and the outer space group 102, the centers of the space groups rotate according to the number of weights included in the inner weight group 201 and the outer weight group 202. It may be arranged so that it is rotationally symmetric with respect to the center, in other words, the relative center of gravity of all the weights coincides with the center of rotation of the damping flange 100. The number, material, and arrangement of weights that distribute the inertial force are the design specifications of each rotating machine, depending on the mass and arrangement space of the rotating body (spindle, axle, grindstone, end mill blade, etc.), and ease of processing. Gives freedom to optimize design with comprehensive consideration of cost and other factors.

  Moreover, in the said embodiment, although the inner periphery weight group 201 and the outer periphery weight group 202 were arrange | positioned over 2 circumference | surroundings of the inner periphery space group 101 and the outer periphery space group 102, it is not restricted to this, A circumferential space group is It may be 1 round, 3 rounds, 4 rounds or more. In the present embodiment, the radius r1 of the inner space group 101 and the radius r2 of the outer space group 102 have a relationship of r1 <r2, but r1 and r2 may be the same. In this case, the inner circumferential space portions 101a to 101h and the outer circumferential space portions 102a to 102l may be arranged so as not to overlap (for example, alternately). The mounting condition of the damping flange is determined by the restriction of the rotation shaft arrangement space, and the same section portion and sleep can be dispersedly arranged on the third, fourth,. The total mass of the weight will generate inertial force, and the number and arrangement of the weights (number of circumferences) will disperse the reaction force due to the inertial force by the number of weights, which will affect the amount of elastic deformation due to collision. Gives freedom of material selection.

  Moreover, in the said embodiment, although the shape of inner peripheral space part 101a-h and outer peripheral space part 102a-l was made into cylindrical shape, it is not restricted to this, Spherical shape, elliptical cross-sectional shape, rectangular cross-sectional shape, polygonal cross-sectional shape, And it is good also as those combination. Further, the shapes of the inner peripheral space portions 101a to 101h and the outer peripheral space portions 102a to 102l may be the same or different. It is necessary to consider the shape of the space and the weight so that the inertial force at the time of collision generates a reaction force in the opposite phase of the collision force and does not recover the collision relaxation reaction force by re-collision with the opposite wall due to the movement of the weight. . It gives design flexibility to prevent recovery of collision relaxation reaction force when phase shift due to normal rotation re-collises.

  Moreover, in the said embodiment, although the shape of inner peripheral weight part 201a-h and outer peripheral weight part 202a-l was made into the spherical shape, it is not restricted to this, A spherical shape, cylindrical shape, elliptical cross-sectional shape, rectangular cross-sectional shape, polygonal cross-section Or a combination thereof. Further, the shapes of the inner peripheral weight portions 201a to 201h and the outer peripheral weight portions 202a to 202l may be the same or different. It is necessary to consider the shape of the space and the weight so that the inertial force at the time of collision generates a reaction force in the opposite phase of the collision force and does not recover the collision relaxation reaction force by re-collision with the opposite wall due to the movement of the weight. . It gives design flexibility to prevent recovery of collision relaxation reaction force when phase shift due to normal rotation re-collises.

  As described above, according to the vibration damping flange of this embodiment, the radial direction causing the deflection of the rotating shaft, the circumferential direction causing the torsion, and the rotating shaft direction causing the expansion and contraction of the shaft. It becomes possible to relieve the impact force and reduce the rotation shaft vibration. Further, the vibration damping flange of the present embodiment has significant features in the following points.

  1. Current countermeasures against chatter vibration of the rotating shaft are to feed back the vibration value to the NC target value with the machining reaction force during cutting as a disturbance, or to finely control the cutting trajectory and angle by feedforward while predicting the disturbance. The invention of the present application suppresses vibration without a sensor or a control device by suppressing the processing reaction force at the origin.

  2. Conventionally, it is a target therapy based on feedback by controlling the position of the trajectory and angle, while the present invention is a fundamental therapy that suppresses external force that causes a core shake vibration called a processing reaction force.

  3. The present invention is a vibration control in which the excitation force of the vibration between the center of rotation and the center of gravity (core vibration) is a cutting resistance. From the viewpoint of the vibration characteristics of the core vibration, not only the rigidity and viscosity of the bearing but also the inertia resistance and rotation This is a technology in which cutting force is reduced by inertial force collision between a flange integrated with a shaft and a weight sliding inside the flange.

  4). According to the present invention, even if the end mill cutting blade or the grindstone of the grindstone is a material having a high crushing force, it does not affect the vibration of the spindle, so that high-precision machining can be performed.

  5. Conventionally, NC machine tools are usually unable to process with high accuracy as the target value, and it is usually necessary to finish by offset post-processing. However, according to the present invention, post-processing is not required and high accuracy is achieved according to the target value. Can be processed.

  Next, a vibration damping method in which the vibration damping flange of this embodiment is attached to a rotating body will be described.

  FIG. 6 is a view showing a state in which the damping flanges 1 and 2 of the present embodiment are respectively attached to both ends of the rotating body X separated along the rotation axis l. As shown in the drawing, by installing two damping flanges 1 and 2 having the same structure on the driving side and the reaction force side along the rotation axis l, the radial and axial impacts causing the flexural vibration are shown. Mitigates circumferential impact forces that cause force and torsional vibrations.

  FIG. 7 is a diagram showing an operation when the damping flanges 1 and 2 of the present embodiment are respectively attached to both ends separated along the rotation axis l of the rotating body X.

  As shown in the figure, the relative difference between the impact force in the rotational axis directions D4 and D5 and the impact force in the radial directions D6 and D7 causes the rotating body X to bend. The inner peripheral weight part 201 (not shown), the outer peripheral weight part 222, and the inner peripheral weight part 221 (not shown) alleviate the relative difference in the impact force. The relative difference between the impact forces in the circumferential directions D8 and D9 causes torsional vibration of the rotating body X, but the outer peripheral weights 202 and 222 and the inner peripheral weights 201 and 221 in the damping flanges 1 and 2 are used. (Not shown) alleviates the relative difference in impact force.

  In addition, the location which attaches the damping flanges 1 and 2 of this embodiment is not restricted to the both ends of the rotary body X, You may each attach to the several place distant along the rotating shaft 1 of the rotary body X.

  As described above, according to the vibration damping method using the vibration damping flange of the present embodiment, the vibration damping flange is installed on the driving side and the reaction force side along the rotation axis, which causes flexural vibration. There is a further effect that the impact force in the circumferential direction that causes the impact force and torsional vibration can be reduced.

  In the above-described embodiment, an example in which the vibration damping flange is configured separately from the rotating body has been described. However, each element of the vibration damping mechanism in the vibration damping flange may be directly incorporated into the rotating body. The term "rotary body" as used herein refers to, for example, drills and spindles of machine tools and polishing machines, holding flanges, tire wheels, railway wheels, shafts of shafts that transmit power from electric motors / generators and internal combustion engines, etc. A flywheel attached to the

  The vibration damping mechanism of the present embodiment is a vibration damping mechanism incorporated in a rotating body having a rotating shaft, and the rotating body is a plurality of spaces arranged rotationally symmetrically on a predetermined circumference around the rotating shaft. The space group including the portion has one or more rounds, and each of the plurality of space portions of the one or more space groups includes a rotation axis direction parallel to the rotation axis, a radial direction perpendicular to the rotation axis, and a rotation body It has a weight group including a plurality of weight parts that are accommodated with a predetermined gap in the rotation direction and that can move freely with respect to the rotating body.

  In the vibration damping mechanism of the present embodiment, the rotating body may have two or more space groups.

  Further, in the vibration damping mechanism of the present embodiment, the space portion may have a cylindrical shape.

  Further, in the vibration damping mechanism of the present embodiment, the shape of the weight portion may be a sphere or a columnar shape.

  In the vibration damping mechanism of the present embodiment, the predetermined gap in the rotation axis direction parallel to the rotation axis, the radial direction perpendicular to the rotation axis, or the rotation direction of the rotating body is 0.1 mm or more and 0.5 mm or less. Good.

  Moreover, you may each provide the damping mechanism of this embodiment in the several place distant along the rotating shaft of the rotary body.

1: Damping flange 100: Flange main body 101: Inner circumferential space group 101a to 101h: Inner circumferential space portion 102: Outer circumferential space group 102a to 102l: Outer circumferential space portion 103: Through hole 201: Inner circumferential weight group 201a to 201h: Inner peripheral weight portion 202: Outer peripheral weight group 202a to 202l: Outer peripheral weight portion

Claims (6)

A vibration damping mechanism incorporated in a rotating body having a rotating shaft,
The rotating body has one or more space groups including a plurality of spherical space portions arranged rotationally symmetrically on a predetermined circumference around the rotation axis,
In each of the plurality of spherical space portions of the one or more space groups, the rotating body is arranged in a rotating shaft direction parallel to the rotating shaft, in a radial direction perpendicular to the rotating shaft, and in a rotating direction of the rotating body. The rotating body is accommodated with a predetermined gap for collision with the rotating body, the rotating shaft direction parallel to the rotating shaft, the radial direction perpendicular to the rotating shaft, and the rotating direction of the rotating body of possible floating of collision in all directions, the shape will have a weight groups each containing one weight part of the sphere,
The predetermined gap in the rotation axis direction parallel to the rotation axis, the radial direction perpendicular to the rotation axis, and the rotation direction of the rotation body is because the weight portion is not integrated with the rotation body and the rotation The predetermined gap for transmitting an impact force caused by the collision of the weight portion with the body, that is, the difference between the inner diameter of the spherical space portion and the outer diameter of the weight portion of the spherical shape is 0.1 mm to 0.5 mm. The vibration control mechanism characterized by being.   The vibration control mechanism according to claim 1, wherein the rotating body has two or more rounds of the space group. A vibration damping method, comprising the vibration damping mechanism according to claim 1 or 2 at a plurality of locations separated along a rotation axis of the rotating body. A damping flange attached to a rotating body having a rotating shaft,
A flange main body having at least one space group including a fixed portion to the rotating body and a plurality of spherical space portions arranged in a rotationally symmetrical manner on a predetermined circumference;
In each of the plurality of spherical space portions of the one or more space groups, the flange main body has a rotation axis direction parallel to the rotation axis, a radial direction perpendicular to the rotation axis, and a rotation direction of the rotation body. A rotation direction parallel to the rotation axis, a radial direction perpendicular to the rotation axis, and a direction of the rotating body. direction of rotation, which can be floating impinging in all directions, the shape will have a weight groups each containing one weight part of the sphere,
The predetermined gap in the rotation axis direction parallel to the rotation axis, the radial direction perpendicular to the rotation axis, and the rotation direction of the rotation body is because the weight portion is not integrated with the rotation body and the rotation The predetermined gap for transmitting an impact force caused by the collision of the weight portion with the body, that is, the difference between the inner diameter of the spherical space portion and the outer diameter of the weight portion of the spherical shape is 0.1 mm to 0.5 mm. damping flange, characterized in that it. The said flange main-body part has the said space group 2 times or more, The damping flange of Claim 4 characterized by the above-mentioned. 6. A vibration damping method, wherein the vibration damping flanges according to claim 4 or 5 are respectively attached to a plurality of locations separated along the rotation axis of the rotating body.