JP2001248687A - Vehicuiar damper - Google Patents

Abstract

PROBLEM TO BE SOLVED: To provide a vehicular damper of a novel structure that can achieve an effective damping effect even on any axis-perpendicular or circumferential vibration of a rotary member. SOLUTION: A housing 12 fixed on a rotary member 18 is integrated with relatively displaceable independent mass members 16 opposed to the housing 12 at a circumferential interval. An elastic butting action of the independent mass members 16 against the housing 12 establishes a damping effect on the rotary member 18.

Description

DETAILED DESCRIPTION OF THE INVENTION

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a vibration damping device for reducing vibrations in a rotating member, for example, a rotating shaft such as a drive shaft, a crankshaft or a camshaft of an automobile, or a rotational driving force of a pulley, a gear or a pulley. The present invention relates to a vehicle vibration damping device having a novel structure that can exhibit an effective vibration damping effect by being applied to a rotating member such as a rotating rotating disk that transmits a signal.

[0002]

BACKGROUND ART Rotary shafts such as drive shafts and crank shafts used in vehicles such as automobiles, pulleys, and the like.
Generally, a rotating disk such as a gear vibrates in a rotation direction perpendicular to the axis, and the vibration may cause a resonance state, which may adversely affect noise and steering stability.

Therefore, in order to reduce such vibration of the rotating member, a dynamic damper provided with, for example, a sub-vibration system for a main vibration system has been adopted. As described in JP-A-62-297557 and JP-A-2-190641, such a dynamic damper has a structure in which a mass member is elastically moved by a spring member such as a rubber elastic body with respect to a rotating member which is a vibration member. It has a structure in which it is connected, and obtains a vibration damping effect on a rotating member, which is a main vibration system, based on the resonance action of a sub-vibration system constituted by a mass member and a spring member.

However, such a dynamic damper has a problem that the frequency range in which the vibration damping effect is exhibited is narrow because the vibration damping effect is obtained based on the resonance action. If the mass of the mass member and the spring constant of the spring member are tuned with respect to the bending vibration in the perpendicular direction, there is a problem that it is extremely difficult to obtain an effective vibration damping effect with respect to the torsional vibration in the circumferential direction. Further, in order to obtain an effective vibration damping effect, the mass of the mass member needs to be 15% or more of the mass of the rotating member which is the vibration member. There was.

Further, in a rotating member such as a pulley, as described in the above-mentioned publication, an inner peripheral boss portion and an outer peripheral rim portion are divided and connected by an annular rubber elastic body. Thus, a dynamic damper using a rim portion as a mass member has been proposed. However, in such a rotating member, a rubber elastic body is disposed on a transmission path of a rotational driving force. In some cases, it is difficult to secure sufficient transmittable torque and durability.

[0006]

The present invention has been made in view of the above circumstances, and an object of the present invention is to provide a method for effectively preventing vibration in a rotating member such as a rotating shaft or a rotating disk. An object of the present invention is to provide a vehicle vibration damping device having a novel structure capable of exhibiting an excellent vibration damping effect.

[0007]

An embodiment of the present invention which has been made to solve such a problem will be described below. In addition, each of the components employed in each of the embodiments described below can be employed in any combination as much as possible. In addition, aspects and technical features of the present invention are not limited to those described below, but are described in the entire specification and drawings, or based on an inventive idea that can be understood by those skilled in the art from the descriptions. It should be understood that the

That is, according to a first aspect of the present invention, a rigid housing is fixedly provided on a rotating member that rotates about a central axis, and an independent mass member is assembled to the housing by non-adhesion so as to be relatively displaceable. In the circumferential direction around the central axis, a vehicle vibration damping device in which the independent mass member and the housing are disposed so as to be elastically abuttable and opposed to each other,
Features.

In the vehicle vibration damping device having the structure according to this aspect, when vibration is input, the independent mass member is displaced relative to the housing so as to jump in the vibration input direction. The member hits the housing, and the vibration energy in the rotating member, which is the vibration member, is reduced based on the sliding friction and the action of the collision at that time, and the vibration damping effect is exhibited. In such a damping device, since the damping effect is not based solely on the resonance action, the mass member having a smaller mass is more effective than a conventional dynamic damper for vibration in a wide frequency range. The effect can be exhibited, and the vibration damping characteristic is hardly affected by the temperature change, so that a stable vibration damping effect can be exhibited.

Further, in such a vibration damping device, since the independent mass member is disposed so as to be independently displaceable and non-adhesive to the housing, a vibration damping effect based on the contact of the independent mass member with the housing is achieved. It can be exerted in any vibration in the direction perpendicular to the axis of the rotating member or in the rotating direction, and together with the vibration damping characteristics in a wide frequency range as described above, both the vibration direction and the frequency range are different. An effective vibration damping effect can be obtained for a plurality of vibrations.

In this embodiment, the housing may be provided as a case or the like formed of a rigid material such as metal which is formed separately from the rotating member to be damped and fixedly attached to the rotating member. In addition, the housing may be a hollow structure, and the housing may be constituted by the rotating member itself, or the outer peripheral surface of the rotating member may be used as a part of the housing. And if a housing formed separately from the rotating member is adopted, regardless of the rotating member,
It becomes easy to set the dimensional accuracy of the housing to a high degree. On the other hand, if at least a portion of the housing is configured using a rotating member, the structure of the housing can be simplified and the size can be reduced. Further, such a housing can be formed of, for example, a metal material such as iron or an aluminum alloy or a synthetic resin material. In order to advantageously secure rigidity for supporting the independent mass member and a vibration damping effect,
A rigid material having an elastic modulus of 5 × 10 ⁴ MPa or more is suitably used.

The independent mass member may be entirely formed of a rubber elastic material, a synthetic resin material, or a foamed material thereof, or may be rigidly fixed with a rigid material such as metal. It is also possible to form the independent mass member from a rigid material having a high specific gravity, such as metal or stone. When the independent mass member is formed from a rigid material, the contact surface between the independent mass member and the housing An elastic material layer such as a rubber elastic body or a synthetic resin is formed on at least one of them. Further, the elastic contact surface made of the elastic material layer or the like preferably has a Shore D hardness of 80 or less according to ASTM standard D2240 in order to reduce the contact sound (hitting sound) and improve the vibration damping effect. More preferably 2
0 to 40. In addition, the elastic contact surface between the independent mass member and the housing has an elastic modulus of preferably 1 to 10 ⁴ MPa, more preferably 1 to 10 ³ MPa for reducing the hitting sound and improving the vibration damping effect. , The loss tangent (tan δ) is preferably 10 ⁻³ or more, more preferably 0.01 to 10. Further, the gap size between the independent mass member and the opposing surface of the housing is set to 0.1 to 0.8 mm, preferably 0.1 to 0.5 mm in order to reduce the contact noise and improve the vibration damping effect. You. The housing has an elastic modulus of 5 × 10 ^{3 to} 5
It can be formed of a rigid material such as a synthetic resin material having a pressure of × 10 ⁴ MPa, and is effective in, for example, reducing the hitting sound and tuning the vibration damping characteristics. Further, when employing a housing having such a relatively low rigidity, it is desirable that the elastic modulus of the elastic material layer or the like at the contact surface between the independent mass member and the housing is lower than the elastic modulus of the housing, which is more preferable. Has an elastic modulus of 1 to 10 ²
MPa, whereby the strength and durability of the housing are advantageously ensured, and for example, it is possible to improve the vibration damping effect in a low frequency range. Furthermore, the mass of the independent mass member is 5 to 1 times the mass of the rotating member to be damped in order to obtain an effective damping effect while suppressing an increase in weight.
It is desirable to set it to 0%. When a plurality of independent mass members are assembled to one vibration damping target, the total mass of the plurality of independent mass members is calculated as 5 times the mass of the rotating member.
It is desirable to set to 10% to 10%.

[0013] Furthermore, the area where the independent mass member is disposed including the space between the independent mass member and the opposing surface of the housing is formed in the housing as an internal space substantially blocked from an external space. Is desirable. By housing and disposing the independent mass member in such an internal space, entry of foreign matters such as water and dust between the independent mass member and the facing surface of the housing is prevented, and the intended vibration damping effect is stabilized. Can be obtained. The internal space does not need to be completely shut off from the external space. For example, a minute communication hole may be formed to avoid an internal pressure change due to a temperature change.

According to a second aspect of the present invention, in the vibration damping device for a vehicle having the structure according to the first aspect, the center of gravity of the independent mass member as a whole under the rotating state of the rotating member is adjusted. It is characterized in that it can be positioned on the rotation center axis of the rotating member. In this embodiment, since the action of the bending force or the like on the rotating member due to the centrifugal force of the independent mass member is prevented, the adverse effect on the rotating member is reduced. There is no need to wear it. In order to position the center of gravity of the independent mass member as a whole under the rotation state on the rotation center axis of the rotation member, for example, a plurality of independent mass members formed independently of each other are circumferentially aligned on the rotation center axis. Are arranged at predetermined intervals, and each of the independent mass members is positioned using the centrifugal force accompanying the rotation of the rotating member so that the center of gravity as a whole is located on the rotation center axis of the rotating member. Such a structure or the like can be adopted.

Still further, according to a third aspect of the present invention, in the vehicle vibration damping device having the structure according to the first or second aspect, a plurality of the independent mass members are provided independently of each other. The independent mass members are configured to elastically abut on the housing in the circumferential direction around the central axis at both ends in the circumferential direction. In this aspect, the independent mass members formed independently of each other can be displaced independently of each other, and the vibration damping effect is exhibited based on the contact of each independent mass member with the housing. Can be done. In particular, in this aspect, since the mass of each independent mass member can be set small, each independent mass member can be easily jumped and displaced, and the vibration damping effect can be improved. In this aspect, the centripetal force exerted on the independent mass member by the housing is canceled between the independent mass members, whereby the bending force applied to the rotating member can be easily reduced or avoided.

Each of the independent mass members employed in the third aspect is, for example, a circle having an arc-shaped cross section extending at a predetermined length in the circumferential direction around the central axis and extending parallel to the central axis. An arc-shaped block or a circular rod having a circular cross-section and extending parallel to the central axis is preferably employed. In particular,
In the former independent mass member having an arc-shaped cross section, it is possible to set a large contact area in the direction perpendicular to the axis and in the circumferential direction. Further, in the latter independent mass member having a circular cross section, a vibration damping effect can be obtained in substantially the same manner with respect to vibration in any direction orthogonal to the central axis of the independent mass member.

In a fourth aspect of the present invention, in the vehicle vibration damping device having the structure according to the first or second aspect, the independent mass member is circumferentially continuous around the central axis. One of the annular mass member and the housing is provided with an engagement concave portion, and the other is provided with an engagement convex portion, and the engagement concave portion and the engagement convex portion are provided at the center. It is characterized in that it can be brought into contact with each other around the axis. In such an embodiment, by adopting the annular mass member that is continuous in the circumferential direction, the centrifugal force acting on the mass member is easily offset,
There is an advantage that the operation of the annular mass member is stabilized.

In the present invention, the rotating member may be a solid or hollow rotating shaft member, or a driving force transmitting member extending outward from the central axis in a direction perpendicular to the axis, such as a pulley, gear, pulley or the like. Rotating discs can also be of interest. And
When the present invention is applied to a rotating disk as such a rotating member, for example, a configuration in which the housing to which the independent mass member is assembled is fixedly provided at a radially intermediate portion of the rotating disk. Is preferably adopted. The housing may be formed integrally with the rotating disk, or may be formed separately and fixed to the rotating disk later. Further, in the vibration damping device having the structure according to the present aspect, since the independent mass member separate from the rotating disk as the driving force transmitting member is employed, the transmission path of the rotational driving force is divided. It is possible to transmit a large rotational driving force and to exhibit excellent durability.

[0019]

BEST MODE FOR CARRYING OUT THE INVENTION Hereinafter, in order to clarify the present invention more specifically, embodiments of the present invention will be described in detail with reference to the drawings.

FIGS. 1 and 2 show a vibration damping device 10 for a drive shaft of an automobile according to a first embodiment of the present invention.
It is shown. The vibration damping device 10 includes a housing 1
The independent mass members 16 are respectively arranged in the plurality of accommodation cavities 14 provided in the housing 2, and the housing 12 is attached to the drive shaft 18 by externally fixing the housing 12 to the drive shaft 18.

More specifically, the housing 12 includes a housing body 20 and a pair of lids 22. The housing body 20 has a thick cylindrical shape, and has a circular fitting hole 2 extending through the center shaft 24.
6 is provided. A plurality (eight in the present embodiment) of through-holes 28 penetrating in the axial direction are formed at equal intervals in the circumferential direction around the central axis 24 in the cylindrical wall portion of the housing body 20. These through-holes 28 have the same shape as each other, and each has a central axis 2 having a circular constant cross-sectional shape.
4 is formed in a straight line in parallel. That is, the housing main body 20 in which the through holes 28 are formed is connected to the center shaft 2.
The rotation balance is set so that the center of gravity axis is located on the center of rotation 4.

The housing body 20 is formed of a rigid material having an elastic modulus of 5 × 10 ⁴ MPa or more. For example, a metal material such as an aluminum alloy is extruded and cut into an appropriate length. Manufactured by If such an extruded material is employed, the fitting hole 26 and the through hole 28 can be formed simultaneously with the molding of the housing body 20.

On the other hand, each of the lids 22 has a thin annular plate shape, and has a flat shape corresponding to the axial end face of the housing body 20, and has one axial surface. A plurality of circular fitting projections 30 are integrally formed.
The lids 22 are connected to the housing body 2.
The fitting projections 30 are fixedly attached to the housing main body 20 by being superimposed on both end surfaces in the axial direction of 0 and press-fitted and fixed to the through holes 28 of the housing main body 20. Note that the lid 22 may be fixed to the housing main body 20 by bolts, welding, or the like. The lids 22 are formed of a hard material such as a metal material such as an aluminum alloy or steel or a synthetic resin material.

A pair of lids 22, 22 are assembled to the housing body 20, and both axial openings of the through holes 28 are covered with the lids 22, 22, respectively. In addition, a plurality of (in this embodiment, eight) accommodation cavities 14 partitioned from the external space are formed. In other words, these accommodation cavities 14 have peripheral walls defined by the inner peripheral surfaces of the through holes 28 of the housing 12 and the projecting distal end surfaces of the fitting projections 30, 30 of the lids 22, 22. .

Further, in each of the housing cavities 14 in the housing 12, a circular rod-shaped independent mass member 16 is housed and arranged. These independent mass members 16
Have the same structure and the same shape, and are composed of a metal mass 32 as a mass main body and a rubber elastic layer 34. The metal mass 32 is formed of a high specific gravity material such as steel, and has a solid circular rod shape that extends linearly with a circular cross section. A rubber elastic layer 34 is formed on the surface of the metal mass 32. The rubber elastic body layer 34 has a thin film shape having a substantially constant thickness dimension as a whole, and has a cylindrical tubular portion 36 that covers the outer peripheral surface of the metal mass 32 over the entire surface. An annular portion 38 is formed to cover each outer peripheral edge of both end surfaces in the axial direction.

Further, the independent mass member 16 has an outer surface shape slightly smaller than the accommodation space 14 and is accommodated and arranged in the accommodation space 14 in an independent state, that is, in a non-adhesive state with respect to the housing 12. ing. Thus, when the independent mass member 16 is positioned at the center of the accommodation space 14, a gap 40 is formed around the independent mass member 16. In particular, in the present embodiment, in order to reduce the impact sound of the independent mass member 16 against the housing 12 and to improve the vibration damping effect, the clearance dimension of the housing 12 in the direction perpendicular to the axis: 2δ is 2δ = 0.1. 0.8 mm, preferably 0.1 mm.
The gap (δ) is set to be 1 to 0.5 mm, and is half the size of the gap 40 over the entire circumference of the independent mass member 16 in a state where the independent mass member 16 is positioned at the center of the accommodation space 14. ) Is set to be formed at δ = 0.05 to 0.4 mm.

Thus, when the independent mass member 16 is relatively displaced in the direction perpendicular to the axis with respect to the housing 12, the outer peripheral surface of the independent mass member 16 moves in any direction perpendicular to the axis. The surface is relatively displaced by a displacement amount (relative amplitude of 2δ) corresponding to the dimension of the gap 40: 2δ with respect to the surface, and is brought into contact with the housing 12 by hitting.

The material of the rubber elastic layer 34 is not particularly limited, and various known rubber materials such as natural rubber, isoprene rubber, butadiene rubber, and styrene rubber can be used. In order to reduce the hardness, the Shore D hardness is set to 80 or less, and more preferably, the Shore D hardness is set to 20 to 40.

In the vibration damping device 10 as described above, the drive shaft 18 is press-fitted and fixed in the fitting hole 26 of the housing main body 20 and externally fitted and fixed to the drive shaft 18. 18 attached. When the vibration damping device 10 is mounted on the drive shaft 18, the vibration mode of the drive shaft 18 is taken into consideration, and the vibration is suppressed to the point where the amplitude becomes the largest when vibration to be damped is input (the point that becomes the antinode of the vibration mode). Shaking device 1
It is desirable to position 0.

In the vibration damping device 10 having such a structure, the plurality of independent mass members 16 extending parallel to the central axis 24 of the drive shaft 18
8 is disposed so as to be freely displaceable by a predetermined distance in any direction perpendicular to the axis within the accommodation space 14 of the housing 12 fixed to the drive shaft 8. When squeezed, the independent mass member jumps and displaces in the accommodation space, and the independent mass member 16 hits and abuts on the housing 12 in the vibration input direction.

In addition, when torsional vibration around the central shaft 24 is generated with respect to the drive shaft 18 due to transmission torque fluctuation or the like, the torsional vibration is generated by the central shaft 2.
4 is applied to the independent mass members 16 spaced outward in the direction perpendicular to the axis, as an exciting force in the direction perpendicular to the axis. Direction).

Accordingly, when the independent mass member 16 is brought into contact with the housing 12, the two members 12, 16 are brought into contact with each other.
Vibration energy in the drive shaft 18 is absorbed or attenuated by a collision action between the two or a sliding friction action caused by an elastic deformation of the rubber elastic layer 34, so that a vibration damping effect is exerted on the drive shaft 18. . Further, in such a vibration damping device 10, a vibration damping effect is exerted by utilizing an energy loss based on hitting of the housing 12 by the independent mass member 16 which is independently jumped and displaced with respect to the housing 12, Since it is not based on a clear resonance effect, the frequency dependence of the vibration damping effect is low, and an effective vibration damping effect can be exhibited for vibration in a wide frequency range.

Therefore, in the vibration damping device 10 as described above, the independent mass member 16 is provided for both the vibration in the direction perpendicular to the axis of the drive shaft 18 and the vibration (torsional vibration) in the rotational direction of the drive shaft 18. This exerts a vibration damping effect based on contact of the housing 12 with the housing 12. In particular, even when the axial perpendicular vibration and the torsional vibration are problematic in different frequency ranges, both are effective against both vibrations. The effect of damping can be obtained.

Further, in the vibration damping device 10, in addition to the fact that the vibration damping effect is not based on a clear resonance effect, the rubber elastic layer 34 forming the contact surface of the independent mass member 16 is attached to the housing 12. Since the independent mass member 16 is not fixed and is arranged independently of the housing 12, the influence of the spring characteristic of the independent mass member 16 on the vibration damping characteristics is small, and therefore, the rubber elastic body accompanying the temperature change or the like The influence on the vibration damping characteristics due to the change in the elastic characteristics of the layer 34 is suppressed,
There is an advantage that the intended damping effect can be obtained stably.

Further, the independent mass member 16 and the housing 1
2 is elastically abutted through the rubber elastic layer 34, so that the generation of collision noise due to the abutment can be reduced.

In the vibration damping device 10 of this embodiment, the independent mass members 16 are displaced outward in the direction perpendicular to the axis by centrifugal force by the rotation of the housing 12 integrally with the drive shaft 18. Although being pressed against the housing 12, the acting force exerted on the housing 12 due to the centrifugal force is mutually canceled around the central axis 24, and the center of gravity of each independent mass member 16 is Since it is located on the upper side, the bending force exerted on the drive shaft 18 is reduced or avoided, so that a stable rotation state can be maintained also in the drive shaft 18.

Further, in the vibration damping device 10 of the present embodiment, the outer peripheral surface shape of each independent mass member 16 and the inner wall surface shape of each accommodation space 14 are both cylindrical, Since the rotation of the independent mass member 16 about the central axis in the cavity 14 is allowed, the rubber elastic layer 34 is prevented from being repeatedly hit at an extreme position, and excellent durability can be exhibited.

FIGS. 3 and 4 show a drive shaft damping device 42 according to a second embodiment of the present invention. In the present embodiment, members and portions having the same structure as the first embodiment are denoted by the same reference numerals as those in the first embodiment in the drawings, and their detailed descriptions are given. Description is omitted.

That is, in the vibration damping device 42 of this embodiment, the housing 43 is formed using the drive shaft 18, and the drive shaft 18 and the outer peripheral housing member 44 constitute the housing 43. The outer peripheral housing member 44 includes a cylindrical wall portion 46 having a cylindrical shape. A pair of annular end wall portions 48, which extend radially inward, are provided at both axial ends of the cylindrical wall portion 46.
48 are integrally formed in the shape of an annular plate. The inner peripheral edges of the annular end walls 48, 48 are curved, and are integrally formed with small-diameter cylindrical fitting cylinders 50, 50 extending outward in the axial direction.

Further, a plurality (four in the present embodiment) of partition walls 52 are integrally formed on the cylindrical wall 46 so as to protrude radially inward. The partition wall portion 52 projects radially inward from the cylindrical wall portion at a height smaller than that of the annular end wall portion 48, and is arranged at regular intervals in the circumferential direction.

Then, the outer peripheral housing member 44
Is externally inserted with respect to the drive shaft 18, and is fixedly attached to the outer peripheral surface of the drive shaft 18 by fitting a pair of fitting cylinder portions 50. In addition, the drive shaft 18 is similar to the first embodiment.
It has a hollow or solid circular cross section and a straight central axis 24.
Is a rotary member that is driven to rotate around the rotation. Also,
In such a mounted state, the partition wall portion 52 is positioned so as to protrude toward the drive shaft 18 from the cylindrical wall portion 46 of the outer peripheral housing member 44, and the protruding tip surface faces the outer peripheral surface of the drive shaft 18. It is located.

As a result, the inner peripheral opening of the outer housing member 44 is covered with the drive shaft 18, and the housing space 54 partitioned from the external space between the outer peripheral surface of the drive shaft 18 and the outer housing member 44. Are formed. In short, in the present embodiment, a part of the housing 43 is configured using the drive shaft 18. Further, the accommodation space 54 thus formed is
Is divided into a plurality of areas (4 in this embodiment) by the partition wall 52.
Thus, a plurality of divided cavities 56 extending in a circular arc shape in the circumferential direction between the drive shaft 18 and the radially opposed surfaces of the outer peripheral housing member 44 are formed. The drive shaft 18 and the outer peripheral housing member 44 constituting the housing 43 are both formed of a rigid material having an elastic modulus of 5 × 10 ⁴ MPa or more.

Then, for each of these divided spaces 56,
An independent mass member 58 having an outer surface shape slightly smaller than the inner wall shape is accommodated and arranged. The independent mass member 58 is also formed of a metal mass 60 made of a high specific gravity material and a rubber elastic layer 62 covering the entire surface, as in the first embodiment. Thus,
When the independent mass member 58 is located at the center of the divided space 56, a gap 64 is formed around the entirety of the independent mass member 58. In particular,
The independent mass member 58 has inner and outer peripheral surfaces in the shape of an arcuate curved surface and flat end surfaces in the circumferential direction extending in a direction perpendicular to the axis. The independent mass member 58 is positioned at the center of the divided space 56. In this state, the inner peripheral surface is radially separated from the outer peripheral surface of the drive shaft 18 so as to face the outer peripheral surface of the drive shaft 18, and the outer peripheral surface thereof It is designed to be spaced apart in the radial direction and to be opposed to each other. Further, both end surfaces in the circumferential direction are opposed to the partition wall portion 52 of the outer peripheral housing member 44 so as to be spaced apart in the circumferential direction.

In the vibration damping device 42 of this embodiment having such a structure, the center shaft 2 of the drive shaft 18 is also provided.
A plurality of independent mass members 58 extending in parallel to 4 are disposed in the accommodation space 54 of the housing 43 fixedly provided on the drive shaft 18 so as to be freely displaceable by a predetermined distance in any direction perpendicular to the axis. When vibration in the direction perpendicular to the axis or vibration in the circumferential direction is generated with respect to the drive shaft 18, the independent mass member 58 is accommodated in the accommodation space 54.
Jumps and displaces, and the independent mass member 58
3, that is, the drive shaft 18 or the outer peripheral housing member 44 is hit against and hit in the vibration input direction.

Therefore, in such a vibration damping device 42,
As in the first embodiment, based on the impact action of the independent mass member 58 on the housing 43, any effective vibration damping effect can be provided for bending vibration in the direction perpendicular to the axis and torsional vibration around the central axis. You can get it.

Further, FIGS. 5 and 6 show a multi-groove V-groove pulley 66 provided with a vibration damping device, which is used in an automobile or the like, as a third embodiment of the present invention. In the present embodiment, members and portions having the same structure as the first embodiment are denoted by the same reference numerals as those in the first embodiment in the drawings, and their detailed descriptions are given. Description is omitted.

That is, the multi-groove V-groove pulley 66 has a structure in which independent mass members 72 are disposed in accommodating cavities 70 formed in the pulley main body 68, respectively. It is designed to be mounted by inserting and fixing.

More specifically, the pulley body 68 includes a small-diameter cylindrical boss 74 and a large-diameter cylindrical rim 76.
The boss portions 74 are arranged radially apart from each other on the same rotation center shaft 78 and are connected to each other by a ring-shaped connecting portion 80 extending between the diametrically opposed surfaces of the boss portion 74 and the rim portion 76. And the rim portion 76 are integrally connected. A fitting hole 81 penetrating in the axial direction is formed in a central portion of the boss 74, and a key groove 82 extending in the axial direction is engraved on the inner peripheral surface of the boss 74. I have. Thus, the pulley main body 68 is externally mounted on a rotating shaft (not shown), and is mounted so as to be relatively non-rotatable by a key fitted into the key groove 82. A multi-groove V-groove extending continuously in the circumferential direction is engraved on the outer peripheral surface of the rim portion 76, so that a multi-groove V-groove belt (not shown) can be wound therearound. As a result, the pulley main body 68 transmits a rotational driving force between the rotation shaft on which the boss 74 is mounted and the V-groove belt wound around the rim 76. The pulley body 68 is formed of a rigid material having an elastic modulus of 5 × 10 ⁴ MPa or more. For example, the pulley body 68 is formed of an aluminum alloy or a steel material.

Further, the pulley body 68 has a plurality of through holes 84 in the rim portion 76 (12 in the present embodiment) at equal intervals in the circumferential direction around the rotation center axis 78 in the rim portion 76. Is formed. These through holes 84
Are formed in the same shape as each other, and are each formed linearly in parallel with the rotation center axis 78 with a circular constant cross-sectional shape. That is, the pulley main body 68 in which these through holes 84 are formed is rotationally balanced so that the center of gravity axis is located on the rotation center axis 78.

Further, lids 86, 86 are respectively attached to the openings on both sides in the axial direction of each through hole 84. The lid 86 has a thin disk shape, and has an outer diameter slightly larger than the cross section of the through hole 84. The lid 86 is press-fitted and fixed at both end faces of the pulley main body 68 into circular fitting recesses 88 formed at both axial openings of the through holes 84. Note that these lids 86, 86 are formed of a hard material such as a metal material such as an aluminum alloy or steel or a synthetic resin material.

The rim portion 7 of the pulley body 68 is covered by the openings 86 on both sides of the through hole 84 of the pulley body 68 as described above.
A plurality (12 in the present embodiment) of accommodation cavities 70 partitioned from the external space are formed inside the interior 6. That is,
These accommodation cavities 70 are provided with through holes 84 of the pulley body 68.
A peripheral wall surface is defined by the inner peripheral surface of the cover and the axial end surfaces 90, 90 of the lids 86, 86. Also, as is apparent from this, in the present embodiment, the pulley body 6
A housing 67 is formed by the cover 8 and the cover 86.

Further, in each of the accommodation spaces 70 in the housing 67, a circular rod-shaped independent mass member 72 is accommodated and arranged. These independent mass members 72
Have the same structure and the same shape, and are composed of a metal mass 92 as a mass body and a rubber elastic layer 94. The metal mass 92 and the rubber elastic layer 94
The same material as that of the first embodiment is adopted as the material of the first embodiment. A rubber elastic layer 94 is formed on the surface of the metal mass 92. The rubber elastic body layer 94 has a thin film shape having a substantially constant thickness dimension as a whole, and has a cylindrical tubular portion 96 that covers the outer peripheral surface of the metal mass 92 over the entire surface. An annular portion 98 is formed to cover each outer peripheral edge of both axial end surfaces.

Further, the independent mass member 72 has an outer surface shape slightly smaller than the accommodation space 70, and is independent of the accommodation space 70, that is, the pulley body 68 and the lid as the housing 67. 86 are accommodated and arranged in a non-adhesive state. Thus, the independent mass member 72 is stored in the accommodation space 7.
0, the independent mass member 72
Is formed so as to extend over the entire circumference. In particular, between the outer peripheral surface of the independent mass member 72 and the radially opposed surface of the inner peripheral wall surface of the storage space 70, a cylindrical gap 99 extending at a constant gap: δ over the entire circumference is formed. ing. Note that the size of the gap: δ is set to δ = 0.05 to 0.4 mm, as in the first embodiment.

Thus, in the V-pulley 66 of the present embodiment, a plurality of independent mass members 72 extending in parallel with the central axis 78 of the V-pulley 66 in any of the housing cavities 70 formed by the pulley body 68 It is disposed so as to be freely displaceable by a predetermined distance also in the direction perpendicular to the axis, and when vibration in the direction perpendicular to the axis or vibration in the circumferential direction is generated with respect to the V pulley 66, the vibration is generated in the accommodation space 70. Independent mass member 7
2, the independent mass member 72 hits and comes into contact with the pulley main body 68 in the vibration input direction.

Therefore, the V-pulley 66 serving as the vibration damping device is used.
In the same manner as in the first embodiment, the independent mass member 7
2 based on a striking action or the like on the pulley body 68
An effective vibration damping effect can be obtained with respect to the bending vibration in the direction perpendicular to the axis of the pulley 66 itself, the rotating shaft on which the V-pulley 66 is mounted, and the like, and the torsional vibration around the central axis.

The V-pulley 6 having the structure described above
6, boss portions 7 on the input and output sides of the driving force
4 and the rim portion 76 are maintained in a state of being integrally connected by the connecting portion 80, and the driving force transmission path is not divided for assembling the independent mass member 72. It can exhibit the force transmission performance, and the assembling of the independent mass members may adversely affect the transmission performance and durability.

Further, FIGS. 7 and 8 show a gear member 100 as a vibration damping device used in an automobile or the like as a fourth embodiment of the present invention. In the present embodiment, members and portions having the same structure as the third embodiment are denoted by the same reference numerals as those in the third embodiment in the drawings, and their detailed descriptions are given. Description is omitted.

That is, the gear member 100 of the present embodiment
Has a structure in which a plurality of storage cavities 104 are formed in a gear main body 102 formed of a rigid material such as steel, and an independent mass member 106 is disposed in each of the storage cavities 104. .

More specifically, the gear body 102 is formed of a rigid material such as steel, and has a disk shape as a whole. A fitting hole 108 penetrating in the axial direction is formed in a central portion of the gear main body 102, and a key groove 109 extending in the axial direction is formed in an inner peripheral surface of the gear main body 102.
Is engraved. With them, the gear body 102
The key is inserted into the key groove 109 by being extrapolated to a rotation shaft (not shown) and is mounted so as to be relatively non-rotatable. Also, on the outer peripheral edge of the gear body 102,
Gear teeth 110 are formed over the entire circumference in the circumferential direction,
A timing belt or the like (not shown) wound around the outer peripheral surface is wound and meshed. The gear main body 102 transmits a rotational driving force between a rotation shaft on which the boss portion 112 is mounted and a timing belt wound around the outer peripheral surface 114.
A plurality of lightening holes 116 penetrating in the axial direction are formed in a radially intermediate portion of the gear main body 102, so that the weight of the entire gear member 100 is reduced.

A plurality of (12 in this embodiment) storage cavities 104 are formed in the outer peripheral portion of the gear body 102 in the same manner as in the third embodiment, and each of these storage cavities 104 is formed. For the space 104, the independent mass member 1
06 are disposed so as to be independently displaceable. Further, each independent mass member 106 has an outer surface shape that is slightly smaller than the inner wall surface of the accommodation space 104, and when positioned at the central portion of the accommodation space 104, all of the independent mass members 106 A clearance 99 is formed in the periphery, and a predetermined displacement can be made relative to each other in the accommodation space 104. As is apparent from this, in the present embodiment, the housing 101 is constituted by the gear body 102 and the lid 86.

Therefore, in the gear member 100 of the present embodiment, as in the third embodiment, the independent mass member 106
Are effective against bending vibration in the direction perpendicular to the axis of the gear member 100 itself, a rotating shaft on which the gear member 100 is mounted, and torsional vibration around the center axis, based on the impact action on the gear body 102. It is possible to obtain a great damping effect.

In the gear member 100,
Since the driving force transmission path is not interrupted for assembling the independent mass member 106, excellent driving force transmission performance and durability can be exhibited.

FIGS. 9 to 10 show a pulley 118 as a vibration damping device used in an automobile or the like as a fifth embodiment of the present invention. In the present embodiment, parts and portions having the same structure as the third embodiment are denoted by the same reference numerals as those in the third embodiment in the drawings, and their details are described. Detailed description is omitted.

That is, in the pulley 118 of this embodiment, a plurality of storage cavities 122 are formed in a pulley main body 120 formed of a rigid material such as steel, and each of the storage cavities 122 has an independent mass member. 124 is accommodated and arranged.

More specifically, the pulley main body 120 is formed of a rigid material such as steel, and has a disk shape as a whole. Further, a fitting hole 126 penetrating in the axial direction is formed in a central portion of the pulley main body 120, and a key groove 127 extending in the axial direction is formed in an inner peripheral surface of the pulley main body 120.
Is engraved. With them, the pulley body 120
The key is inserted into the key groove 127 by being extrapolated to a rotating shaft (not shown) and is mounted so as to be relatively non-rotatable. Further, a V groove 128 extending continuously over the entire circumference in the circumferential direction is formed on the outer peripheral surface of the pulley main body 120, and the V belt is wound around the outer peripheral surface. The pulley body 120 is provided with the boss 1
The rotation driving force is transmitted between the rotation shaft on which the motor 30 is mounted and the V-belt wound around the outer peripheral surface 132.

A plurality (four in the present embodiment) of receiving cavities 122 are formed in the radially intermediate portion of the pulley main body 120 in the same manner as in the third embodiment. An independent mass member 124 is accommodated and arranged in each accommodation space 122 so as to be independently displaceable.
Further, each independent mass member 124 has an outer surface shape slightly smaller than the inner wall surface of the accommodation space 122, and when positioned at the central portion of the accommodation space 122, all the independent mass members 124 A gap is formed in the periphery, and the housing space 122 is relatively displaceable by a predetermined amount. Also, as is clear from this,
In the present embodiment, the housing 119 is constituted by the pulley main body 120 and the lid 86.

Therefore, in the pulley 118 of this embodiment, as in the third embodiment, the pulley 11 is formed based on the impact of the independent mass member 124 on the pulley body 120 and the like.
An effective vibration damping effect can be obtained with respect to bending vibration in the direction perpendicular to the axis of the shaft 8 or the rotating shaft on which the pulley 118 is mounted, and torsional vibration around the central axis.

Further, in the pulley 118, since the driving force transmission path is not divided because the independent mass member 122 is assembled, excellent driving force transmission performance and durability can be exhibited.

Although the embodiments of the present invention have been described in detail, these are merely examples, and the present invention
By the specific description in these embodiments,
It is not to be construed as limiting.

For example, in each of the above embodiments, the vibration damping effect on the vibration in the direction perpendicular to the rotation center axis and the vibration in the circumferential direction around the rotation center axis has been described. Similarly, it is possible to obtain an effective vibration damping effect on the vibration in the axial direction along with the impact action of the independent mass member on the housing.

Further, in each of the above embodiments, a plurality of independent mass members arranged independently in the circumferential direction are employed. However, they may be connected in the circumferential direction to be integrated. is there. Specifically, for example, in the vibration damping device shown in FIGS. 3 and 4, each of the independent mass members 58 is formed so that the inner peripheral edge portion thereof extends around the partition wall portion 52 of the outer peripheral housing member 44 and the opposing surface of the drive shaft 18. It is also possible to integrally connect each other by a rigid connecting portion extending in the direction, thereby forming an annular integral independent mass member. Alternatively, in the first to fifth embodiments, each independent mass member is connected to each other at any one of the axial ends to form a single rigid independent mass member which is integrally displaced. May be.

Further, in each of the above embodiments, the shape of the outer surface of the independent mass member and the shape of the inner wall surface of the housing are similar to each other. Whatever is realized,
For example, in the first embodiment and the third to fifth embodiments, the shape of the inner wall surface of the housing has a rectangular cross-sectional shape as a flat surface shape that spreads substantially in the radial direction, while the independent mass portion having the circular cross-sectional shape remains as it is. It is also possible that the displacement of the independent mass member in the circumferential direction with respect to the housing and the circumferential contact with the housing can be more positively generated, thereby improving the vibration damping effect in the circumferential direction. obtain.

Further, in each of the above-described embodiments, a closed structure in which the area where the independent mass members are provided is partitioned from the external space is not necessarily required.

In addition, in the above embodiment, a specific example in which the present invention is applied to a vibration damping device for an automobile has been described. However, the present invention is also applicable to a rotating member used for various vehicles other than an automobile. It goes without saying that it is widely applicable as a vibration damping device.

In addition, although not enumerated one by one, the present invention
Based on the knowledge of those skilled in the art, various changes, modifications, improvements, and the like can be made, and unless such embodiments depart from the spirit of the present invention.
Both are included in the scope of the present invention,
Of course.

[0076]

As is apparent from the above description, in the vibration damping device having the structure according to the present invention, the vibration damping effect based on the contact of the independent mass member with the housing is exhibited over a wide frequency range. At the same time, it is possible to obtain an effective vibration damping effect for any vibration in the direction perpendicular to the axis of the rotating member and in the rotating direction.

[Brief description of the drawings]

FIG. 1 is a cross-sectional view showing a vibration damping device for a drive shaft of an automobile as a first embodiment of the present invention, and FIG.
FIG. 3 is a view corresponding to the II section in FIG.

FIG. 2 is a sectional view taken along line II-II in FIG.

FIG. 3 is a cross-sectional view showing a vibration damping device for a drive shaft of an automobile according to a second embodiment of the present invention.
FIG. 3 is a view corresponding to a III-III section in FIG.

FIG. 4 is a sectional view taken along line IV-IV in FIG.

FIG. 5 is a cross-sectional view showing a multi-groove V-groove pulley provided with a vibration damping device used for an automobile or the like as a third embodiment of the present invention, and is a view corresponding to a VV cross section in FIG. It is.

6 is a sectional view taken along line VI-VI in FIG.

FIG. 7 is a cross-sectional view showing a gear member as a vibration damping device used in an automobile or the like as a fourth embodiment of the present invention, and is a view corresponding to a VII-VII cross section in FIG.

8 is a sectional view taken along line VIII-VIII in FIG.

FIG. 9 shows a pulley as a vibration damping device used in an automobile or the like according to a fifth embodiment of the present invention.
It is a IX sectional view.

FIG. 10 is a sectional view taken along line XX in FIG. 9;

[Explanation of symbols]

 10, 42 Drive shaft vibration suppression device 12, 43, 67, 101, 119 Housing 16, 58, 72, 106, 124 Independent mass member 18 Drive shaft 24 Central axis 66 Multi-groove V-groove pulley 78 Rotation central axis 100 Gear member 118 pulley

Claims (13)

[Claims] A rigid housing is fixedly provided on a rotating member that rotates about a central axis, and an independent mass member is assembled to the housing in a non-adhesive manner so as to be relatively displaceable, so that a circumferential direction around the central axis is provided. A vibration damping device for a vehicle, characterized in that the independent mass member and the housing are opposed to each other so as to be elastically contactable with each other. 2. The vibration damping device for a vehicle according to claim 1, wherein a center of gravity of the independent mass member as a whole is positioned on a rotation center axis of the rotating member when the rotating member is in a rotating state. . 3. A plurality of independent mass members are provided independently of each other, and each of the independent mass members elastically elastically extends in the circumferential direction around the central axis with respect to the housing at both ends in the circumferential direction. 3. The vibration damping device for a vehicle according to claim 1, wherein the vibration damping device is in contact with the vehicle. 4. The independent mass member according to claim 3, wherein the independent mass member has an arc-shaped cross section extending in a predetermined length in a circumferential direction around the central axis, and has an arc-shaped block shape extending parallel to the central axis. Vehicle damping device. 5. The vibration damping device for a vehicle according to claim 3, wherein the independent mass member has a circular cross section and has a circular cross section and extends parallel to the central axis. 6. The independent mass member is constituted by an annular mass member which is circumferentially continuous around the central axis, and an engagement recess is provided in one of the annular mass member and the housing, and the other is provided. The vibration damping device for a vehicle according to claim 1 or 2, wherein an engagement convex portion is provided on the vehicle, and the engagement concave portion and the engagement convex portion are brought into contact with each other around the central axis. 7. The vehicle vibration damping device according to claim 1, wherein at least a part of the housing is configured using the rotating member. 8. The rotating member is constituted by a rotating disk for transmitting driving force, which extends outward in a direction perpendicular to the axis from the center axis, and the independent mass member is provided at a radially intermediate portion of the rotating disk. The vehicle vibration damping device according to claim 1, wherein the assembled housing is fixedly provided. 9. The independent mass member includes a mass main body made of a metal material, and an elastic material layer is formed on a contact surface of at least one of the mass main body and the housing. The vibration damping device for a vehicle according to any one of the above. 10. The housing according to claim 1, wherein an inner space is formed in the housing, the inner space being substantially blocked from an outer space, and the independent mass member is accommodated in the inner space. A vibration damping device for a vehicle according to any one of the claims. 11. The vehicle vibration damping device according to claim 1, wherein a contact surface of at least one of the independent mass member and the housing has a Shore D hardness of 80 or less. 12. The vibration damping device for a vehicle according to claim 1, wherein a gap dimension between the independent mass member and the facing surface of the housing is 0.1 to 0.8 mm. 13. The vehicle vibration damping device according to claim 1, wherein a total mass of the independent mass member is 5 to 10% of a mass of the vibration member including the rotating member.