JP2002286089A - Damping device for vehicle - Google Patents

Abstract

PROBLEM TO BE SOLVED: To provide a damping device for a vehicle having a novel structure capable of obtaining effective damping effects against vibration of a plurality of or wide frequency bands on the basis of the contact of an independent mass member with a housing. SOLUTION: A circular or a cylindrical mass member 14 formed from a substantially unit member with respect to a rod-shaped vibratory member 12 is externally inserted in a vibratory member 12 and brought into direct and elastic contact with the mass member 14 at a plurality of contact positions 22a, 22b, and the contact conditions to the vibratory member 12 in the plurality of contact conditions 22a, 22b axially isolated are made different from each other.

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 a vehicle mounted on a vibration member of a vehicle to reduce vibration of the vibration member, and for example, a suspension member of an automobile, a subframe, a body panel, an engine unit, a mount bracket, The present invention relates to a vehicle damping device having a novel structure that can exhibit an effective damping effect by being applied to a vibration member such as an exhaust system member.

[0002]

2. Description of the Related Art Conventionally, as a method of reducing vibration which is a problem in a vehicle such as an automobile, a mass damper for fixing a mass material to a vibration member or a dynamic method of connecting and supporting a mass material to a vibration member via a spring material is known. Dampers, and
A vibration damping material in which a sheet-like elastic material is adhered to a surface of a vibration member is known. However, both the mass damper and the dynamic damper require a large mass of mass material and have a problem that the frequency range in which an effective vibration damping effect is exhibited is narrow. In addition, the above-mentioned vibration damping material has a problem that a large attaching area is required and the weight increases. Further, the dynamic damper and the vibration damping material have a problem that it is difficult to stably obtain a target vibration damping effect because the temperature dependency of the vibration damping effect is high.

[0003] Accordingly, the present applicant has previously described the international publication WO
In Japanese Patent Application Publication No. 00/14429, an independent mass member is disposed in a non-adhesive manner relative to a housing fixed to a vibration member so as to be relatively displaceable with a gap therebetween. We propose a new structure of a vehicle damping device with a new structure that uses a sliding friction at the time of contact and energy loss due to collision to achieve a damping effect by making contact with an elastic contact surface. did. In the vehicle vibration damping device having such a structure, an effective vibration damping effect with respect to vibration over a wide frequency range can be obtained with a small mass mass.

Incidentally, as a result of further studies by the present inventors, in the vehicle vibration damping device described in WO 00/14429, the mass of the independent mass member and the vibration It has been confirmed that by adjusting the spring stiffness of the elastic material constituting the contact portion of the member, the vibration damping effect of the vibration member on vibration in a specific frequency range can be significantly improved. In addition, such a phenomenon,
Examination of the frequency characteristics and the like of the vibration suppression effect suggests that the relative displacement of the independent mass member accompanying the contact with the vibrating member may be based on exerting a resonance action.

However, when tuning the frequency range in which the vibration-proof effect based on the resonance action of the independent mass member is exerted to the vibration frequency range in which vibration is to be prevented, the size of the independent mass member is limited by the size of the installation space or the like. Conditions are often limited by the conditions, and the reduction in spring stiffness of the elastic material forming the contact portion between the independent mass member and the vibration member is often limited by conditions such as durability. There is a problem that is limited. In particular, if there is a vibration frequency to be damped in a low frequency range where a large mass of the independent mass member or a low spring constant of the elastic material constituting the contact portion is required, the vibration frequency range to be damped is used. Tuning was difficult, and it was difficult to obtain a sufficient damping effect.

Further, even when the frequency range in which the vibration damping effect based on the resonance action of the independent mass member is exhibited is tuned to the vibration frequency range to be damped, the frequency range in which the effective vibration damping effect is exhibited. In some cases, it is difficult to obtain an effective vibration damping effect for vibrations in a vibration frequency range in which vibrations should be prevented.

[0007]

Here, the present invention has been made in view of the above-mentioned circumstances, and an object of the present invention is to provide a plurality of objects based on contact of an independent mass member with a housing. An object of the present invention is to provide a vehicle vibration damping device having a novel structure capable of obtaining an effective vibration damping effect for vibrations in a wide frequency range.

[0008]

An embodiment of the present invention which has been made to solve such a problem will be described below. The components employed in each of the embodiments described below can be employed in any combination as possible. In addition, aspects or 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 the invention ideas that can be understood by those skilled in the art from the descriptions. It should be understood that it is recognized on the basis of.

That is, the features of the present invention are as follows:
In a vibration damping device for a vehicle, a mass member is disposed so as to be independently displaceable without adhesion to a vibration member so that the mass member can be directly and elastically contacted with the vibration member. The vibrating member has a rod shape, and the mass member formed of a substantially rigid single member as a whole has a cylindrical or annular shape. In one input direction, the mass member can be directly and elastically contacted with the vibration member at a plurality of contact points axially separated from each other, and further, the plurality of contact members separated in the axial direction. This is because the contact conditions of the mass member at the location with the vibration member are different from each other.

In the vibration damping device having the structure according to the present invention, since the mass member is brought into contact with the vibration member at a plurality of contact points under different contact conditions,
The mass member is in an uncoupled vibration state, and it is possible to set a plurality of natural frequencies different from each other for a single mass member. In several regions, the mass member can be efficiently jumped and displaced with respect to the vibration member.

Therefore, in such a vibration damping device, the vibration damping effect exerted on the basis of the hitting (contact) action of the mass member on the vibration member is obtained in a plurality of natural frequency ranges of the mass member. Therefore, it is possible to obtain an advantageous effect by utilizing the resonance action. Therefore, a vibration damping device capable of exhibiting an effective vibration damping effect with respect to a plurality of vibrations in a wide or wide frequency range is compact as a whole. It can be realized with a small size.

In the vibration damping device for a vehicle having the structure according to the present invention, the mass member is formed in an annular or cylindrical shape and is externally arranged on the rod-shaped vibration member. On the other hand, the contact portion of the mass member can be easily formed with a simple structure, and there is no need to specially form a large housing or the like that covers the mass member. Can be advantageously employed in the case of a rod shape, whereby the intended vibration damping device can be realized with a more compact and simple structure.

In the present invention, the shape of the vibrating member and the shape of the mass member are not particularly limited. For example, a vibrating member having a solid rod structure, a hollow pipe structure, or a circular or polygonal cross section may be used. It is also possible to adopt.
Further, the material of the mass member is not particularly limited, but a metal material such as steel is preferably employed in order to advantageously secure the mass of the mass member in a compact size. Furthermore, in the present invention, it is desirable that the plurality of contact points separated in the axial direction be separated as much as possible in order to stabilize the vibration state of the mass member.

In the present invention, at least one of the plurality of contact portions separated in the axial direction is formed in an annular or cylindrical shape extending continuously in the circumferential direction of the mass member. , May be advantageously employed. By employing the contact portion extending continuously in the circumferential direction, the contact state of the mass member with respect to the vibration member can be made substantially constant in any direction perpendicular to the axis of the mass member. Therefore, even when the relative position of the mass member to the vibrating member changes in the circumferential direction, the intended vibration damping effect can be stably obtained, and the mass can be suppressed even in the vibration in the direction perpendicular to the axis. A vibration damping effect based on the contact of the member with the vibration member can be similarly obtained.

Further, in the present invention, at a plurality of abutting locations provided in the axial direction, for example, at least one of the abutting locations is disposed on an opposing surface of the vibration member and the mass member in a direction perpendicular to the axis. A compression elastic body that is provided and is compressed and deformed by the contact of the mass member with the vibration member;
Advantageously, or at least one of them can be advantageously formed by an elastic body which is sheared by a load in the abutment direction. In particular, as in the former case, by forming the contact portion by the compression elastic body, it becomes easy to tune the natural frequency of the mass member to a high frequency range by setting a large spring constant at the contact portion, As in the latter case, by forming the contact portion with an elastic body that is subjected to shear deformation, it is easy to set the spring constant at the contact portion to a small value and tune the natural frequency of the mass member to a low frequency range. As the compression elastic body or the elastic body that can be sheared, a rubber elastic body, an elastomer, or a foamed body thereof is preferably used.

In addition, as in the latter case, in particular, the elastic body which is sheared by an abutting load is provided with, for example, a cylindrical abutting portion extending outward from both sides of the mass member in the axial direction. By forming a contact portion of the mass member with the vibrating member by the shape contact portion, the mass member can be advantageously realized, or a through hole is formed in the mass member to form the contact portion. By arranging the elastic body forming in the through hole, the elastic body can be advantageously formed. When such a through-hole is employed, a proper length in the circumferential direction of the mass member, or a plurality of pieces on the circumference of the mass member are used so that the relative displacement of the mass member with respect to the vibration member is stably generated. It is desirable to form a through hole at a location.

Further, in the present invention, the contact conditions of the mass member with respect to the vibration member at the plurality of contact points are different from each other. For example, (a) when the vibration input direction is substantially vertical The configuration in which the abutment condition of the mass member with respect to the housing is made different from each other by making the shared support loads in the direction perpendicular to the axis of the mass of the mass member by the vibrating member at a plurality of abutting portions separated in the axial direction different from each other. (B) a configuration in which the contact conditions of the mass member with respect to the housing are made different from each other by making spring constants different at a plurality of abutting portions of the vibration member in the axial direction with respect to the mass member;
(C) A configuration in which the contact conditions of the mass member with respect to the housing are made different from each other by making the spring constants at the plurality of contact portions of the mass member different from each other with respect to the vibration member can be adopted.

Further, in the present invention, it is desirable to provide a stopper for limiting the relative displacement of the mass member with respect to the vibration member in the axial direction, whereby the state of contact of the mass member with the vibration member can be stabilized. Becomes
Further stabilization of the vibration damping effect exerted based on the striking (contact) of the mass member with the vibration member can be achieved.

Further, in the present invention, it is desirable to set the mass of the simple substance in the mass member to 10 to 1000 g, and more preferably to 50 to 500 g. That is, by setting the mass of the mass member alone to 1000 g or less, more preferably 500 g or less, the displacement of the mass member at the time of vibration input can be easily or efficiently generated, so that it is 10 g or more, more preferably 50 g or more.
By setting g or more, a more effective vibration damping effect can be obtained based on the contact of the mass member with the vibration member.

Further, in the present invention, the mass member is brought into contact with the vibrating member on both sides in the vibration input direction, and the mass member is held between the contact portions on both sides in the vibration input direction. The reciprocating movable distance is desirably 0.1 to 1.6 mm in the vibration input direction,
More preferably, the reciprocating movable distance is 0.1 to 1.0 m.
m. By setting such a small movable range, the mass member can be easily brought into contact with the vibrating member on both sides in the vibration input direction even with the vibration of the vehicle having a small amplitude, and a more excellent vibration damping effect is obtained. It becomes possible.

Further, in the present invention, in order to advantageously reduce the contact noise and effectively obtain the vibration damping effect, at least all the elastic contact portions between the vibration member and the mass member have at least the vibration member and the mass member. ASTM standard D on one contact surface
The Shore D hardness of 2240 is preferably set to 80 or less, more preferably 20 to 40. In addition, the contact portion between the mass member and the vibration member preferably has a compression elastic modulus of 1 to 10 ⁴ MPa in order to reduce the contact sound and improve the vibration damping effect.
More preferably, the loss tangent (tan) is 1 to 10 ³ MPa.
δ) is preferably 10 ⁻³ or more, more preferably 0.01
To 10.

Furthermore, in the present invention, it is desirable that the mass of the mass member is set to be 5 to 10% of the mass of the vibration member. If the mass of the mass member is less than 5% of the mass of the vibrating member, it may be difficult to obtain an effective vibration damping effect. On the other hand, if it exceeds 10%, the weight of the entire apparatus becomes a problem. Because. When a plurality of vehicle vibration suppression devices are mounted on the vibration member, the total mass of all mass members is 5 to 10% of the mass of the vibration member.
It is desirable to set so that

[0023]

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.

First, FIGS. 1 and 2 show a vibration damping device 10 as a first embodiment of the present invention. This vibration damping device 10 has a rod-shaped arm 12 as a vibration member used in various devices of a vehicle such as a suspension device.
A mass member 1 having a thick cylindrical shape as a whole
4 is extrapolated and arranged.

More specifically, the arm 12 is constituted by a solid rod-shaped member having a circular cross section.
Are externally fitted and fixed to each other in the axial direction by any method such as press-fitting and welding. Each abutment 16 has an annular shape having a substantially constant thickness and extending continuously in the circumferential direction, and extends over the entire circumference of the arm 12 in the circumferential direction.
At a substantially constant height from the outer peripheral surface of the main body. In the present embodiment, the contact fittings 16, 16
Have substantially the same shape and size.

On the other hand, the mass member 14 is constituted by a mass fitting 18 having a thick cylindrical shape, and contact rubber elastic bodies 22a and 22b attached to the mass fitting 18. The mass metal fitting 18 has an inner diameter larger than the outer diameter of the contact metal fittings 16, 16 protruding from the outer peripheral surface of the arm 12, and has a substantially constant rectangular cross-section and is continuous in the circumferential direction. A pair of extending concave grooves 20, 20 are provided so as to open on the inner peripheral surface. Also, the contact rubber elastic bodies 22a, 22b
Is formed in an annular shape extending in the circumferential direction with a rectangular cross section substantially the same as the cross sectional shape of the concave grooves 20, 20.
In the state where 2a and 22b are fitted in the concave grooves 20 and 20, respectively, the axial both end surfaces and the outer peripheral surfaces of the contact rubber elastic bodies 22a and 22b are moved with respect to the bottom surface and the side wall surface of the concave grooves 20 and 20, respectively. It has been vulcanized. Thus, cell 18
The contact rubber elastic bodies 22a, 22b vulcanized and bonded to the concave grooves 20, 20 are set such that the inner peripheral surface thereof is substantially flush with the inner peripheral surface of the mass metal fitting 18. Further, the axial lengths of the contact rubber elastic bodies 22a and 22b are sufficiently larger than the axial lengths of the contact fittings 16 and 16, respectively.

The contact rubber elastic bodies 22a and 22b are
A known rubber material such as natural rubber, styrene butadiene rubber, isoprene rubber, acrylonitrile butadiene rubber, chloroprene rubber, or butyl rubber, which is appropriately selected according to the use conditions, is vulcanized by itself or blended. It can be formed by the obtained various rubber elastic bodies. In particular, while exhibiting a desired vibration damping effect, a contact sound at the time of contact between the mass member 16 and the housing member 14 is eliminated or reduced. For this purpose, the contact rubber elastic bodies 22a and 22b preferably have a Shore D hardness of 80 or less, more preferably 20 to 40. Further, the contact rubber elastic bodies 22a and 22b preferably have a compression elastic modulus of 1 to 10 ⁴ Mpa, more preferably 1 to 10 ⁴ Mpa.
10 ³ while being set in MPa, loss tangent (tan
δ) is preferably 10 ⁻³ or more, more preferably 0.01
-10 is set.

The arm 1 having the above-described structure is used.
The mass member 2 and the mass member 14 are assembled to each other by externally inserting the mass member 14 into the arm 12. Under such an assembled state, the mass member 14 is inserted and supported by the arm 12. . That is,
Since the inner diameter of the mass member 14 is larger than the outer diameter of the contact fittings 16, 16 protruding from the outer surface of the arm 12 by a predetermined size, the mass member 14
2, the mass member 14 is allowed to be slightly displaced in the direction perpendicular to the axis of the arm 12, whereby the mass member 14 is moved in the direction perpendicular to the axis. 12 can be displaced independently. Here, the contact rubber elastic bodies 22 a and 22 b in the mass member 14 are connected to the contact fitting 1 in the arm 12.
The rubber elastic members 22a, 22b are located radially outward of the rubber elastic members 22a, 22b because their axial lengths are sufficiently larger than the axial lengths of the contact fittings 16, 16.
Can be advantageously secured to the contact fitting 16.

As described above, on both sides in the axial direction of the mass member 14 positioned in the axial direction with respect to the arm 12,
A pair of annular stoppers 24, 24 as stopper means are externally fitted to the arm 12 according to an arbitrary method such as press-fitting or welding.
In the axial direction, the mass members 14 are opposed to each other at an axial distance larger than the axial length of the mass member 14 by a predetermined amount. These stopper fittings 24, 24
4 is set so as to have an outer diameter larger than the inner diameter of the mass member 14. It is possible to prevent excessive displacement of the mass member 14 with respect to the arm 12 in the axial direction while allowing independent displacement in the direction. Thereby, the axial position of the mass member 14 with respect to the arm 12 can be maintained within a predetermined range, and the contact between the contact rubber elastic bodies 22a and 22b and the contact fittings 16 and 16 in the direction perpendicular to the axis is reliably ensured. Can be done. When the mass member 14 abuts against the stopper metal fittings 24, 24, the axial end face of the mass metal fitting 18 is provided with a contact rubber elastic body 22a, in order to reduce or avoid noise such as a hitting sound at the time of abutting. It is desirable to be covered with a cushion rubber extending outward in the axial direction from 22b.

Then, in a state where the arm 12 and the mass member 14 shown in FIG.
A continuous gap δ is formed over the entire circumference between the outer peripheral surfaces of the contact fittings 16 fixed to 2 and the contact rubber elastic bodies 22 a and 22 b provided on the mass member 14. It has become. In particular, in the present embodiment, such a gap: δ
Is preferably 0.05 to 0.8 mm, more preferably 0.05 to 0.5 mm. Thereby, the reciprocating movable distance (2δ) of the mass member 14 in the direction perpendicular to the axis with respect to the arm 12 is preferably 0.1 to 1.6.
mm, more preferably 0.1 to 1.0 mm. In FIG. 1, in order to facilitate understanding,
The state where the mass member 14 and the arm 12 are positioned concentrically as described above is shown.
2, the mass member 14 is displaced vertically downward by the gap: δ due to the action of gravity.
2 is brought into contact.

In the vibration damping device 10 having such a structure, when the arm 12 is vibrated in the direction perpendicular to the axis, the mass member 14 extrapolated to the arm 12 is jumped and displaced in the direction perpendicular to the axis. The contact rubber elastic bodies 22a and 22b provided on the mass member 14 hit against the contact fittings 16 and 16 provided on the arm 12 (contact).
The contact rubber elastic body 22a,
The vibration damping effect is exerted on the arm 12 based on the contact of the contact 22b with the contact fittings 16,16.

Here, the vibration damping device 10 of the present embodiment
In the above, the contact rubber elastic bodies 22a and 22b are formed of different materials, and
The spring constants in the vibration input direction 22b are different from each other. Thereby, the arm 1 of the mass member 14
2 are set to be different from each other, and the mass member 14 hits the arm 12 (contact).
Can be exerted in a plurality of or a wide frequency range.

Specifically, for example, like the vibration damping device 10 of the present embodiment, the mass member 14
If you are hit (abutted) at a point,
The spring constant of a plurality of contact portions separated in the axial direction, that is, in this embodiment, the contact rubber elastic body 2 of the mass member 14
The spring constants of 2a and 22b are k ₁ and k ₂ , the vertical displacement of the center of gravity of the mass member 14 is x, the rotation angle of the mass member 14 around the center of gravity is θ, the mass of the mass member 14 is M, L ₁ the distance in the horizontal direction around the center of gravity of the moment of inertia J, between the axial center of the center of gravity and one of the contact rubber elastic body 22a of the mass member 14, the center of gravity and the other contact rubber elastic body 22b of the mass member 14 Assuming that the horizontal distance between the centers in the axial direction is L ₂ , the following equation of motion holds for the vertical movement of the center of gravity of the mass member 14 and the rotational movement around the center of gravity.

[0034]

(Equation 1)

(Equation 2)

Here, in the case of k ₁ · L ₁ ≠ k ₂ · L ₂ , the following vibration equation is obtained from these equations (1) and (2), as is well known.

[0036]

(Equation 3)

In this embodiment, the contact of the mass member 14 is performed.
The rubber contacting elastic bodies 22a and 22b are formed of different materials.
And the vibration input direction of the contact rubber elastic bodies 22a and 22b.
The spring constants at are different from each other.
In equations (1) and (2), k ₁≠ k_TwoIt depends on
Therefore, from the above equation (3), the following two natural frequencies ω
₁, Ω_TwoIs expressed.

[0038]

(Equation 4)

(Equation 5)

That is, in the vibration damping device 10 of the present embodiment, the mass member 14 is brought into contact with the arm 12 under different contact conditions by the contact rubber elastic bodies 22a and 22b. The mass member 14, which is a rigid single member, is in an coupled vibration state. Therefore, in the vibration damping device 10, the contact rubber elastic bodies 22a, 22b
Are set to be appropriately different from each other, and based on the abutting action of the mass member 14 on the arm 12, the respective resonating actions are used for input vibrations in two different natural frequency ranges. An effective damping effect can be exhibited.

Further, since two different natural frequency ranges are set for the single mass member 14, the single mass member can be used without increasing the number of mass members. A vibration damping device 1 capable of exhibiting an effective vibration damping effect for vibrations in two different natural frequency ranges or a wide frequency range.
0 can be realized with a compact size as a whole.

Further, since the arm 12 itself, which is a vibration member, is used, and the cylindrical mass member 14 is disposed on the outer layer of the arm 12, the vibration damping device 10 of the present embodiment is configured. There is no need to form a special housing, the number of parts is small, the overall size is compact, the structure is simple, the manufacturability is excellent, and the manufacturing cost is reduced. It becomes possible.

Further, the contact rubber elastic bodies 22a, 22b
And the contact fittings 16, 16 are each formed in an annular shape, and the axial length of the rubber elastic bodies 22a, 22b is sufficiently larger than the axial length of the contact fittings 16, 16. Since the size is increased, the state of contact of the mass member 14 with the arm 12 can be stabilized, and a desired vibration damping effect can be stably exhibited.

In addition, instead of or in addition to adjusting the material of the contact rubber elastic bodies 22a and 22b, the mass of the mass metal fitting 18 of the mass member 14 is adjusted and the contact rubber elastic bodies 22a and 22b are adjusted.
By adjusting the shape and size of b, the supporting load and arrangement position in the axial direction, or adjusting the shape, size and material of the contact fittings 16, 16, the contact rubber elastic body 22a,
It is also possible to make the contact conditions of the contact fittings 16, 22 b different from each other.

FIGS. 3 to 8 show vibration damping devices 26, 34, 44, and 58 as another embodiment of the present invention. In the following description, members and parts having the same structure as in the first embodiment will be denoted by the same reference numerals as those in the first embodiment, and detailed description thereof will be omitted. I do.

First, FIGS. 3 and 4 show a vibration damping device 26 according to a second embodiment of the present invention. The vibration damping device 26 of the present embodiment differs from the vibration damping device (10) of the first embodiment in that the structure of the mass member 28 and the elastic body that is compressed and deformed are provided on the arm 12 side. I have.

More specifically, a thick-walled cylindrical metal sleeve 30 is externally fitted and fixed to the arm 12 according to an arbitrary method such as press-fitting or welding. A mass member 28 having a thick cylindrical shape with a diameter larger than 30 is externally arranged. Further, in the vicinity of both ends in the axial direction of the metal sleeve 30, annular contact rubber elastic bodies 32 a and 32 b extending continuously in the circumferential direction with a substantially constant rectangular cross section are provided on the outer peripheral surface of the metal sleeve 30. It is provided to protrude radially outward from the outer peripheral surface. The outer diameters of the rubber elastic bodies 32a and 32b are smaller than the inner diameter of the mass member 28 by a predetermined size. As a result, the mass member 28 is inserted and supported by the arm 12, and A slight displacement in the direction perpendicular to the axis with respect to the arm 12 is allowed. In addition, these contact rubber elastic bodies 32a and 32b
The contact rubber elastic bodies (22a, 22a,
Similarly to 22b), an arbitrary rubber material selected in accordance with the required characteristics of the vibration damping device 26 is vulcanized on the outer peripheral surface of the metal sleeve 30 and is simultaneously vulcanized and bonded, so that the metal sleeve 30 The rubber elastic bodies 32a and 32b formed by vulcanizing an arbitrary rubber material in advance may be externally arranged at predetermined positions on the outer peripheral surface of the metal sleeve 30. Then, it may be fixed with an adhesive or the like.

Then, as shown in FIG.
When the arm 8 and the arm 12 are positioned concentrically, a continuous gap is formed over the entire circumference between the outer peripheral surfaces of the contact rubber elastic bodies 32a and 32b and the inner peripheral surface of the mass member 28:
δ is formed. In the present embodiment, the size of the gap: δ is set in the same manner as in the first embodiment.

In the vibration damping device 26 of this embodiment having such a structure, similarly to the vibration damping device (10) of the first embodiment, a vertical (vertical) vibration to be damped is input. Then, the mass member 28 extrapolated and arranged on the arm 12 is jumped and displaced independently of the arm 12 and hits (contacts) the arm 12. In the device 26 as well, the same vibration damping effect as in the first embodiment can be effectively exerted.

Here, in this embodiment, the arm 1
The contact portions on the two sides, that is, the contact rubber elastic members 32a and 32b are formed of rubber elastic members of different materials, so that the contact rubber elastic members 32a and 32b have different spring constants in the vibration input direction. Therefore, as in the first embodiment, in the equations (1) and (2),
Since k ₁ ≠ k ₂ , two natural frequencies ω ₁ and ω ₂ are developed. Therefore, the vibration damping device 26 of the present embodiment
Also, in these natural frequency ranges, an excellent vibration damping effect can be exhibited.

In the present embodiment, the contact rubber elastic body 3
The metal sleeve 30 to which the 2a and 32b are fixed is externally fitted and fixed to the arm 12, so that the contact portion on the vibration member (arm 12) side can be formed of a rubber elastic body. That is, a long arm 1 as a vibration member
With respect to 2, the abutting portion of the rubber elastic body can be formed on the vibrating member side only by externally fixing the separately formed metal sleeve 30, so that the workability is advantageously improved. Can be planned.

In the vibration damping device 26 of this embodiment, the mass and material of the mass member 28 are changed, and the shapes, sizes and materials of the contact rubber elastic bodies 32a and 32b are changed.
Due to a change in the supporting load in the axial direction of the contact rubber elastic bodies 32a, 32b, a change in the arrangement position of the contact rubber elastic bodies 32a, 32b, etc., the mass member 28 at a plurality of positions separated in the axial direction with respect to the arm 12 The contact conditions can be different from each other.

Next, FIG. 5 shows a vibration damping device 34 as a third embodiment of the present invention. The vibration damping device 34 according to the present embodiment includes a structure of the mass member 36 and a contact fitting (1).
6, 16) is different from the vibration damping device (10) of the first embodiment in that it is not provided. The contact rubber elastic bodies 22a and 22b are formed of rubber elastic bodies of the same material.

More specifically, the mass member 36 of the present embodiment
One end in the axial direction (left side in FIG. 5) of the mass metal member 18 that constitutes the outer peripheral portion protrudes radially outward from the other end in the axial direction and is thickened to form a thick portion 40. . Thereby, the supporting load in the axial direction of the contact rubber elastic bodies 22a and 22b is set to be different from each other. Further, at the axially central portion of the inner peripheral surfaces of the contact rubber elastic bodies 22a and 22b, contact portions 42a and 42b projecting inward in the radial direction and extending over the entire periphery with a substantially constant cross section are integrally formed. I have. The contact portions 42a and 42b gradually become narrower toward the radially inwardly projecting distal end surface, and the arm 1
2 is formed with a protruding height that does not reach the outer surface.

When the mass member 36 and the arm 12 are positioned substantially concentrically, the contact rubber elastic body 2
A continuous gap over the entire circumference between the inner peripheral surfaces of the contact portions 42a and 42b of the 2a and 22b and the outer peripheral surface of the arm 12:
δ is formed. In the present embodiment, the size of the gap: δ is set in the same manner as in the first embodiment.

In the vibration damping device 34 of this embodiment having such a structure, similarly to the vibration damping device (10) of the first embodiment, a vertical (vertical) vibration to be damped is input. Then, the mass member 36 extrapolated and arranged on the arm 12 is jumped and displaced independently of the arm 12 and hits (contacts) the arm 12. In the device 34 as well, the same vibration suppression effect as in the first embodiment can be effectively exerted.

Here, in this embodiment, since the shared supporting loads in the axial direction of the contact rubber elastic bodies 22a and 22b are set to be different from each other, the relative displacement of the mass member 36 with respect to the arm 12 is different from each other. The tuning can advantageously be carried out so as to have a resonant effect in different frequency ranges, whereby the mass member 36 hits the arm 12 against vibrations in a plurality of or wide frequency ranges. ) Can be effectively obtained.

More specifically, the vibration damping device 3 of this embodiment
In No. 4, since the shared supporting loads of the contact rubber elastic bodies 22a and 22b are different from each other, in the equation of motion shown in the above equations (1) and (2), L ₁
≠ L ₂ , whereby the following two natural frequencies ω ₁ and ω ₂ are expressed from the equation (3).

[0058]

(Equation 6)

(Equation 7)

Therefore, the vibration damping device 34 of this embodiment can exhibit an excellent vibration damping effect in those natural frequency ranges.

Further, in the vibration damping device 34 of the present embodiment, the mass of the mass metal fitting 18 is changed,
a, 22b and the shape and size and material of the abutting portions 42a, 42b, change of the shared load of the abutting rubber elastic bodies 22a, 22b in the axial direction, and the abutting rubber elastic bodies 22a, 22b.
It is also possible to change the contact conditions of the mass member 14 with respect to the arm 12 at a plurality of locations spaced apart in the axial direction by changing the disposition position, the shape of the thick portion 40, or the like.

FIG. 6 shows a vibration damping device 44 according to a fourth embodiment of the present invention. The vibration damping device 44 of the present embodiment includes a mass member 46 and a contact rubber elastic body 50.
a, 50b and the point that the contact fittings (16, 16) are not provided, the vibration damping device (1
0).

More specifically, the mass member 46 of the present embodiment
Are elastic members 50a and 50b as cylindrical contact portions provided on both sides of the mass metal member 48 in the axial direction.
It is comprised including. The mass metal fitting 48 has a cylindrical shape having a substantially constant thickness, and is thickened such that one end in the axial direction projects radially outward from the other end. , The thick part 52. Also,
The contact rubber elastic bodies 50a and 50b are formed in a tapered cylindrical tapered portion 54 whose diameter gradually decreases as going outward in the axial direction.
a, 54b, and cylindrical extension tubular portions 56a, 56b extending from the axially outer ends of the tapered portions 54a, 54b further outwardly in the axial direction with substantially constant inner and outer diameters. It has a structure. The end faces of the tapered portions 54a and 54b on the inner side in the axial direction are respectively
Vulcanized adhesive is applied to both ends in the axial direction of the mass metal fitting 48 so that the contact rubber elastic bodies 50a and 50b extend outwardly in the axial direction from the mass metal fitting 48, and the contact rubber elasticity is increased. Extension cylinder part 5 in bodies 50a and 50b
6a and 56b are positioned inward in the direction perpendicular to the axis with respect to the mass metal fitting 48. In addition, the contact rubber elastic bodies 50a, 5
0b is the contact rubber elastic body (22) of the first embodiment.
Like a and 22b), it can be suitably formed of a rubber material arbitrarily selected according to the required characteristics of the vibration damping device. Furthermore, in the present embodiment, the contact rubber elastic bodies 50a, 50
The shape and size of b are set substantially the same. Note that the inner and outer peripheral surfaces of the mass metal fitting 48 are
a, 50b, and is preferably covered with a covering rubber layer extending from the contacting rubber elastic body 5.
The bonding strength of the masses 0a and 50b to the mass metal fitting 18 can be secured firmly.

When the mass member 46 and the arm 12 are positioned substantially concentrically, the outer peripheral surface of the arm 12 and the inner peripheral surface of the mass member 46, that is, the contact rubber elastic body 50
A continuous gap δ is formed over the entire circumference between the inner peripheral surfaces of the extension tubular portions 56a and 56b at the positions a and b. In the present embodiment, the size of the gap: δ is set in the same manner as in the first embodiment.

In the vibration damping device 44 of this embodiment having such a structure, similarly to the vibration damping device (10) of the first embodiment, the vertical (vertical) vibration to be damped is input. Then, the mass member 46 extrapolated to the arm 12 is jumped and displaced independently of the arm 12 and hits (contacts) the arm 12. In the device 44 as well, the same vibration suppression effect as in the first embodiment can be effectively exerted.

In this embodiment, the contact rubber elastic members 50a, 50b extending axially outward from both ends in the axial direction of the mass metal fitting 48 are positioned radially inward of the mass metal fitting 48. Extension cylinder portions 56a, 56b
In this case, since the mass member 46 is configured to be brought into contact with the arm 12,
When the contact rubber elastic member 5 is brought into contact with the rubber elastic member 5, an external force in the shearing direction is exerted between the mass metal fitting 48 and the extension cylinder portions 56 a and 56 b which are separated in the axial direction.
The tapered portions 54a and 54b of 0a and 50b are elastically deformed mainly in the shearing direction.

By employing the contact rubber elastic bodies 50a and 50b which can be sheared as described above, the contact rubber elastic body can be reduced while reducing or avoiding the enlargement of the mass member and the decrease in the durability of the elastic material. 50a, 50b taper portions 54a,
54b, based on the shear deformation of the rubber elastic body 50a,
The spring constant of 50b can be set sufficiently small. Therefore, it is possible to advantageously set the resonance-active peak region in the vibration suppression effect exerted by the striking (contact) of the mass member 46 against the arm 12 in the low frequency range. 10 generally problematic
An effective vibration damping effect can be obtained for vibration in a low frequency range of about 100 Hz to about 100 Hz.

The contact rubber elastic body 50 of the mass member 46
Since the tapered portions 54a and 54b in the a and 50b are configured to be elastically deformed in the shearing direction,
Even at the time of vibration input of small energy in low frequency range,
Hitting (contact) of the mass member 46 against the arm 12
The amplitude magnification of the mass member 46 with respect to the arm 12 can be set to 1 or more based on the resonance effect generated at that time. Therefore, the mass member 46 can be efficiently jumped and displaced with respect to the arm 12 at the time of vibration input. For example, even when the acceleration of vibration to be damped in the arm 12 is 1 G (gravitational acceleration) or less, the mass member 46 can be displaced. 46 can be jumped up and displaced with respect to the arm 12, so that the mass member 46 can be displaced.
The vibration damping effect exerted on the basis of the hitting (contact) of the arm 12 can be advantageously obtained even for vibrations of small energy such as vibrations in an automobile.

Here, in the present embodiment, since the shared supporting loads in the axial direction of the contact rubber elastic bodies 50a and 50b are set to be different from each other, the relative displacement of the mass member 46 with respect to the arm 12 is different from each other. The tuning can advantageously be carried out so as to have a resonant effect in different frequency ranges, whereby the mass member 46 hits against the arm 12 against a plurality of or wide frequency ranges of vibration. ) Can be effectively obtained.

More specifically, the vibration damping device 4 of the present embodiment
In No. 4, since the shared supporting loads of the contact rubber elastic bodies 50a and 50b are different from each other, the movement shown in the formulas (1) and (2) as in the third embodiment. In the equation, L ₁ ≠ L ₂ , whereby two natural frequencies ω ₁ and ω ₂ are developed. Therefore, the vibration damping device 44 of the present embodiment
Means that the mass member 46 is jumped and displaced with a larger amplitude magnification at two different natural frequencies ω ₁ and ω ₂ , and therefore, a better vibration damping effect in those natural frequency ranges. Can be exhibited.

Further, in such a vibration damping device 44, even when the vibration to be damped is in a low frequency range, the low dynamic spring of the abutting portion (the abutting rubber elastic bodies 50a, 50b) of the mass member 46 is provided. By the characterization, the frequency range in which the resonance-type vibration damping effect is exhibited can be tuned to the low frequency side, so that the mass of the mass metal fitting 48 is prevented from increasing, and the vibration damping device can be made more compact. It can be done.

In this embodiment, the contact rubber elastic members 50a, 50 provided at both ends in the axial direction of the mass member 46 are provided.
b, the arms 12
The mass member 46
Of the arm 12 can be stabilized.

Further, in the vibration damping device 44 of this embodiment, the mass of the mass metal fitting 48 is changed,
a, 50b material change, contact rubber elastic body 50a, 50
b. Change in the shared support load in the axial direction, abutment rubber elastic body 50
a, 50b, the inclination angle and free length of the tapered portions 54a, 54b, the radial thickness of the contact rubber elastic bodies 50a, 50b, the size and shape of the thick portion 52, and the contact. By changing the arrangement positions of the rubber elastic bodies 50a and 50b, the contact conditions of the mass member 46 with the arm 12 at a plurality of locations separated in the axial direction can be made different from each other.

FIGS. 7 and 8 show a vibration damping device 58 according to a fifth embodiment of the present invention. The vibration damping device 58 of the present embodiment includes a mass member 60 and a contact rubber elastic body 6.
It differs from the vibration damping device (10) of the first embodiment in that the structures 8a and 68b and the contact fittings (16, 16) are not provided.

More specifically, the mass member 60 of the present embodiment
Has a mass metal fitting 62. This square fitting 62
It has a cylindrical shape with a substantially constant thickness, and is thickened so that one end in the axial direction protrudes radially outward from the other end in the axial direction. Is configured. A plurality of (six in the present embodiment) through holes 66 are formed in the vicinity of both ends in the axial direction of the mass metal fitting 62 in a circular cross section in the thickness direction. The through holes 66 are positioned at equal intervals in the circumferential direction of the mass metal fitting 62, and a plurality of through holes 66 formed at one end in the axial direction and a plurality of through holes 66 formed at the other end in the axial direction. The individual through-holes 66 are formed at substantially the same circumferential position as each other, and are each formed with substantially the same size.

The plurality of through holes 6 on the side of the thick portion 64
6, the contact rubber elastic bodies 68a are arranged in a filled state, while the contact rubber elastic bodies 68b are arranged in a filled state in the other plurality of through holes 66 in the axial direction. It is arranged. The contact rubber elastic bodies 68a, 68
8b has a disk shape that spreads with a substantially constant thickness, and its outer peripheral surface is vulcanized and bonded to the inner peripheral surface of the through hole 66, so that the outer peripheral surface of the mass metal fitting 62 is The contact rubber elastic bodies 68a and 68b are fixed.
The surface of the mass metal fitting 62 has a contact rubber elastic body 68a,
Desirably, it is covered with a covering rubber layer extending from the contact rubber 68b. Thereby, the contact rubber elastic bodies 68a,
The adhesive strength of the 68b to the mass metal fitting 62 can be advantageously secured. Further, the inner peripheral surfaces of the contact rubber elastic bodies 68a, 68b are projected radially inward from the inner peripheral surface of the mass metal fitting 62, and the protruding portions cause the frusto-conical contact portions 70a, 68b. 70b is formed, and the projecting distal end surfaces of the contact portions 70a and 70b are formed in an arc shape along the outer peripheral surface of the arm 12. The contact rubber elastic members 68a and 68b are similar to the contact rubber elastic members (22a and 22b) in the first embodiment, and are similar to the vibration damping device 58.
Can be suitably formed by a rubber elastic body or the like obtained from a rubber material appropriately selected according to the required characteristics of the above.

When the mass member 60 and the arm 12 are positioned substantially concentrically, the outer peripheral surface of the arm 12 and the inner peripheral surface of the mass member 60, that is, the outer peripheral surface of the arm and the contact rubber elastic body 68a , 68b, contact portions 70a, 7b
In each case, a gap δ is formed between the protruding distal end surface of Ob. In the present embodiment, the size of the gap: δ is set in the same manner as in the first embodiment.

In the vibration damping device 58 of this embodiment having such a structure, similarly to the vibration damping device (10) of the first embodiment, when a vertical vibration to be damped is inputted. The mass member 60 extrapolated and arranged on the arm 12 is jumped and displaced independently of the arm 12, and hits (contacts) the arm 12, so that the vibration damping device 58 of the present embodiment also has Therefore, the same vibration damping effect as that of the first embodiment can be effectively exerted.

In this embodiment, the outer peripheral surfaces of the contact rubber elastic bodies 68a and 68b are fixedly supported by the mass metal fitting 62, and the contact rubber elastic bodies 68a and 68b
When the contact load of the mass member 60 is input in a direction perpendicular to the contact rubber elastic bodies 68a, 68b, that is, in the vertical direction (vertical direction), with respect to the central portions of the contact portions 70a, 70b of the contact member 68b. The contact rubber elastic bodies 68a and 68b are elastically deformed mainly in the shearing direction. Therefore, also in the vibration damping device 58 of the present embodiment, the same vibration damping effect as in the fourth embodiment can be exhibited.

In this embodiment, the contact rubber elastic body 6
8a and 68b are set so that the shared supporting loads in the axial direction are different from each other. Therefore, similarly to the third embodiment, L _{1 in the} equations of motion shown in the equations (1) and (2). ≠ L ₂ , whereby two natural frequencies ω ₁ and ω ₂ are developed.
Therefore, also in the vibration damping device 58 of the present embodiment, the mass member 60 jumps and displaces with a larger amplitude magnification at two different natural frequencies ω ₁ and ω ₂ , respectively, A better vibration damping effect can be exhibited in the frequency range.

Further, in the vibration damping device 58 of this embodiment, the mass of the mass metal fitting 62, the shape and size of the through hole 66, the shape, size and material of the contact rubber elastic bodies 68a and 68b are changed. Change, the contact rubber elastic body 68a,
68b, the mass member 60 contacts the arm 12 at a plurality of locations separated in the axial direction by changing the supporting load in the axial direction, changing the shape and size of the thick portion 64, changing the formation position of the through hole 66, and the like. The contact conditions can be different from each other.

Although some embodiments of the present invention have been described in detail, these are merely examples, and the present invention is not to be construed as being limited in any way by the specific description in the embodiments. Not something.

For example, in the second embodiment, the cross-sectional shape of each of the contact rubber elastic bodies 32a and 32b is a rectangular cross-sectional shape, but any one of the two contact rubber elastic bodies is used. It is also possible that the cross-sectional shape is a semi-circular cross-sectional shape, so that even if the two contact rubber elastic bodies are formed of the same material rubber elastic body,
The spring constants of the two contact rubber elastic bodies in the vibration input direction can be different from each other.

In the third embodiment, the cross-sectional shape of the contact portions 42 is not limited to that of the embodiment, and may be, for example, a semicircular cross-section. Further, the axial length of the thick portion 40 is arbitrary, and is not limited to the length of the above-described embodiment. Further, the contact rubber elastic bodies 22 and 22 can be formed of rubber elastic bodies made of different materials from each other, so that the tuning of the natural vibration range can be appropriately changed. Further, the axial position at which the contact rubber elastic body 22 is provided is not limited to that of the above-described embodiment, and may be provided at the axial position at which the thick portion 40 is formed, for example.

In the fourth embodiment, the axial dimension of the thick portion 52 is arbitrary, and is not limited to the dimension of the embodiment. Further, the contact rubber elastic bodies 50a and 50b can be formed of different materials.

In the fifth embodiment, the formation position, shape, size and number of the through holes 66 are not limited to those of the fifth embodiment. Further, the axial length of the thick portion 64 is not limited to the embodiment. Further, the shape of the contact portion of the contact rubber elastic body is not limited to the shape of the embodiment, and may be, for example, a hemispherical shape. Further, the contact rubber elastic bodies 68a and 68b are formed of the same material, but may be formed of different materials. Furthermore, by changing the size of the through hole 66, it is also possible to change the spring constant of the contact rubber elastic bodies 68a and 68b.

In the fourth and fifth embodiments,
Although the outer diameter dimension of the mass metal fitting was only partially different in the axial direction, it is also possible to make the outer diameter dimension of the mass metal fitting different in a plurality of portions in the axial direction. It is not necessary for the outer diameter of the mass metal fitting to gradually increase as going to.

Further, in the above embodiment, when the shared support load is varied, the shared support load in the axial direction of the contact rubber elastic body is varied by varying the outer diameter of the mass metal fitting in the axial direction. However, the outer diameter of the mass metal fitting is kept constant in the axial direction, and the distance between the formation position of the two abutment rubber elastic bodies and the center of gravity of the mass member in the axial direction is made different from each other. It is also possible to make the supporting load in the axial direction of the elastic rubber contact member different from each other.

In the first to fourth embodiments, the abutting portion of the mass member is formed in a cylindrical or annular shape which is continuous in the circumferential direction. There is no.

In the above-described embodiment, the mass member is directly extrapolated to the vibration member. However, the mass member may be extrapolated to a rod or the like fixedly attached to the vibration member. It is possible. Further, the structure and outer shape of the vibration member are arbitrary, and are not to be construed as being limited to those of the illustrated embodiment.

In addition, although not enumerated one by one, the present invention
Based on the knowledge of those skilled in the art, the present invention can be implemented in a form in which various changes, modifications, improvements, and the like are added.
It goes without saying that all such embodiments are included in the scope of the present invention, without departing from the spirit of the present invention.

[0091]

As is apparent from the above description, in the vehicle vibration damping device having the structure according to the present invention, the contact conditions of the mass member with respect to the vibration member at the plurality of contact points separated in the axial direction are determined. By making the mass members different from each other, an effective vibration damping effect can be provided for a plurality of or a wide frequency range of vibrations based on the hitting (contact) of the mass members with respect to the vibration member. Can be obtained.

[Brief description of the drawings]

FIG. 1 is a sectional view showing a vibration damping device as a first embodiment of the present invention.

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

FIG. 3 is a sectional view showing a vibration damping device as a second embodiment of the present invention.

FIG. 4 is a sectional view taken along line IV-IV in FIG. 3;

FIG. 5 is a sectional view showing a vibration damping device according to a third embodiment of the present invention.

FIG. 6 is a sectional view showing a vibration damping device according to a fourth embodiment of the present invention.

FIG. 7 is a sectional view showing a vibration damping device as a fifth embodiment of the present invention.

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

[Explanation of symbols]

 DESCRIPTION OF SYMBOLS 10 Vibration suppression device 12 Arm 14 Mass member 16 Contact fitting 22 Contact rubber elastic body

Claims (12)

[Claims] 1. A vehicle in which a mass member is disposed so as to be independently displaceable and non-adhesive to a vibration member so that the mass member can be directly and elastically brought into contact with the vibration member. In the vibration damping device for use, while the vibrating member has a rod shape, the mass member formed of a substantially rigid single member as a whole has a cylindrical or annular shape, and the mass member is attached to the vibrating member. And the mass member is directly and elastically contacted at a plurality of contact points axially separated from the vibration member in one direction of the vibration input direction. A contact condition of the mass member with respect to the vibrating member at a plurality of contact points is different from each other. 2. The vibration damper for a vehicle according to claim 1, wherein at least one of the plurality of contact points separated in the axial direction has an annular shape or a cylindrical shape extending continuously in a circumferential direction of the mass member. apparatus. 3. At least one of the plurality of contact points separated in the axial direction is disposed on a surface of the vibration member and the mass member opposed to each other in a direction perpendicular to the axis, and the mass member contacts the vibration member. The vehicle vibration damping device according to claim 1, wherein the vibration damping device is formed of a compression elastic body that is compressed and deformed by contact. 4. The vehicle vibration damping device according to claim 1, wherein at least one of the plurality of contact portions separated in the axial direction is formed of an elastic body that is sheared and deformed by a load in the contact direction. . 5. A cylindrical contact portion extending outwardly on both sides in the axial direction from the mass member, and a contact portion of the mass member with respect to the vibration member is formed by the cylindrical contact portion. The vehicle vibration damping device according to claim 4. 6. The vibration damping device for a vehicle according to claim 4, wherein a through hole is formed in the mass member, and the elastic body forming the contact portion is disposed in the through hole. 7. The load supporting the mass of the mass member in the direction perpendicular to the axis by the vibrating member at the plurality of contact points separated in the axial direction is different from each other.
The vibration damping device for a vehicle according to any one of the above. 8. The vehicle vibration damping device according to claim 1, further comprising stopper means for limiting a relative displacement of the mass member with respect to the vibration member in an axial direction. 9. The mass member having a mass of 10
The vehicle vibration damping device according to any one of claims 1 to 8, wherein the weight is from 1000 to 1000 g. 10. The reciprocating movable distance of the mass member between the contact portions on both sides in the vibration input direction, wherein the mass member is brought into contact with the vibration member on both sides in the vibration input direction. Is set to 0 in the vibration input direction.
The vehicle vibration damper according to any one of claims 1 to 9, wherein the distance is 1 to 1.6 mm. 11. The vibration damping device for a vehicle according to claim 1, wherein a contact surface of at least one of the vibration member and the mass member has a Shore D hardness of 80 or less. 12. The vehicle vibration damping device according to claim 1, wherein a total mass of the mass member is 5% to 10% of a mass of the vibration member.