JP3879542B2 - Damping device and control method thereof - Google Patents

Description

[0001]
【Technical field】
The present invention relates to a vibration damping device that is mounted on a vibration member to reduce vibration of the vibration member, and more particularly to a vibration damping device that can exhibit an effective vibration damping effect when applied to a vibration member in an automobile. Is.
[0002]
[Background]
Conventionally, as a method of reducing the vibration that causes problems in the vibration member, (1) a mass damper that fixes the mass material to the vibration member, and (2) a mass material is connected and supported to the vibration member via a spring material. There are known dynamic dampers and (3) vibration damping materials in which a sheet-like elastic material is attached to the surface of a vibration member. However, each of the above (1) mass damper and (2) dynamic damper has a problem that a large mass material mass is required and a frequency range where an effective damping effect is exhibited is narrow. . Further, the above (3) vibration damping material has a problem that a large sticking area is required and the weight increases. Furthermore, the upper air (2) dynamic damper and (3) damping material have high temperature dependence of damping effect, so it is difficult to obtain the desired damping effect stably depending on the usage conditions. There was also.
[0003]
Therefore, the present applicant previously arranged an independent mass member in the international publication WO 00/14429 in such a manner that the independent mass member can be displaced relative to the housing fixed to the vibration member with no gap therebetween. At the time of vibration input, such an independent mass member is brought into contact with the housing by an elastic contact surface, thereby obtaining a vibration damping effect by utilizing sliding friction at the time of contact and energy loss due to collision. Therefore, a damping device with a novel structure was proposed as a damping device for vehicles. In the vibration damping device having such a structure, it is possible to obtain an effective vibration damping effect against vibrations over a wide frequency range due to the small mass.
[0004]
[Solution]
Here, the present invention has been completed as a result of further investigations by the inventor of the vehicle vibration damping device described in the above-mentioned International Publication WO00 / 14429, and is to be solved. However, an object of the present invention is to provide a vibration damping device having an improved structure capable of obtaining a vibration damping effect superior to that of the vehicle vibration damping device described in International Publication WO 00/14429.
[0005]
[Solution]
Hereinafter, the aspect of this invention made | formed in order to solve such a subject is described. In addition, the component employ | adopted in each aspect as described below is employable by arbitrary combinations as much 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 can be understood by those skilled in the art from those descriptions. It should be understood that it is recognized on the basis of.
[0006]
That is, as a result of further studies on the vibration damping device for a vehicle described in the above-mentioned International Publication WO00 / 14429, the present inventor can displace the independent mass member relative to the housing more efficiently, and further jump up. It was possible to find a new technical idea that the damping effect based on the substantial abutting contact with the housing of the independent mass member can be exhibited more effectively by making the jumping displacement. Therefore, the present inventor has completed the present invention based on such new knowledge.
[0007]
Accordingly, a first aspect of the present invention relating to a vibration damping device includes: (a) a contact member that is attached to the vibration member and receives vibration to be damped; and (b) non-adhered to the corresponding contact member And (c) by vibrating the contact surface of the independent mass member in the contact member. It has the vibration means which exerts the jumping force from an applicable contact member on an independent mass member, It is characterized by the above-mentioned.
[0008]
In the vibration damping device having such a structure according to this aspect, even when the excitation force input from the outside is small by exciting the contact surface of the independent mass member in the contact member by the vibration means. By applying the internal excitation force generated by the vibration damping device itself, the independent mass member can be advantageously jumped and displaced to hit and come into contact with the contact member.
[0009]
Therefore, in the vibration damping device according to this aspect, for example, even when the acceleration of the vibration to be damped in the vibration member is 1 G (gravity acceleration) or less, the independent mass member jumps from the contact member and jumps and displaces. Therefore, even with such a small energy vibration, the vibration damping effect based on the contact of the independent mass member with the contact member can be effectively exhibited.
[0010]
Further, in this aspect, since the independent mass member can be forcedly displaced by arbitrary vibration at an arbitrary frequency by the vibration means and can come into contact with the contact member, the vibration frequency to be controlled changes. In this case, an effective damping effect can be obtained.
[0011]
In this aspect, the contact member may be fixed and directly attached to the vibration member, but indirectly through a spring member as shown in a fourth aspect to be described later. It may be attached to. Further, in this aspect, the independent mass member is entirely formed of a rubber elastic body, a synthetic resin material, or a foamed material thereof, or a rigid material such as a metal is fixedly attached to such an independent mass member. However, in addition, the entire independent mass member may be formed of a rigid material such as a metal. In that case, the independent mass member is elastically formed with respect to the contact member. It is desirable that at least one of the contact surface of the independent mass member and the contact surface of the contact member is formed of an elastic material such as a rubber elastic body or a synthetic resin material so as to be in contact.
[0012]
Further, in this aspect, there is no member that elastically and directly connects the independent mass member and the contact member. That is, the entire outer surface of the independent mass member is completely independent from the contact surface of the contact member, and the independent mass member is independent in the state where the independent mass member is positioned at the center of movement relative to the contact member. The abutting surface of the mass member is spaced apart from the abutting surface of the abutting member with a gap formed by a predetermined space. In other words, it is non-adhesive and can be displaced independently.
[0013]
Furthermore, in this aspect, as the vibration structure of the contact surface of the independent mass member in the contact member, a structure that directly vibrates the contact surface, and a vibration other than the contact surface of the contact member, Either or both of the structures for transmitting the excitation force to the abutment surface for excitation can be employed. In this aspect, the contact surface to be vibrated is preferably a contact surface with which the independent mass member is in contact with no vibration input. In addition, an arbitrary surface that is brought into contact with the displacement of the independent mass member at the time of vibration input may be included, and there may be a plurality of contact surfaces that are vibrated.
[0014]
Further, the vibration means in this aspect can be constituted by an electric motor, a hydraulic actuator, or the like, but a magnetostrictive element, electrostrictive element, electromagnetic type capable of easily controlling the vibration frequency and the like. It is desirable that the contact surface of the independent mass member in the contact member is vibrated at a high frequency, and further, the frequency and phase of the excitation force can be controlled with high accuracy. It becomes.
[0015]
Further, a second aspect of the present invention relating to the vibration damping device is that in the vibration damping device according to the first aspect, the vibration means is attached to the contact surface of the independent mass member in the contact member. The contact surface is directly vibrated by repeatedly deforming the contact surface. In the vibration damping device having the structure according to this aspect, since the contact surface of the independent mass member in the contact member is directly deformed by the vibration by the vibration unit, the vibration force by the vibration unit Can be more efficiently applied to the independent mass member, and the excitation force exerted on the independent mass member can be easily controlled.
[0016]
In this aspect, the deformation of the contact surface of the independent mass member in the contact member by the vibration means is, for example, using a magnetostrictive element attached to the contact surface of the independent mass member in the contact member. An electrostrictive element (piezoelectric element) attached to the contact surface of the independent mass member in the contact member, or an output member of an electromagnetic actuator on the contact surface of the independent mass member in the contact member Any of the fixed ones can be suitably employed.
[0017]
According to a third aspect of the present invention relating to the vibration damping device, in the vibration damping device according to the first or second aspect, the contact member is configured by a housing having a hollow structure, and the independent mass member is It is characterized in that it is accommodated in the housing as a circular cross section having a spherical or circular rod shape. In the vibration damping device having the structure according to this aspect, it is possible to form a plurality of contact surfaces of the independent mass member around the independent mass member by the inner surface of the housing having the hollow structure, and thereby, in a plurality of directions. It is possible to obtain an effective damping effect even with respect to the vibration input from. Further, since the independent mass member has a circular cross section having a spherical shape or a circular rod shape, the sliding contact area with respect to the housing when the independent mass member jumps and displaces is reduced, and the catching resistance is also reduced. Therefore, when the abutment surface is vibrated by the vibration means, the independent mass member jumps and displaces more efficiently, and the control based on the abutting contact of the independent mass member against the abutment member (housing). The vibration effect can be obtained more advantageously.
[0018]
In addition, it is desirable to adopt this aspect in combination with the second aspect. In that case, a vibration means such as a magnetostrictive element is fixed to the contact surface of the independent mass member in the housing (contact member). A configuration is advantageously employed.
[0019]
According to a fourth aspect of the present invention relating to the vibration damping device, in the vibration damping device according to any one of the first to third aspects, the damper mass is elastically supported by the vibration member via a spring member. Thus, a sub-vibration system for the vibration member is formed, and the contact member is provided integrally with the damper mass. In the vibration damping device having the structure according to this aspect, the vibration of the vibration member is input to the sub-vibration system including the spring member and the damper mass, and the damper mass is provided with the damper mass in response to the vibration displacement. The independent mass member is displaced relative to the contact member. In particular, when a vibration having a frequency component in the natural frequency range of the secondary vibration system is input, the amplitude of the damper mass increases due to the resonance action of the secondary vibration system, and the relative displacement of the independent mass member relative to the contact member also increases. Thus, the independent mass member is brought into direct and elastic contact with the contact member. As a result, the amplitude suppression effect on the vibration member is exhibited based on the contact of the independent mass member with the contact member. As a result, in the sub-vibration system including the damper mass and the spring member, apparently A state similar to that in which the loss factor is increased and the damping effect is improved is exhibited.
[0020]
Therefore, in the vibration damping device according to this aspect, since the amplitude of the damper mass is suppressed by the contact of the independent mass member with the contact member, the secondary vibration system is configured even if the loss coefficient of the spring member itself is small. The amount of displacement of the damper mass is suppressed and the resonance peak value is lowered. With the addition of the secondary vibration system, in the vibration member that is the main vibration system, both the low frequency side and the high frequency side across the tuning frequency range of the secondary vibration system By suppressing new vibration peaks respectively generated in the frequency domain, it is possible to obtain a satisfactory damping effect over a wide frequency domain as a whole.
[0021]
Further, in the vibration damping device according to this aspect, the independent mass member can be jumped and displaced from the contact member by the vibration means regardless of the natural frequency of the sub-vibration system. When the vibration to be damped is in a plurality of frequency ranges, the natural frequency of the sub-vibration system is tuned to one of the plurality of frequency ranges to control based on the resonance action of the sub-vibration system. The abutting member of the independent mass member that effectively exerts the vibration effect against vibrations in such a frequency range, and is jumped and displaced from the abutting member by vibration means for vibrations in other frequency ranges. It is possible to exert a vibration damping effect on the basis of the abutting contact with respect to, and thereby it is also possible to exert an effective vibration damping effect over a wide frequency range.
[0022]
As the spring member in this aspect, various spring materials such as a metal spring, a rubber spring, and a resin spring can be adopted depending on the required vibration damping characteristics. A rubber spring formed of a specific rubber material such as silicon rubber, natural rubber, or a blend of natural rubber and butadiene rubber has a small loss factor, and more preferably is a temperature. A metal spring formed of spring steel or the like having a small dependency is employed.
[0023]
Further, in the vibration damping device according to this aspect, the structure of the employed spring member is not particularly limited. For example, when adopting a spring member that elastically supports the damper mass with respect to the vibration member in a cantilever structure. In the projection of the position of the center of gravity of the damper mass in the input direction of the vibration to be damped, the fixed portion of the spring member with respect to the vibrating member rather than the protruding tip portion of the spring member arranged extending from the fixed portion to the vibrating member It is desirable to position it on the side. By adopting such a configuration, it is possible to secure a large free length of the spring member while keeping the damper mass arrangement position close to the vibration member and keeping the size of the entire vibration damping device compact.
[0024]
A fifth aspect of the present invention relating to a vibration damping device is characterized in that, in the vibration damping device according to the fourth aspect, the damper mass is constituted by the contact member. That is, in the fourth aspect, the contact member can be formed separately from the damper mass and fixed. However, according to this aspect, for example, a damper mass having a hollow casing structure is adopted, and the damper mass has a hollow casing. By accommodating and disposing the independent mass member in the body, the damper mass itself can also constitute the abutting member, so that the target damping device can be realized with a small number of members and a simple structure.
[0025]
Further, a sixth aspect of the present invention relating to a vibration damping device is characterized in that, in the vibration damping device according to the fourth or fifth aspect, a loss coefficient in the spring member is 0.07 or less. To do. In the vibration damping device having the structure according to this aspect, a larger vibration amplitude is generated with respect to the damper mass and the contact member, and as a result, the independent mass member is applied to the contact member. As a result, it is possible to more effectively exhibit the damping effect based on repeated contact of the independent mass member with the contact member.
[0026]
In the present invention relating to the vibration damping device including the first to sixth aspects as described above, it is desirable that the mass of the independent mass member is 5 to 20% of the mass of the vibration member. If the mass of the independent mass member is smaller 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 the mass exceeds 20%, the weight of the entire vibration damping device is problematic. Because it becomes. In addition, when the damping device has a plurality of independent mass members, it is desirable that the total mass of the plurality of independent mass members is 5 to 20% of the mass of the vibration member.
[0027]
Further, in the present invention relating to the vibration damping device, at least one contact surface in the vibration input direction between the contact member and the independent mass member is formed in order to reduce a contact sound of the independent mass member with respect to the contact member. The elastic member is configured so that the Shore D hardness of ASTM standard D2240 is preferably 80 or less, more preferably 20 to 40, at the contact surface. Furthermore, in order to reduce the contact noise of the independent mass member with respect to the contact member, the compression elastic modulus of the elastic member is preferably 1 to 10. ^Four MPa, more preferably 1-10 ^Three In addition, the loss tangent (tan δ) is preferably 10 ^-3 As mentioned above, More preferably, it shall be 0.01-10.
[0028]
Further, in the present invention relating to the vibration damping device, it is desirable that the independent mass member is brought into contact with the contact member on both sides of the vibration input direction of the vibration member to be damped. The reciprocating movable distance between the contact surfaces on both sides in the vibration input direction with respect to the contact member of the mass member is preferably 0.1 to 1.6 mm, more preferably 0.1 to 1.0 mm.
[0029]
Further, in the present invention related to the vibration damping device, the contact member can be formed of, for example, a metal material such as iron or aluminum alloy, a synthetic resin material, or the like, and particularly has a rigidity for supporting the independent mass member. In order to advantageously secure the damping effect, the elastic modulus is 5 × 10 at least on the contact surface of the independent mass member. ^Three A rigid material having a pressure equal to or higher than MPa is preferably employed. In addition, as a rigid material which comprises a contact member, for example, an elastic modulus is 5 × 10. ^Three ~ 5x10 ^Four A hard synthetic resin material such as MPa can also be used, and such a rigid material may be desirable for reducing contact noise and improving vibration damping characteristics in a low frequency range. In order to obtain a more effective damping effect in the high frequency range, 5 × 10 ^Four A rigid material such as a metal having an elastic modulus of MPa or more is preferably employed.
[0030]
Further, the present invention provides the vibration damping device according to the present invention as described above, wherein the vibration control means controls the vibration means so that the vibration means exerts a vibration force including a random frequency component on the contact member. An apparatus control method is also a feature. According to such a control method of the vibration damping device, the vibration to be damped in the vibration member does not include only the vibration component of the sine waveform but includes a random vibration component in which the waveform and the frequency component change In addition, an effective damping effect can be obtained.
[0031]
Further, according to the present invention, in the vibration damping device according to the present invention as described above, the excitation unit controls the excitation unit so that the excitation member includes an excitation force including a single or a plurality of frequency components. The vibration damping device control method is also characterized. According to such a control method of the vibration control device, when the vibration to be controlled in the vibration member includes a specific frequency component, an effective vibration suppression effect is obtained for the vibration of the specific frequency component. I can do it.
[0032]
DETAILED DESCRIPTION OF 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.
[0033]
First, FIG. 1 shows a vibration damping device 10 as a first embodiment of the present invention. The vibration damping device 10 has a structure in which an independent mass member 16 is accommodated in an accommodation space 14 formed by a housing 12 as a contact member. And this damping device 10 is mounted | worn with the housing 12 being bolt-fixed with respect to vibration members, such as a vehicle body which is not shown in figure. Further, under such a mounted state, main vibration to be damped in the vibration member is input in the vertical direction (vertical direction in FIG. 1). In particular, in this embodiment, the vertical direction is a substantially vertical direction. It is said that.
[0034]
More specifically, the housing 12 includes a housing body 18 and a lid body 20. The housing body 18 is formed of a hard synthetic resin material, and includes a substantially cylindrical tube wall portion 22 and a substantially disk-shaped upper bottom portion 24, and has an inverted cup shape as a whole. . Further, the outer peripheral edge portion of the upper bottom portion 24 has a tapered cylindrical shape that gradually expands toward the cylindrical wall portion 22, and a tapered cylindrical portion 26 is formed by the outer peripheral edge portion. Further, a pair of attachment pieces 28, 28 that extend outward in the radial direction are integrally formed at the opening side end of the housing body 18. Each of the pair of attachment pieces 28 and 28 has a flat plate shape, and is directed radially outward on both sides of the opening of the housing body 18 in one radial direction of the housing body 18. Projected. A metal sleeve 30 as a bolt insertion hole is fixed in a penetrating state at a substantially central portion of the pair of attachment pieces 28, 28.
[0035]
On the other hand, similarly to the housing body 18, the lid body 20 is made of a hard synthetic resin material and has a thin disk shape slightly larger in diameter than the opening of the housing body 18. In addition, a disc-shaped fitting portion 32 that protrudes in one direction in the thickness direction (upward in FIG. 1) is integrally formed at the center portion of the lid 20. On the other hand, the housing body 18 is provided with a fitting recess 34 extending continuously in the circumferential direction by forming the inner peripheral edge of the opening in a stepped shape. The housing main body 18 and the lid body 20 are fixed to each other by welding or bonding by fitting the fitting portion 32 of the lid body 20 to the lid 34. In this manner, the opening of the housing body 18 is covered with the lid body 20, so that the housing 12 is defined by the inner peripheral surface of the housing body 18 and the upper surface of the lid body 20, and is independent of the external space. The accommodation space 14 is formed. Here, as described above, under the state where the lid 20 is fixed to the opening of the housing body 18, the lower surface of the lid 20 and the lower surfaces of the pair of attachment pieces 28, 28 are substantially flush, The separation distance between the center portion of the upper bottom portion 24 in the housing body 18 and the center of the upper surface of the lid 20 is substantially the same as the inner diameter dimension of the cylindrical wall portion 22 in the housing body 18. The elastic modulus of the housing body 18 and the lid 20 is 5 × 10. ^Three It is set as MPa or more. The housing 12 having such a structure is bolted to the vibration member by a bolt (not shown) inserted through the metal sleeves 30 and 30 fixed to the pair of attachment pieces 28 and 28. ing.
[0036]
The independent mass member 16 is composed of a mass fitting 36 having a solid sphere shape and a covering rubber layer 38 formed on the entire surface of the mass fitting 36 with a substantially constant thickness. The dimension is made smaller than the inner diameter dimension of the cylindrical wall portion 22 of the housing body 18 by a predetermined dimension. The mass metal fitting 36 is formed of a metal material having a high specific gravity such as iron. On the other hand, the covering rubber layer 38 is a natural rubber, styrene butadiene rubber, or isoprene rubber appropriately selected according to use conditions. , Acrylonitrile butadiene rubber, chloroprene rubber, butyl rubber and the like, and is formed of a rubber elastic body obtained by vulcanizing a single rubber or a blend. Here, the covering rubber layer 38 has a contact surface with respect to the housing 12 in order to exhibit a desired vibration damping effect and to eliminate or reduce the contact sound at the time of contact between the independent mass member 16 and the housing 12. , Preferably with a Shore D hardness of 80 or less, more preferably 20-40. Further, the coating rubber layer 38 has a compression modulus of preferably 1 to 10. ^Four MPa, more preferably 1-10 ^Three The loss tangent (tan δ) is preferably 10 while being set to MPa. ^-3 As mentioned above, More preferably, it sets to 0.01-10.
[0037]
The independent mass member 16 having such a structure is accommodated and disposed in the accommodation space 14 of the housing 12 in a non-adhesive manner, and defines the independent mass member 16 and the accommodation space 14 in such a accommodated state. Between the inner surface of the housing 12 (that is, the inner peripheral surface of the housing main body 18 and the upper surface of the lid body 20), the independent mass member 16 is positioned in the center of the accommodation space 14. A predetermined gap is formed over the entire periphery. Thereby, the independent mass member 16 can be relatively displaced with respect to the inner surface of the housing 12 independently.
[0038]
Specifically, as shown in FIG. 1, in the stationary state where the independent mass member 16 is placed on the lid body 20 below the accommodation space 14 by gravity, the cylindrical wall in the housing body 18. The gap dimension δ between the inner peripheral surface of the portion 22 and the outer peripheral surface of the independent mass member 16 is preferably 0.05 to 0.8 mm, more preferably 0.05 to 0.5 mm. The gap dimension 2δ between the central inner surface of the upper bottom 24 of the housing body 18 and the outer peripheral surface of the independent mass member 16 is preferably 0.1 to 1.6 mm, more preferably 0.1 to 1.0 mm. Has been. That is, in the state where the independent mass member 16 is positioned at the movement center of the accommodation space 14, the gap δ is formed between the outer peripheral surface of the independent mass member 16 and the inner peripheral surface of the cylindrical wall portion 22. At the same time, the gap δ is formed between the outer peripheral surface of the independent mass member 16, the inner surface of the central portion of the upper bottom portion 24, and the lid body 20. As a result, the vertical and horizontal reciprocating distances (2δ) in the accommodating space 14 of the independent mass member 16 are both 0.1 to 1.6 mm, more preferably 0.1 to 1.0 mm. Yes. In the present embodiment, the independent mass member 16 strikes and comes into contact with the housing 12 on both sides of the main vibration input direction (vertical direction in the drawing) to be damped in the vibration member. Therefore, the vertical reciprocating distance in the accommodating space 14 of the independent mass member 16 is 0.1 to 1.6 mm, but the main vibration input direction in which the independent mass member 16 should be damped, that is, the vertical direction In the case where only the lower side of this is abutted against and brought into contact with the housing 12, the vertical reciprocating distance of the independent mass member 16 may be set to be larger than 1.6 mm.
[0039]
Further, a recess 40 is provided on the lower surface of the lid 20, and a magnetostrictive element 42 that constitutes a vibration means is fixedly provided in the recess 40. The magnetostrictive element 42 is formed of a ferromagnetic material of iron, nickel, or an alloy thereof that causes magnetostriction phenomena such as dimensional change and torsion when magnetized, and corresponds to the upper bottom of the recess 40 as a whole. It has a flat plate shape. The one side of the magnetostrictive element 42 is superposed on the upper bottom surface of the recess 40, and is fixed to the lid 20 by a fixing member 44 that covers the entire magnetostrictive element 42 from the other side. Yes. As a material for forming the fixing member 44, an elastic material that allows a magnetostriction phenomenon of the magnetized magnetostrictive element 42 in a use state of the vibration damping device 10 is preferably used. In particular, in this embodiment, an epoxy resin is used. It has been adopted. Although not clearly shown in the drawing, a lead wire is wound around the magnetostrictive element 42, and current is passed through the lead wire from an external control device, thereby magnetizing the magnetostrictive element 42. As a result, a magnetostriction phenomenon is caused in the magnetostrictive element 42, whereby an excitation force is exerted on the lid 20 on which the magnetostrictive element 42 is superimposed. As is clear from this, in this embodiment, the vibration means is configured to include the magnetostrictive element 42, the lead wire, and the control device, and the housing 12 (contact member) that is vibrated by the vibration means. The contact surface of the independent mass member 16 is formed by the upper surface of the lid 20. Then, due to the magnetostriction phenomenon of the magnetostrictive element 42, the upper surface of the lid 20 on which the magnetostrictive element 42 is overlaid, that is, the contact surface of the independent mass member 16 in the housing 12 (contact member) is repeatedly deformed.
[0040]
As a control device for controlling the energization of the lead wire to control the magnetostriction phenomenon of the magnetostrictive element 42, and hence the vibration of the lid 20, vibration of an acceleration sensor or the like that detects the vibration state of the vibration member is used. Based on the detection signal of the sensor, one that outputs an electrical signal corresponding to the detection signal is employed so that an effective damping effect can be exerted against the vibration. For example, on the basis of preset data, a current having a magnitude corresponding to the magnitude of the detection signal is controlled in a feed-forward manner by feeding the detection signal with a predetermined phase difference, or A device that feedback-controls the magnitude of the current or the like so as to make the vibration value of the vibration member included in the detection signal as zero as possible can be suitably employed.
[0041]
As described above, the vibration damping device 10 having such a structure is fixedly attached to the vibration member by the housing 12 being bolted to the vibration member. Under the mounted state, when the vibration of the vibration member is input to the housing 12, the independent mass member 16 is relatively displaced so as to jump independently in the vibration input direction with respect to the housing 12 in the housing space 14. The mass member 16 strikes and comes into contact with the housing 12. Then, based on the contact action of the independent mass member 16 to the housing 12, a vibration damping effect is exerted on the vibration member.
[0042]
In addition, by magnetizing the magnetostrictive element 42 with a period corresponding to the vibration frequency to be damped, the magnetostrictive element 42 generates a magnetostriction phenomenon such as deformation and torsion of the period corresponding to the vibration frequency to be damped, and magnetostriction. The lid 20 on which the element 42 is superimposed can be vibrated at a vibration frequency to be damped, and is thereby placed on the lid 20 in a stationary state where no vibration is input. The independent mass member 16 is independently jumped and displaced in the vibration direction with respect to the housing 12, that is, in the vertical direction as the main vibration input direction in the present embodiment, so that the independent mass member 16 is separated from the independent mass member 16 in the housing 12. It is possible to hit and come into contact with the upper surface of the lid 20 constituting the contact surface. As a result, the damping effect of the damping device 10 is exerted on the vibrating member based on the contact action of the independent mass member 16 with the housing 12.
[0043]
Therefore, even when the vibration energy to be damped in the vibration member is small and the acceleration thereof is 1 G (gravity acceleration) or less, the independent mass member 16 can jump up and displace from the housing 12 and be independent. The vibration damping effect that is exhibited based on the contact of the mass member 16 against the housing 12 can be advantageously obtained even for vibrations of small energy.
[0044]
If the vibration to be damped in the vibration member exists over a wide frequency range without including only a specific frequency component, the magnetostrictive element is based on a random waveform not including only the specific frequency component. 42 is magnetized, and the lid 20 on which the magnetostrictive element 42 is superposed is vibrated using the magnetostriction phenomenon of the magnetized magnetostrictive element 42, so that a wide frequency range can be obtained without including only a specific frequency component. An effective vibration damping effect can be exhibited with respect to the vibration to be damped throughout. Further, when the vibration to be damped in the vibration member exists in a single or a plurality of specific frequency ranges, the magnetostrictive element 42 is magnetized based on a sine waveform including these specific frequency components, and magnetization is performed. By utilizing the magnetostriction phenomenon of the magnetostrictive element 42 thus applied, the lid body 20 on which the magnetostrictive element 42 is superimposed is vibrated, thereby exhibiting an effective damping effect against vibrations of these specific frequency components. Is possible. It is also possible to employ a combination of both excitation based on a random waveform that does not include only a specific frequency component as described above and excitation based on a waveform that includes only one or a plurality of specific frequency components. Thus, the excitation based on the plurality of waveforms can be appropriately selected according to the purpose.
[0045]
Incidentally, in FIG. 2, the result of simulating the frequency dependence of the vibration level in the vibration member when the vibration damping device 10 of the present embodiment is mounted on the vibration member is shown by a solid line. In this simulation, the vibration to be damped in the vibration member is a vibration including only a single specific frequency component. For comparison, the frequency dependence of the vibration level of the vibration member in a state where the vibration damping device is not mounted is indicated by a broken line, and the mass member is elastically supported by the vibration member via the spring member. The result of simulating the frequency dependence of the vibration level in the vibration member with the so-called dynamic damper attached is shown by a one-dot chain line.
[0046]
As is clear from the simulation results shown in FIG. 2, it is recognized that the vibration damping device 10 of the present embodiment exhibits an effective vibration damping effect against vibration including only a single specific frequency component. .
[0047]
In FIG. 3, a solid line shows a result of simulating the frequency dependence of the vibration level in the vibration member when the vibration damping device 10 of the present embodiment is mounted on the vibration member. In this simulation, the vibration to be damped in the vibrating member exists over the entire wide frequency range without including only a specific frequency component. For comparison, the frequency dependence of the vibration level of the vibration member in a state where the vibration damping device is not attached is indicated by a broken line.
[0048]
As is clear from the simulation results shown in FIG. 3, the vibration damping device 10 of this embodiment is effective for vibrations that exist over the entire wide frequency range without including only specific frequency components. It is recognized that it exerts a vibration effect.
[0049]
FIG. 4 shows a vibration damping device 46 as a second embodiment of the present invention. In the following description of the second to fourth embodiments, for members and parts having the same structure as in the first embodiment, the same reference numerals as those in the first embodiment are attached in the drawing. Detailed description thereof will be omitted.
[0050]
That is, in the first embodiment, the contact surface of the independent mass member 16 in the housing 12 is formed on the lid 20 that forms the housing, and the lid 20 is made using the magnetostriction phenomenon of the magnetostrictive element 42. By oscillating and deforming, the independent mass member 16 jumps up and displaces with respect to the housing 12, but in this embodiment, the contact surface of the independent mass member 16 in the housing 12 is fixed to the lid body 20. The independent mass member 16 jumps up and displaces directly with respect to the housing 12 by using the magnetostriction phenomenon of the magnetostrictive element 42.
[0051]
More specifically, in this embodiment, a recess 48 is provided on the upper surface of the lid 20 instead of the recess (40) provided on the lower surface of the lid 20 in the first embodiment. The magnetostrictive element 42 is disposed in the recess 48. In addition, a substantially flat rubber plate 50 is interposed between the opposing surfaces of the magnetostrictive element 42 and the lid 20 so that the magnetostrictive phenomenon of the magnetostrictive element 42 is allowed. . As is clear from this, in the present embodiment, the contact surface of the independent mass member 16 in the housing 12 (contact member) is constituted by the upper surface of the magnetostrictive element 42, and the magnetostrictive element 42 is energized by energizing the lead wires. As a result of the magnetostriction phenomenon, the upper surface of the magnetostrictive element 42, that is, the contact surface of the independent mass member 16 in the housing 12 (contact member) is repeatedly deformed.
[0052]
In the vibration damping device 46 having such a structure, the independent mass member 16 is accommodated in the accommodating space 14 formed inside the housing 12 so as to be relatively displaceable with respect to the housing 12, and magnetostriction is provided. Based on the magnetostriction phenomenon of the element 42, the independent mass member 16 jumps up and displaces with respect to the housing 12, so that the same vibration damping effect as in the first embodiment can be obtained. It is.
[0053]
Further, in the present embodiment, since the contact surface of the independent mass member 16 in the housing 12 is configured by the magnetostrictive element 42, the jumping displacement of the independent mass member 16 with respect to the housing 12 is easily generated.
[0054]
FIG. 5 shows a vibration damping device 52 as a third embodiment of the present invention.
[0055]
That is, in this embodiment, an electromagnetic exciter 54 is employed instead of the magnetostrictive element (42) employed in the first embodiment. In addition, a part of the pair of attachment pieces 28 and 28 and the metal sleeves 30 and 30 are protruded downward so that the vibrator 54 can be displaced between the lower surface of the lid 20 and the vibration member. It can be arranged with.
[0056]
In this vibrator 54, a mass metal fitting 58 is elastically connected to a mounting metal fitting 56 attached to the lid body 20 by a connecting rubber elastic body 60, whereby the mass metal fitting 58 is used as a mass component, and the connecting rubber elastic body is used. A vibration system having 60 as a spring component is configured.
[0057]
More specifically, in the mounting bracket 56, a first plate bracket 62 and a second plate bracket 64 each having a disk shape are overlapped and fixed to each other by a fixing bolt 66. In addition, an accommodation recess 68 is formed in the central portion of the second metal plate 64 so as to open to the surface overlapped with the first metal plate 62, and the head is accommodated in the accommodation recess 68. A guide rod 72 is fixed by a support bolt 70 having a leg projecting downward in the axial direction. The guide rod 72 is formed of a hard material such as a metal, extends linearly with a substantially constant cross-sectional shape, protrudes downward in the axial direction on the central axis of the mounting bracket 56, and A stopper 74 that extends outward in the axial direction is integrally formed at the protruding tip.
[0058]
Further, a bobbin 76 spreading in a skirt shape in the axially outward direction is overlaid on the lower surface of the second metal plate 64, and the second metal plate is fixed by a guide rod 72 fixed by a support bolt 70. 64 is fixed. The bobbin 76 is formed of an electrical insulating material such as synthetic resin, and a coil 78 is wound and fixed to a cylindrical portion provided at a protruding tip portion in the axial direction.
[0059]
On the other hand, the mass fitting 58 includes a coupling fitting 80, a mass block 82, and a permanent magnet 84. The connecting fitting 80 has an annular block shape, and is arranged radially outwardly spaced from the mounting fitting 56 and coaxially and offset by a predetermined amount axially downward. The second plate metal 64 and the connection metal 80 constituting the attachment metal 56 are connected to each other by the connection rubber elastic body 60. The connecting rubber elastic body 60 has a generally annular plate shape or a tapered cylindrical shape as a whole, and a mounting bracket 56 (second plate bracket 64) with respect to the inner peripheral surface of the small-diameter side end. The outer peripheral surface of the connecting metal fitting 80 is vulcanized and bonded to the outer peripheral surface of the end portion on the large diameter side.
[0060]
The mass block 82 is formed in a large-diameter circular block shape from a material made of a ferromagnetic material such as iron and a high specific gravity material, and a guide hole 86 penetrating in the axial direction is formed on the central axis. In addition, a sliding bush 88 is incorporated in the guide hole 86. Furthermore, the mass block 82 is formed with an annular concave groove 90 that continuously extends in the circumferential direction in the radial direction and opens to one side in the axial direction (upward in FIG. 5). A permanent magnet 84 is inserted into the groove 90 and fixed to the inner surface of the outer peripheral side wall of the annular groove 90. Note that the permanent magnet 84 may be continuous over the entire circumference in the circumferential direction, or may be discontinuous. The permanent magnet 84 is provided with both magnetic poles on the inner peripheral surface side and the outer peripheral surface side, thereby forming a donut-shaped magnetic path as a whole in the mass block 82. An annular groove 90 is positioned on the magnetic path to form a cylindrical magnetic gap as a whole.
[0061]
The mass block 82 is disposed opposite to the mounting bracket 56 on the same central axis and spaced downward in the axial direction. The upper surface of the mass block 82 is overlapped with the lower surface of the coupling bracket 80 to be connected. By fixing with the bolts 92, the mass block 82 is elastically connected to the mounting bracket 56 via the connecting rubber elastic body 60.
[0062]
The mass block 82 is fixed with an annular buffer rubber 94 protruding toward the mounting bracket 56 around the upper end opening of the guide hole 86, and the mass block 82 is interposed via the buffer rubber 94. Comes into contact with the mounting bracket 56 side (the upper bottom wall portion of the bobbin 76), so that the relative displacement amount in the axial direction of the mounting bracket 56 and the mass bracket 58 is limited in a buffering manner. . A large-diameter recess 96 is formed in the lower end opening of the guide hole 86 in the mass block 82, and a stopper 74 of the guide rod 72 is accommodated in the large-diameter recess 96. Then, when the mass metal fitting 58 is largely displaced in the separation direction with respect to the attachment metal fitting 56, the stopper portion 74 of the guide rod 72 is interposed through the buffer rubber layer 98 fixed to the bottom surface of the large-diameter recess 96. By abutting on the upper bottom surface of the large-diameter recess 96 of the mass block 82, the relative displacement amounts of both the metal fittings 56 and 58 are limited in a buffering manner.
[0063]
A coil 78 supported by the mounting bracket 56 is inserted and disposed in the annular groove 90 of the mass block 82, and the annular groove 90 constituted by the inner peripheral side wall surface of the annular groove 90 and the permanent magnet 84. It is arrange | positioned so that an axial direction displacement is possible between the radial direction opposing surfaces with the outer peripheral side wall surface. In addition, a drive current is supplied from an external control device to the coil 78 through a power supply lead wire (not shown). When the drive current is supplied to the coil 78, the coil 78 and the permanent magnet 84 are supplied. Thus, an electromagnetic force is generated between them, so that a relative displacement force in the approach / separation direction on the central axis is exerted between the mounting bracket 56 and the mass bracket 58. In particular, by making the direction of the current flowing through the coil 78 reverse, the relative displacement force exerted between the mounting bracket 56 and the mass bracket 58 can be reversed, and an alternating current is applied to the coil 78. By energizing, a relative vibration force in the axial direction is exerted on the mounting bracket 56 and the mass bracket 58.
[0064]
As a control device for controlling the excitation of the vibration exciter 54 by controlling the energization of the coil 78, the vibration control should be controlled in the same manner as the control device for the driving current of the magnetostrictive element 42 in the first embodiment. Various devices capable of supplying a drive current corresponding to vibration to the coil 78 can be suitably employed.
[0065]
A mounting bracket 56 is superimposed on a mounting plate 100 that is fixed to the lower surface of the lid by bolts, bonding, welding, or the like (not shown), and is fixed to the mounting plate 100 by bolts, bonding, welding, or the like (not shown). As a result, the mounting bracket 56 is mounted on the lid 20, and under such mounting state, the displacement direction of the mass bracket 58 substantially coincides with the vibration direction (vertical direction in FIG. 5) to be damped in the vibrating member. ing.
[0066]
When the vibration damping device 52 having such a structure is energized to the coil 78 of the vibration exciter 54, an axial vibration force based on the electromagnetic force generated between the coil 78 and the magnetic field of the permanent magnet 84 is generated. Therefore, the vibration system composed of the mass fitting 58 and the connecting rubber elastic body 60 is forcibly excited. Here, since such a vibration system has a natural frequency, if the vibration system is vibrated in a frequency range corresponding to the natural frequency, the mass metal fitting 58 is greatly displaced by the resonance action of the vibration system. Thus, a large excitation force is exerted on the lid, whereby the independent mass member 16 is jumped up and displaced by jumping with respect to the housing 12, so that the independent mass member 16 strikes and contacts the housing 12. The vibration control effect based on the frequency range corresponding to the natural frequency of the vibration system can be exhibited. Therefore, by tuning the natural frequency of such a vibration system to the vibration frequency region to be damped in the vibration member, in such a frequency region, an effective vibration damping effect is exerted on the vibration member with small power consumption. I can do it. As is clear from this, in the present embodiment, the upper surface of the lid 20 constituting the contact surface of the independent mass member 16 in the housing 12 (contact member) is repeatedly deformed by the vibrator 54.
[0067]
Further, FIG. 6 shows a vibration damping device 102 as a fourth embodiment of the present invention. The vibration damping device 102 has a structure in which a damper mass 108 as a contact member (housing) is elastically supported by a vibration member 104 to be damped through a leaf spring 106 as a spring member. The damper mass 108 constitutes a secondary vibration system for the vibration member.
[0068]
More specifically, the leaf spring 106 is made of spring steel, has a thin rectangular plate shape as a whole, and is bent at one side in the plate thickness direction and the other side at the central portion in the longitudinal direction. Yes. Further, the loss coefficient of the leaf spring 106 is set to 0.07 or less. The leaf spring 106 has one end overlapped with the vibration member 104 and is fixed to the vibration member 104 with a bolt 110. Further, by fixing one end of the leaf spring 106 in the longitudinal direction to the vibration member 104 in this way, the leaf spring 106 is separated from the vibration member 104 from the intermediate portion to the other portion of the leaf spring 106. Yes. A damper mass 108 is attached to the protruding tip portion (the other end) of the leaf spring 106.
[0069]
Each of the damper masses 108 includes a damper mass main body 112 and a lid body 114 formed of an aluminum alloy or the like, and the elastic moduli of the damper mass main body 112 and the lid body 114 are all 5 × 10 5. ^Three It is set as MPa or more. The damper mass body 112 has an inverted cup shape that opens downward as a whole, and the inner diameter dimension of the inner hole 116 is substantially the same as the depth dimension of the inner hole 116. The lid 114 has a disk shape corresponding to the shape of the opening of the inner hole in the damper mass main body 112, and is press-fitted into the opening of the inner hole 116 of the damper mass main body 112 and fixed by welding or adhesion. ing. As a result, the opening of the damper mass body 112 is covered with the lid body 114, so that a storage space 118 is formed in the damper mass 108. Note that a stepped portion 120 extending in the circumferential direction is formed in the opening portion of the inner hole 116 of the damper mass body 112 for press-fitting positioning of the lid body 114, and the lid body 114 is fixed to the damper mass body 112. Below, the lid 114 is brought into contact with the stepped portion 120.
[0070]
In addition, a bolt 122 projects downward and is fixed to the central portion of the lower surface of the lid 114, and the bolt 122 is inserted into a mounting hole 124 formed at the other end in the longitudinal direction of the leaf spring 106. The nut 126 is screwed and fixed. As a result, the damper mass 108 is elastically supported by the vibration member 104 via the leaf spring 106, so that the sub-vibration system for the vibration member 104, which is the main vibration system, includes the damper mass 108 and the leaf spring 106. It is configured.
[0071]
Further, one independent mass member 16 is accommodated in the accommodation space 118 defined by the damper mass body 112 and the lid 114. Since the independent mass member 16 has the same structure as that of the first embodiment, the same reference numerals as those of the first embodiment are attached to the drawings, and the detailed description thereof is omitted.
[0072]
Further, in the state in which the independent mass member 16 is accommodated and disposed in the accommodation space 118, between the independent mass member 16 and the wall surface of the accommodation space 118, as in the first embodiment, around the entire circumference of the independent mass member 16. A predetermined gap is formed so that the independent mass member 16 can be independently displaced with respect to the wall surface of the accommodation space 118. In the present embodiment, the independent mass member 16 is configured to abut against the damper mass 108 on both sides in the main vibration input direction (vertical direction in FIG. 6). The size of the gap between 108 is set in the same manner as in the first embodiment.
[0073]
Further, a recess 128 is provided on the upper surface of the lid 114, and the magnetostrictive element 42 that constitutes a vibration means is disposed in the recess 128. Since the magnetostrictive element 42 has the same structure as that of the first embodiment, the same reference numerals as those of the first embodiment are used to omit detailed description thereof. In addition, a substantially flat rubber plate 130 is interposed between the opposing surfaces of the magnetostrictive element 42 and the lid 114, thereby allowing the magnetostrictive phenomenon of the magnetostrictive element 42 to be allowed. . The independent mass member 16 is accommodated in the accommodating space 118 while being placed on the magnetostrictive element 42. As is clear from this, in the present embodiment, the contact surface of the independent mass member 16 in the damper mass 108 is configured by the magnetostrictive element 42.
[0074]
When the vibration to be damped in the vibration member 104 exists in a plurality of frequency regions, the vibration damping device 102 having such a structure has a natural vibration of the sub-vibration system in any one of the plurality of frequency regions. By tuning the number, based on the resonance action of the sub-vibration system, an effective damping effect is exhibited for vibrations in one frequency region among the vibrations in a plurality of frequency regions to be damped. For vibrations in a frequency range other than the frequency range in which the natural frequency of the vibration system is tuned, the damper mass of the independent mass member 16 that is jumped and displaced with respect to the damper mass 108 using the magnetostriction phenomenon of the magnetostrictive element 42 is used. Therefore, when the vibration to be damped in the vibration member 104 is present in a plurality of frequency ranges, the vibration damping effect based on the contact with the contact with 108 can be exhibited. You can have, it is possible to exhibit an effective damping effect.
[0075]
As mentioned above, although several embodiment of this invention has been explained in full detail, these are illustrations to the last, Comprising: This invention is not limited at all by the specific description in this embodiment. .
[0076]
For example, in the first to fourth embodiments, one independent mass member is brought into contact with the contact member, but a plurality of independent mass members may be provided. Moreover, when employ | adopting a several independent mass member, these several independent mass members may have the same mass, and may have a mutually different mass.
[0077]
In the first to fourth embodiments, the contact surface of the independent mass member in the contact member is vibrated by the magnetostrictive element 42 and the vibrator 54, but the shape is deformed by applying an electric field. The contact surface of the independent mass member in the contact member may be vibrated by the electrostrictive element. Furthermore, the contact surface of the independent mass member in the contact member can be vibrated by pneumatic vibration. Specifically, for example, in the first embodiment, an opening window is formed in the lid, and a rubber plate that closes the opening window in a fluid-tight manner is disposed, whereby the contact of the independent mass member in the contact member is achieved. The contact surface is made of a rubber plate capable of shearing deformation in the vibration input direction. Then, by providing a working air chamber in which a part of the wall portion is formed by the rubber plate on the opposite side of the rubber plate against the contact surface of the independent mass member, and by exerting air pressure fluctuations on the working air chamber, You may make it vibrate the contact surface of a member.
[0078]
In the fourth embodiment, the spring member is made of spring steel. However, the present invention is also applicable to a vibration damping device in which the spring member is made of a rubber elastic body having a high damping characteristic. The invention is applicable. In particular, when the present invention is applied to a dynamic damper having a secondary vibration system using a spring member formed of a rubber elastic body as a spring component, for example, a spring member constituting the spring component of the secondary vibration system is formed. Even when the temperature of the elastic rubber member to be changed changes, and the loss coefficient and spring characteristics of the spring member change accordingly, an effective damping effect is obtained based on the contact of the independent mass member with the contact member. You can get it.
[0079]
Further, the shape of the contact surface of the independent mass member and the external shape of the independent mass member in the contact member are not limited to those of the first to fourth embodiments, and the installation space of the vibration damping device, etc. For example, the contact surface of the independent mass member in the contact member is made into a polygonal shape or a spherical shape, or the independent mass member is made into a circular rod shape or a flat plate shape. Is also possible.
[0080]
In the first to fourth embodiments, the contact member has a housing structure having an accommodation space therein, and the independent mass member is formed in the accommodation space formed inside the contact member. For example, a rod-shaped contact member whose outer peripheral surface has a circular cross section is attached to the vibration member, and an independent mass member having an annular shape or a cylindrical shape is attached to the contact member. By inserting and assembling, the hollow inner peripheral surface of the independent mass member may strike and contact the outer peripheral surface of the rod-shaped contact member.
[0081]
In the present invention, it is also possible to form a thin rubber film on the contact surface of the contact member. In that case, a hard material such as a metal whose rubber film is not attached to the independent mass member It is also possible to adopt directly.
[0082]
In the first to fourth embodiments, the jumping displacement of the independent mass member with respect to the contact member by the vibration means is generated in the vertical direction. The vibration of the contact surface of the mass member may be in the horizontal direction. Furthermore, in the first to fourth embodiments, in the contact member, the portion where the independent mass member is placed in a state where no vibration is input is directly vibrated by the vibration means. By vibrating the portion other than the portion where the independent mass member is placed by the vibration means, and exerting the excitation force on the portion where the independent mass member is placed, the independent mass member becomes the contact member. On the other hand, it may be made to jump and displace.
[0083]
In addition, although not enumerated one by one, the present invention can be carried out in a mode to which various changes, modifications, improvements and the like are added based on the knowledge of those skilled in the art. It goes without saying that all are included in the scope of the present invention without departing from the spirit of the present invention.
[0084]
【The invention's effect】
As is clear from the above description, in the vibration damping device structured according to the present invention, the vibration energy to be damped in the vibration member is small, for example, the acceleration of vibration in the vibration member is 1 G (gravity acceleration) or less. Even in this case, the independent mass member can jump up and displace by jumping up from the contact member, and the vibration damping effect based on the contact of the independent mass member with the contact member can be obtained extremely effectively. It is.
[0085]
Further, according to the method of the present invention, an effective damping effect can be exhibited in the vibration damping device having the structure according to the present invention as described above.
[Brief description of the drawings]
FIG. 1 is a longitudinal sectional view showing a vibration damping device as a first embodiment of the present invention.
FIG. 2 is a graph showing the result of simulating the frequency dependence of the vibration level of the vibration member on which the vibration damping device of the first embodiment is mounted.
FIG. 3 is a graph showing the result of simulating the frequency dependence of the vibration level of the vibration member on which the vibration damping device of the first embodiment is mounted.
FIG. 4 is a longitudinal sectional view showing a vibration damping device as a second embodiment of the present invention.
FIG. 5 is a longitudinal sectional view showing a vibration damping device as a third embodiment of the present invention.
FIG. 6 is a longitudinal sectional view showing a vibration damping device as a fourth embodiment of the present invention.
[Explanation of symbols]
10 Vibration control device
12 Housing
16 Independent mass members
42 Magnetostrictive element

Claims (12)

A contact member that is attached to the vibration member and receives vibration to be damped;
An independent mass member that is disposed in a non-adhering and independently displaceable manner with respect to the abutting member and is brought into direct and elastic contact with the corresponding abutting member, and a contact surface of the independent mass member in the abutting member are added. Vibration means for applying a jumping force from the contact member to the independent mass member by shaking,
A vibration damping device characterized by comprising: The said vibration means is attached to the said contact surface of the said independent mass member in the said contact member, and vibrates a corresponding contact surface directly by deforming a corresponding contact surface repeatedly. The vibration control device described in 1. 3. The control according to claim 1, wherein the abutting member is constituted by a housing having a hollow structure, and the independent mass member is accommodated and disposed in the housing as a circular cross-section having a spherical shape or a circular rod shape. Shaker. The damper mass is elastically supported by the vibration member via a spring member to constitute a sub-vibration system for the vibration member, and the contact member is provided integrally with the damper mass. 4. The vibration damping device according to any one of 3. The vibration damping device according to claim 4, wherein the damper mass is configured by the contact member. The vibration damping device according to claim 4 or 5, wherein a loss coefficient of the spring member is 0.07 or less. The vibration damping device according to claim 1, wherein a mass of the independent mass member is 5 to 20% of a mass of the vibration member. Contact surface in the vibration input direction of the contact member and the independent mass member so that at least one of the contact surfaces in the vibration input direction of the contact member and the independent mass member has a Shore D hardness of 80 or less. The vibration damping device according to any one of claims 1 to 7, wherein at least one of the members is formed of an elastic member. The independent mass member is brought into contact with the contact member on both sides in the vibration input direction to be damped in the vibration member, and the independent mass member is brought into contact with the corresponding contact member on both sides in the vibration input direction. The vibration damping device according to any one of claims 1 to 8, wherein a reciprocating movable distance between the surfaces is 0.1 to 1.6 mm. The vibration control device according to claim 1, wherein the contact member is formed of a rigid material having an elastic modulus of 5 × 10 ³ MPa or more. 11. The vibration damping device according to claim 1, wherein the vibration control unit controls the vibration unit to apply a vibration force including a random frequency component to the contact member. Control method of the vibration damping device. 11. The vibration damping device according to claim 1, wherein the excitation unit is controlled so that the excitation unit exerts an excitation force including a single or a plurality of frequency components on the contact member. A control method for a vibration damping device.

Images