JP4656433B2 - Vibration control device - Google Patents

Description

  The present invention relates to a vibration damping device having a novel structure that reduces vibration of a vibration input member that is a vibration damping target.

  Conventionally, as a vibration control device for reducing vibration of a vibration input member such as an automobile body, a window glass of a house, a fitting, etc., for example, an asphalt sheet or a rubber sheet attached to the surface of the vibration input member A vibration damper (dynamic vibration absorber) or the like in which a mass member is connected and supported via a spring member to a vibration input member is known.

  However, in both the vibration damping structure material and the dynamic damper, in order to obtain an effective vibration damping effect, a large sticking area and a mass of a large mass member are required, thereby increasing the weight. . In addition, since the characteristics of the asphalt that constitutes the damping structure and the rubber elastic body that constitutes the spring member of the dynamic damper are easily affected by temperature, the temperature dependence of the damping effect increases and the desired damping There was a problem that it was difficult to obtain stable effects.

  Moreover, in the dynamic damper, the vibration damping effect on the vibration input member is achieved by tuning the natural frequency of the sub-vibration system consisting of the mass-spring system to the vibration frequency range to be damped in the vibration input member as the main vibration system. However, there is a problem that such a damping effect is hardly exhibited only in a relatively narrow frequency range in which the secondary vibration system is tuned.

  In recent years, with the diversification of vibration input members and the improvement in required damping performance, for example, a damping device as disclosed in Patent Document 1 (Japanese Patent Laid-Open No. 2001-241498) has been proposed. . Such a vibration damping device has a structure in which an independent mass member is displaceable with a gap with respect to a rigid housing fixed to the vibration input member. By striking through an elastic contact surface, a vibration damping effect is obtained by utilizing energy loss due to sliding friction and collision at the time of hitting.

  However, it is sometimes difficult to obtain a sufficient damping effect with a hitting vibration damping device having a conventional structure. In particular, an effective damping effect is obtained for a plurality of vibrations in a wide frequency range. Sometimes it was difficult.

  Incidentally, in Patent Document 2 (Japanese Patent Application Laid-Open No. 07-293659), as in the above-mentioned Patent Document 1, a longitudinal rod shape with a circular cross section is used as a vibration control device that uses the vibration suppression effect by the striking of the independent mass member. The structure using the rod-shaped mass which has is disclosed. In this vibration damping device, a ball screw shaft, which is a vibration input member, has a hollow cylindrical shape, and a rod-shaped mass is inserted and accommodated in the center hole thereof. In particular, a plurality of bushes are externally spaced apart from each other in the axial direction of the rod-shaped mass, and by adjusting the mounting position of these bushes in the axial direction of the rod-shaped mass, the inherent characteristic of the rod-shaped mass in the radial direction It is said that the vibration control effect can be obtained in a plurality of frequency ranges by changing the frequency.

  However, it is difficult to think that it is possible to change and adjust the natural frequency of a single rod-shaped mass simply by changing the mounting position of the bush on the rod-shaped mass, and effective vibration suppression effects in multiple frequency ranges It is doubtful whether it is obtained. In addition, since the gap between the inner peripheral surface of the ball screw shaft and the outer peripheral surface of each bush is substantially constant, the striking action of the rod-shaped mass with respect to the ball screw shaft becomes simple. It is considered that the vibration frequency range where an effective vibration damping effect is exhibited must be narrow.

JP 2001-241498 A Japanese Patent Application Laid-Open No. 07-293659

  Here, the present invention has been made in the background as described above, and the problem to be solved is that the damping effect against small vibration and large vibration is advantageously exhibited in a plurality of or a wide frequency range. An object of the present invention is to provide a vibration damping device having a novel structure.

  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. Further, 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 an invention that can be understood by those skilled in the art from those descriptions. It should be understood that it is recognized based on thought.

That is, a feature of the present invention is that a plurality of contact mass portions that contact the vibration input member are spaced apart from each other, and the plurality of contact mass portions are connected by a spring member , and the vibration At least one corresponding contact mass portion is configured to be able to jump and displace as a whole independently from the input member , and all the corresponding contact mass portions in a stationary state do not simultaneously contact the vibration input member. Are separated from the vibration input member so that they are in a stationary state, and there are two or more types of stationary states in which the contact mass portions are in a contact state and a separate state in different combinations. It is in the damping device that can be tightened.

  In the vibration damping device having the structure according to the present invention, a plurality of abutting mass portions are connected by a spring member, thereby forming a mass-spring system for a vibration input member which is a main vibration system. A secondary vibration system is configured. Accordingly, when the vibration of the vibration input member is directly input to the spring member that is in contact with the vibration input member, or is input to the spring member via the contact mass portion that is in contact with the vibration input member, The spring member is elastically deformed, and bending vibration is generated in the spring member. Based on this bending vibration, a vibration damping effect (vibration damping effect) is exerted on the vibration input member.

  In addition, an excitation force is applied to the contact mass portion with the elastic deformation of the spring member, or the contact mass portion that has been in contact with the vibration input member is lifted from the vibration input member due to vibration. When the contact mass portion hits the vibration input member, a vibration damping effect based on energy loss due to sliding friction or impact is obtained.

  In particular, at least one contact mass portion contacts the vibration input member, and at the same time, at least one other contact mass portion is separated from the vibration input member, so that the stationary state with respect to the vibration input member can be taken. Thus, a plurality of types of placement states are realized by the contact mass portions having a plurality of different combinations of contact states and separation states. This abutting state refers to a state where the abutting mass portion abuts against the vibration input member in at least one kind of stationary state, and the separated state refers to at least one abutting mass portion against the vibration input member. This refers to a state of separation in a kind of stationary state.

  Accordingly, since the stationary state becomes unstable because all the contact mass portions are not in contact with each other in the stationary state, the vibration damping device can be easily displaced and separated even if there is even a small vibration. The state in which the contact mass portion that has been in contact with the vibration input member is easily taken. In short, the abutting mass portion can be made to hit the vibration input member even when a minute vibration is input that allows only a slight displacement of the vibration damping device as a whole.

  In addition, since the plurality of contact mass portions are in a stationary state and take a plurality of different combinations of contact states and separated states, the contact of the contact mass portions with the vibration input member becomes simple. In other words, various hitting modes are generated depending on the magnitude and frequency range of vibration.

  Therefore, in addition to the vibration suppression effect based on the bending vibration described above, the vibration suppression effect based on the energy loss due to sliding friction and impact is advantageously exerted, and the vibration suppression against a small vibration or a large vibration in a plurality of or a wide frequency range. The vibration effect can be obtained effectively.

  In the present invention, it is desirable that the mass difference between the contact mass portions is reduced to such an extent that the masses of the plurality of contact mass portions are substantially equated. Due to this, there is a large mass difference between the contact mass portion that is in contact with the vibration input member and the contact mass portion that is separated from the vibration input member, and the stationary state is stabilized. When the vibration is input, such a problem that the contact mass portions that are separated from each other do not contact the target vibration input member is solved.

  In the present invention, preferably, the primary natural frequency in the vibration damping device is tuned with respect to the frequency range of vibration to be damped by the vibration input member. Thereby, the fundamental vibration is tuned to the vibration of the resonance frequency of the vibration input member, and the desired vibration damping effect can be obtained more stably.

Further, in the vibration damping apparatus according to the present invention, a plurality of contact mass unit, respectively, is an abutment for the vibration input member at least one stationary state of the two or more Rutotomoni, said two or more structure are separated state and against the vibration input member at least one stationary state, may be employed. According to such a structure, a mode in which all of the abutting mass portions abut on the vibration input member is realized, and the vibration damping effect based on the mass power can be further improved.

  In the vibration damping device according to the present invention, a structure in which a leaf spring is employed as the spring member is preferably employed. As a result, in addition to facilitating the tuning of the damping performance based on the bending strength, mass, etc. of the leaf spring, the contact state and separation state of the contact mass portion in the stationary state are based on the rigidity of the leaf spring. It is held stably.

  In the vibration damping device according to the present invention, a structure in which the contact mass portion is integrally formed with the leaf spring may be employed. Thereby, the vibration damping device can be realized with a simple structure.

  In the vibration damping device according to the present invention, a structure in which the contact mass portion is formed separately from the spring member and is fixed to the spring member may be employed. Thereby, the design of the mass of the contact mass portion can be changed without being influenced by the design of the spring member.

  In the vibration damping device according to the present invention, a structure in which the contact surface of the contact mass portion and the vibration input member is formed of a rubber elastic body may be employed. According to such a structure, using the elasticity of the rubber elastic body, it is possible to suppress the magnitude of the hitting sound that accompanies the contact of the contact mass portion with the vibration input member. The rubber elastic body may be configured by forming the contact mass portion itself with a rubber elastic body. When the contact mass portion is formed of a hard material, a rubber layer may be attached to the contact mass portion. If the contact mass portion and the vibration input member are both hard materials, a rubber layer may be formed on at least one of the contact surfaces. Incidentally, when the contact mass portion also contacts other members other than the vibration input member, it is desirable that the contact surface between the other member and the contact mass portion is also made of a rubber elastic body.

  In the vibration damping device according to the present invention, a structure in which a plurality of contact mass portions are arranged on a plurality of straight lines intersecting each other may be employed. According to such a structure, a plurality of contact mass portions can be brought into contact with each other over a wide range in the vibration input member, thereby further improving the damping performance against vibration in a wider frequency range. .

  Further, in the vibration damping device according to the present invention, a support portion is formed that is positioned at the center of gravity of the plurality of contact mass portions as a whole and is brought into contact with the vibration input member in any stationary state. The structure is preferably employed. According to this structure, all the plurality of contact mass portions do not simultaneously contact the vibration input member, and the stationary state in which at least one contact mass portion is separated from the vibration input member is stabilized by the support portion. . In short, since the unstable stationary state is suitably maintained with respect to the vibration input member, the vibration damping effect based on hitting can be more advantageously exhibited.

  Moreover, in the vibration damping device according to the present invention, a structure in which the support portion is formed as one of the contact mass portions is preferably employed. Thereby, the further expansion of the aspect in which the contact mass portion contacts the vibration input member can be achieved while the number of parts is reduced.

  Further, in the vibration damping device according to the present invention, it is possible to employ a structure in which positioning means that engages with the support portion and restricts free displacement is formed in the vibration input member. According to such a structure, the vibration damping device is prevented from unnecessarily moving on the surface of the vibration input member, and is stably positioned at a predetermined place on the vibration input member. Therefore, it is possible to hit a plurality of contact mass portions against the target position of the vibration input member, and the desired vibration damping effect can be obtained more stably.

  Further, in the vibration damping device according to the present invention, the spring member is configured by a leaf spring extending radially around the support portion, and a structure in which a contact mass portion is provided at each of the tip portions of the leaf springs. , May be adopted. According to such a structure, an unstable stationary state is suitably maintained by the support portion, and a plurality of contact mass portions can be contacted in a wide range in the vibration input member.

  Further, in the vibration damping device according to the present invention, the spring member is constituted by one leaf spring that linearly extends on both sides with the support portion interposed therebetween, and contact mass portions are provided at both end portions of the leaf spring. A structure may be adopted. Accordingly, at least two types of stationary are provided in which the one (other) contact mass portion is brought into contact with the vibration input member with the support portion interposed therebetween, and the other (one) contact mass portion is separated from the vibration input member. The state can be advantageously realized. In addition, it is possible to cause both contact mass portions sandwiching the support portion to simultaneously strike the vibration input member based on the bending deformation of the spring member. Further, it is possible to alternately abut the abutting mass portions on both sides of the support portion against the vibration input member, and a vibration damping device having a novel structure that moves like a so-called seesaw can be suitably realized.

Further, in the vibration damping device according to the present invention, by adopting a structure that allows the jump displacement as a whole independently of the vibration input member, the jump displacement of the contact mass portion and the bending deformation of the spring member are adopted. Thus, the tuning performance of the damping effect based on the jumping displacement and the bending deformation can be further improved.

  In the vibration damping device according to the present invention, a rigid housing having a hollow structure fixed to the vibration member to be damped is provided, and a spring member in which a plurality of contact mass portions are connected is accommodated in the housing. Accordingly, a structure in which the vibration input member is configured by the housing and the entire spring member in which the abutting mass portion is connected to the housing can be jumped and displaced independently may be employed. According to such a structure, the positioning with respect to the vibration input member is stabilized by being accommodated in the housing, and the desired vibration damping effect can be stably obtained. In addition, with the setting change of the separation distance between the wall portion of the housing and the contact mass portion, tuning of the vibration damping performance by hitting becomes easy.

  Hereinafter, in order to clarify the present invention more specifically, embodiments of the present invention will be described. First, FIG. 1 shows a vibration damping device 10 as a first embodiment of the present invention. The vibration damping device 10 includes an elastic plate 12 as a spring member and a mass portion 14, and is disposed so as to be superimposed on an automobile body 16 as a vibration member that is a member to be damped. As a result, the vibration damping device 10 is mounted on the body 16 which is the main vibration system, and constitutes a sub vibration system for the main vibration system. In the present embodiment, since the vibration damping device 10 is placed on the surface of the vehicle body 16, the vehicle body 16 is configured as a vibration input member that directly inputs vibration to the vibration damping device 10. Yes.

  More specifically, the elastic plate 12 is formed using a leaf spring made of a metal material such as steel or aluminum alloy, a resin material such as nylon resin, or a composite material thereof. The elastic plate 12 is appropriately set in size, mass, and shape in accordance with the shape and size of the mounting portion of the automobile body 16 that is a vibration input member, the mass of the mounting portion, the frequency range of vibration, and the like. Although not particularly limited, it is preferably a rectangular plate shape as shown.

  In particular, in the present embodiment, the elastic plate 12 is set to have a sufficiently large length dimension with respect to the thickness dimension so that bending deformation occurs. Length dimension: L is the dimension in the longitudinal direction of the elastic plate 12 (the direction extending between the upper left and lower right in FIG. 1). Thickness dimension: Length dimension with respect to t: L is preferably 50 ≦ L / t ≦ 10000, more preferably 100 ≦ L / t ≦ 1000. The planar shape is not necessarily rectangular, but is desirably rectangular in order to cause stable bending deformation. In that case, the width dimension B is set to 1 ≦ L / B ≦ 10 in order to effectively give a vibration damping force to the automobile body 16.

  Further, the bending strength of the elastic plate 12 depends on the magnitude of the input vibration, the rigidity (strength) of the automobile body 16, the resting state of the elastic plate 12 on the automobile body 16, which will be described later, and the like. This will be taken into account when determining the size.

  On the other hand, the mass portion 14 is configured by a rectangular plate-shaped portion that is a predetermined length from each end edge in the longitudinal direction of the elastic plate 12 toward the center. That is, the pair of mass portions 14 and 14 are separated from each other and connected by the elastic plate 12, and particularly have a structure in which the elastic plate 12 is integrally formed with both ends of the elastic plate 12 in the longitudinal direction. . An additional mass 18 is provided at one end (surface) in the thickness direction of each mass portion 14 (upper in FIG. 1). The additional mass 18 is made of a heavy material such as a rectangular metal material, and its lower surface is fixed to the surface of the mass portion 14.

  A contact rubber layer 20 is provided on the other end (surface) in the thickness direction of each mass portion 14 (lower side in FIG. 1). The contact rubber layer 20 is made of a rubber elastic body having a thin, substantially rectangular flat plate shape, and the upper surface thereof is formed on the surface of the mass portion 14. As the material of the contact rubber layer 20, various rubber elastic materials such as diene rubber such as natural rubber and chlorine rubber can be adopted. In this embodiment, when the mass portion 14 and the automobile body 16 hit each other. Since the contact rubber layer 20 is employed mainly for the purpose of suppressing the hitting sound when the hitting sound becomes a problem, the rubber material and the rubber hardness are not particularly limited. When the elastic plate 12 is a resin material, the contact rubber layer 20 is often unnecessary. However, for the purpose of reducing the hitting sound, a rubber elastic material having a Shore D hardness of 20 to 40 is suitably employed as the contact rubber layer 20.

  The thickness dimension of the contact rubber layer 20 is substantially constant throughout, and is preferably 0.1 to 0.3 mm. When it is covered and smaller than 0.1 mm, it is difficult to obtain the desired sound reduction effect particularly when low frequency large amplitude vibration is input. On the other hand, when it is larger than 0.3 mm, it is based on the hit of the elastic plate 12. This is because the vibration damping force is absorbed by the contact rubber layer 20 relatively large, and the desired vibration damping effect may not be obtained.

  Further, the length dimension from the end of one mass portion 14 to the center of the elastic plate 12 is equal to the length dimension l1 from the end of the other mass portion 14 to the center of the elastic plate 12 is equal to l2. A central protrusion 22 as a support portion is provided at the longitudinal center portion of the plate 12. As is clear from this, the total length of the length dimension 11 and the length dimension 12 is the length dimension (full length) of the elastic plate 12: L.

  The central protrusion 22 is formed using a rubber elastic body, and is vulcanized on the other surface in the thickness direction (the lower side in FIG. 1) which is the side to which the contact rubber layer 20 of the elastic plate 12 is fixed. It is fixed by bonding or the like. The Shore D hardness of the central protrusion 22 is not particularly limited, and may be 20 to 40, for example, as with the contact rubber layer 20. In particular, the central protrusion 22 has a substantially constant semicircular cross section that protrudes downward, and has a bowl shape that extends continuously in the width direction of the elastic plate 12, so that the outer peripheral surface of the central protrusion 22 is The curved surface is curved in the longitudinal direction of the elastic plate 12.

  The central portion of the central protrusion 22 in the width direction (the direction extending between the upper left and the lower right in FIG. 1) is positioned at the longitudinal central portion of the elastic plate 12. Further, since the height dimension of the central portion in the width direction of the central protrusion 22 is made larger than the thickness dimension of the contact rubber layer 20, the central portion in the width direction of the central protrusion 22 becomes the contact rubber layer. Compared with 20, it protrudes greatly downward from the elastic plate 12.

  In short, the elastic plate 12 is constituted by a single flat plate-like plate spring that extends linearly on both sides across the central central protrusion 22, and the shape, size, and mass of both ends of the elastic plate 12 are mutually different. Each pair of mass portions 14, additional masses 18, and contact rubber layers 20 that are made of the same material are provided, so that both sides of the central protrusion 22 are symmetrical to each other. That is, the protruding height of each contact rubber layer 20 from the elastic plate 12 is the same. Here, the contact mass portion according to the present embodiment includes the mass portion 14 and the contact rubber layer 20. As a result, the center of the central protrusion 22 is positioned at the center of gravity of the elastic plate 12 having two contact mass portions.

  Further, the natural frequency of the vibration damping device 10 is tuned based on its mass. The mass of the vibration damping device 10 is determined in consideration of vibration energy to be damped. In general, about 0.05 to 10% of the mass of the vibration suppression target portion in the automobile body 16 is preferable, and more preferable. Is 0.1 to 5%. This is because if the mass is too small, it is difficult to obtain a sufficient vibration damping effect, while if the mass is too large, weighting becomes a problem.

  As specific tuning of the mass, in addition to setting and changing the weight of the additional mass 18 and the contact rubber layer 20, the length, width, and thickness of the elastic plate 12 are set and changed. It has been confirmed from the experiments and examination results of the present inventor that the natural frequency shifts to the low frequency side when the width dimension of the elastic plate 12 is longer than the length dimension. In this embodiment, only the length dimension is changed in a form in which the thickness dimension is sufficiently smaller than the length dimension and the width dimension is smaller than the length dimension. Thus, the natural frequency of the vibration damping device 10 is tuned.

  Such a vibration damping device 10 is mounted on the vehicle body 16 by placing the central protrusion 22 on a portion of the vehicle body 16 that is subject to vibration suppression. Here, a concave groove 24 as a positioning means is provided in the vibration suppression target portion of the body 16. The concave groove 24 extends in a predetermined length with a substantially constant arc-shaped cross section that opens upward. In particular, the curvature of the inner surface of the concave groove 24 having an arc shape is larger than the curvature of the outer peripheral surface of the central protrusion 22, so that the inner surface of the concave groove 24 is compared with the outer peripheral surface of the central protrusion 22. Are greatly curved in the width direction (the direction extending between the upper left and lower right in FIG. 1).

  The center of the center protrusion 22 is placed on the bottom surface of the center of the groove 24 so that the width direction of the center protrusion 22, that is, the longitudinal direction of the elastic plate 12 extends in parallel with the width direction of the groove 24. Thereby, the center protrusion 22 is engaged with the concave groove 24 in the width direction, and the displacement in the longitudinal direction of the elastic plate 12 is limited.

  As shown in FIGS. 2 and 3, the center of the central protrusion 22 is placed on the bottom surface at the center of the concave groove 24, and the elastic plate 12 and the automobile body 16 extend substantially parallel to each other. In the state, the contact rubber layers 20 provided at both ends in the longitudinal direction (left and right in FIGS. 2 and 3) of the elastic plate 12 are positioned at substantially the same height from the automobile body 16. In the present embodiment, since the surface of the vibration suppression target portion and the surface of the elastic plate 12 in the automobile body 16 are flat with each other, the separation distance between each contact rubber layer 20 and the automobile body 16 is substantially the same. However, when these surfaces have a shape with irregularities or the like, the separation distance between each contact rubber layer 20 and the vehicle body 16 may be different from each other depending on the shape.

  Further, the inner surface of the concave groove 24 is greatly curved in the width direction as compared with the outer peripheral surface of the central protrusion 22. Therefore, displacement in the width direction of the elastic plate 12 in which the central protrusion 22 and the groove 24 extend in parallel with each other is allowed.

  Further, since the central protrusion 22 is freely supported with respect to the body 16 except that the central protrusion 22 is engaged with the concave groove 24 in the width direction, the central protrusion 22 is lifted from the body 16 so that the elastic plate 12 is in the body. As the center protrusion 22 abuts against the body 16 again, the displacement in the direction in which the elastic plate 12 approaches the body 16 (up and down in FIGS. 2 and 3) is allowed.

  Furthermore, as the outer circumferential surface of the central protrusion 22 abuts the inner surface of the concave groove 24 and the surface continuously abutting along the direction of curvature of the inner surface of the concave groove 24 changes, Displacement in a direction (up and down in FIGS. 2 and 3) in which the mass portions 14 positioned at both ends approach / separate from the body 16 is allowed. In particular, in the form in which the central protrusion 22 is fitted in the concave groove 24 of the body 16, the initial shape in which the elastic plate 12 spreads flat is maintained, and one mass portion 14 is interposed through the contact rubber layer 20. In the state where it abuts against 16, the other mass portion 14 is separated from the body 16. That is, both the mass portions 14 and 14 are alternately brought into contact with the body 16 with the central protrusion 22 interposed therebetween, whereby the elastic plate 12 is displaced like a seesaw.

  In particular, in the present embodiment, since the central protrusion 22 is located at the approximate center of gravity of the vibration damping device 10, the center of the central protrusion 22 is placed on the bottom surface at the center of the concave groove 24 and the elastic plate 12. And the vehicle body 16 extend substantially in parallel with each other, and the pair of mass portions 14 and 14 of the elastic plate 12 are positioned to be spaced apart from the vehicle body 16 at substantially the same height. The first stationary state as one of the stationary states with respect to is taken. One mass portion 14 abuts the body 16 via the abutting rubber layer 20 with the central projection 22 fitted in the concave groove 24 of the body 16 interposed therebetween, and the other mass portion 14 is separated from the body 16. In the separated state, a second stationary state is generated as one of the stationary states. Furthermore, one mass portion 14 is separated from the body across the central protrusion 22 fitted in the concave groove 24 of the body 16, and the other mass portion 14 contacts the body 16 via the contact rubber layer 20. In the contacted state, a third stationary state is taken as one of the stationary states.

  In short, in any of the first to third stationary states, the central protrusion 22 and the pair of mass portions 14 and 14 do not all come into contact with the body 16 at the same time. , 14 abuts on the body 16, and at the same time, at least one of the central protrusion 22 and the mass portions 14, 14 is separated from the body 16 so as to be in a stationary state. Further, in the present embodiment, three stationary states in which the central protrusion 22 and the mass portions 14 and 14 are brought into a contact state and a separated state by different combinations are generated.

  The elastic plate 12 is a hard leaf spring having rigidity sufficient to at least take the above-described stationary state. Moreover, although it is said that there are the above three cases in the stationary state according to the present embodiment, in the first stationary state, the balance of the contact mass portions on both sides of the central protrusion 22 is balanced. Since it is realized when it is taken, there may be substantially two cases of the second stationary state and the third stationary state.

  In the vibration damping device 10 stationary on the body 16 as described above, when a relatively large vibration is generated in the body 16, the vibration damping device 10 is lifted from the body 16 and comes into contact with the body 16. In particular, since the central protrusion 22 is positioned at the center of gravity of the vibration damping device 10 and protrudes downward from the contact rubber layer 20, the central protrusion 22 is most likely to hit the body 16. In the present embodiment, since the central protrusion 22 functions as an abutting mass portion, the mass portions 14 and 14 on both sides of the elastic plate 12 sandwiching the central protruding portion 22 and the abutting rubber layer 20 are added to be elastic. Three contact mass portions are arranged at equal intervals on a single straight line extending in the longitudinal direction of the plate 12.

  Further, when a relatively large vibration is input in the thickness direction of the elastic plate 12 (up and down in FIGS. 2 and 3), the central protrusion 22 contacts the body 16 and the central protrusion 22 of the elastic plate 12. One end portion sandwiching the body is displaced so as to approach the body 16 and the other end portion is separated from the body 16, and the mass portion 14 provided at one end portion passes through the contact rubber layer 20. Then hit the body 16 (see the broken line diagram in FIG. 3). Alternatively, as indicated by a broken line in FIG. 2, the portions on both sides of the elastic plate 12 sandwiching the central protrusion 22 are symmetrically bent and deformed, and a pair of mass portions 14, 14 at both ends of the elastic plate 12. May hit the body 16 through the contact rubber layer 20 at the same time.

  Further, when vibration is input in the longitudinal direction (left and right in FIGS. 2 and 3) of the elastic plate 12 with the central protrusion 22 fitted in the concave groove 24 of the body 16, the outer peripheral surface of the central protrusion 22. As the surface continuously contacting along one of the curved directions of the inner surface of the concave groove 24 changes while the inner surface of the concave groove 24 is in contact with the inner surface of the concave groove 24, one mass portion 14 causes the contact rubber layer 20 to And the other mass portion 14 is separated from the body 16 (see the broken line in FIG. 3). In addition, since both the mass portions 14 and 14 are symmetrical to each other, one mass portion 14 is separated from the body 16 and the other mass portion 14 abuts according to the magnitude and direction of vibration. The body 16 may be hit through the rubber layer 20 (refer to the one-dot chain line diagram in FIG. 3).

  Furthermore, the vibration in question is input in the longitudinal direction of the elastic plate 12 so that the central protrusion 22 alternately passes between both wall portions in the width direction (left and right in FIG. 3) of the concave groove 24. When the contact surface changes while the outer peripheral surface of the central protrusion 22 is in contact with the inner surface of the concave groove 24, the one mass portion 14 and the other mass portion 14 sandwich the body 16 with the central protrusion 22 interposed therebetween. On the other hand, the contact state and the separation state are alternately set.

  In addition, a relatively small vibration is input in the thickness direction of the elastic plate 12 in a state where the central protrusion 22 contacts the body 16 and the mass portions 14 and 14 at both ends of the elastic plate 12 are separated from the body 16. As a result, the portions on both sides of the elastic plate 12 sandwiching the central protrusion 22 are bent and deformed, and bending vibration is generated. A vibration damping effect is obtained based on this bending vibration.

  In particular, in the present embodiment, the primary natural frequency of the vibration damping device 10 is tuned to the vibration frequency of the primary mode of the body 16 to be damped. Therefore, due to the bending resonance of the elastic plate 12, the vibration damping effect based on the bending vibration of the elastic plate 12 can be advantageously exerted, and the mass portions 14 on both sides of the elastic plate 12 can efficiently hit the body 16. The elastic plate 12 is lifted from the body 16 efficiently, and the central protrusion 22 hits the body 16. Thus, a vibration damping effect based on energy loss due to sliding friction or impact is advantageously obtained.

  In the vibration damping device 10 as described above, the central projection 22 and the mass portion 14 are not left in contact with the body 16 at the same time, while the central projection 22 and the pair of mass portions 14 and 14 are not in contact with the body 16 at the same time. , 14 is in contact with the body 16 and at the same time, at least one of the central protrusion 22 and the mass portions 14, 14 is separated from the body 16 and is allowed to stand still. Another mass part 14 or the central protrusion 22 abuts the body 16 and the other mass part 14 or the central protrusion 22 is separated from the body 16 by a small vibration that easily breaks the balance. A kind of stationary state can be easily realized.

  In addition, a plurality of abutments configured to include a pair of mass portions 14 and 14 and the central protrusion 22 by being placed in a plurality of types (three types in the present embodiment) of stationary states. The hitting of the mass portion against the body 16 cannot be simple, and various hitting modes are generated according to the magnitude and frequency range of vibration.

  Therefore, in addition to the vibration suppression effect based on the bending vibration described above, the vibration suppression effect based on the energy loss due to sliding friction and impact is advantageously exerted, and the vibration suppression against a small vibration or a large vibration in a plurality of or a wide frequency range. The vibration effect can be obtained effectively.

  In particular, the center protrusion 22 is fitted into the groove 24 and is mounted on the automobile body 16, so that the positioning with respect to the body 16 is ensured, and the width dimension of the groove 24 is the width of the center protrusion 22. By making it larger than the dimension, when the central protrusion 22 jumps up from the body 16 and hits the body 16, it is supported stably. As a result, the central protrusion 22 and the mass portion 14 can be hit against the vibration suppression target portion of the body 16 with high accuracy, and the desired vibration suppression effect can be obtained more stably.

  Further, in the present embodiment, the contact surfaces of the central protrusion 22 and the concave groove 24 are curved, so that it can be smoothly contacted in the bending direction. Thus, it is possible to tune the vibration damping effect based on the bending vibration of the elastic plate 12 and the vibration damping effect based on the hitting of the central protrusion 22.

  Next, FIG. 4 shows a vibration damping device 30 as a second embodiment of the present invention. In the following description, members and parts having substantially the same structure as those of the first embodiment are denoted by the same reference numerals as those of the first embodiment, and detailed description thereof is omitted.

  Specifically, the contact rubber layer 20 according to the present embodiment is vulcanized and bonded with a substantially constant thickness over the entire surface of the elastic plate 12 opposite to the side where the additional mass 18 is provided.

  Further, a central protrusion 22 as a support portion that functions as one of the contact mass portions is provided between the elastic plate 12 and the central portion of the contact rubber layer 20. The central protrusion 22 according to the present embodiment is formed using a hard metal material or the like having a substantially cylindrical shape, and is elastic so as to extend in parallel with the width direction of the elastic plate 12 or the contact rubber layer 20. It is sandwiched between the plate 12 and the central portion of the contact rubber layer 20 and fixed to at least one of them. Thereby, the center of the contact rubber layer 20 to which the central protrusion 22 is fixed is curved and protrudes so as to bulge outward by the size of the central protrusion 22.

  Such a vibration damping device 30 has a structure in which a pair of mass portions 14 and 14 are provided on both sides of the central protrusion 22 as in the first embodiment. The central protrusion 22 is in contact with the body 16 through the contact rubber layer 20 and the mass parts 14 on both sides are not in contact with the body 16 at the same time. The stationary state in which 14 is separated from the body 16, the stationary state in which one mass portion 14 is abutted and the other mass portion 14 is separated while the central protrusion 22 is in contact with the body 16, and the one mass portion There are three types of stationary state in which the other mass portion 14 abuts while the 14 is separated.

  As a result, as in the first embodiment, based on the unstable stationary state in which all of the contact mass portions do not contact the body 16 at the same time, the mass portion 14 and the like can be moved to the body 16 even when a small amplitude vibration is input. The vibration damping effect can be advantageously exhibited.

  In particular, in the present embodiment, the contact rubber layer 20 is formed on the entire surface of the elastic plate 12 so that the bending resonance of the elastic plate 12 is tuned by the elasticity of the contact rubber layer 20. You can also

  Next, FIGS. 5 to 6 show a vibration damping device 40 as a third embodiment of the present invention.

  Specifically, the central portion of the elastic plate 12 according to the present embodiment is bent, and one plate portion 42 and the other plate portion 44 sandwiching the center of the elastic plate 12 are relatively inclined at a predetermined angle. ing. In other words, the pair of plate portions 42 and 44 made of leaf springs are integrally formed with each other so as to be connected in the longitudinal direction (left and right in FIGS. 5 and 6) while being relatively inclined at a predetermined angle. ing.

  Each plate portion 42, 44 is provided with a plurality of contact rubber masses 46 as contact mass portions (two in this embodiment, each plate portion 42, 44). The abutting rubber mass 46 is formed using a hard rubber elastic body and has a substantially hemispherical shape that protrudes downward, with a predetermined distance in the longitudinal direction of the plate portions 42 and 44. It is arranged. The substantially circular upper surface of the contact rubber mass 46 is fixed to the lower surfaces of the plate portions 42 and 44 by vulcanization bonding or the like when the elastic plate 12 is arranged so as to protrude downward. . In short, the contact rubber mass 46 according to the present embodiment is formed separately from the elastic plate 12 and is fixed to the elastic plate 12.

  Accordingly, two contact rubber masses 46 and 46 are arranged on one straight line extending in the longitudinal direction of one plate portion 42, and 2 on one straight line extending in the longitudinal direction of the other plate portion 44. Two abutting rubber masses 46, 46 are arranged, and these two straight lines intersect each other at the bent central portion of the elastic plate 12.

  In such a vibration damping device 40, the pair of abutting rubber masses 46, 46 in one plate portion 42 abuts on the flat surface of the vibration suppression target portion of the automobile body 16, so that the one plate portion 42 is A pair of abutting rubber masses 46, 46 that extend substantially parallel to the surface of the body 16 and are separated from the body 16 in a form in which the other plate portion 44 is inclined with respect to the surface and fixed to the other plate portion 44. Also, one of the stationary states is taken away from the body 16. On the other hand, when a pair of contact rubber masses 46 and 46 fixed to the other plate portion 44 abut on the body 16, one plate portion 42 and the contact rubber masses 46 and 46 fixed to the plate portion 42 are provided. Is placed in a stationary state in a state of being separated from the body 16.

  That is, in this embodiment, when focusing on each of the pair of contact rubber masses 46 and 46 fixed to the one plate portion 42 and the pair of contact rubber masses 46 and 46 fixed to the other plate portion 44, All of the contact rubber masses 46, 46 in the other plate portion 42 (44) are brought into contact with the body 16 in one stationary state, and are separated from the body 16 in another stationary state. It is done.

  In the present embodiment, the protruding tip surfaces of the contact rubber masses 46 on both sides of the center bent portion of the elastic plate 12 are positioned below the tip surface of the center bent portion. As a result, the central abutting rubber mass 46 of the one plate portion 42 and the central abutting rubber mass 46 of the other plate portion 44 abut against each other against the body 16, and from the center of the respective plate portions 42, 44. In a state where the separated contact rubber masses 46 are separated from the body 16, the elastic plate 12 is substantially V-shaped in a side view so that one of the stationary states is taken.

  In the vibration damping device 40 having the above-described structure, as in the first embodiment, based on the unstable stationary state in which all of the contact mass portions of the elastic plate 12 do not contact the body 16 simultaneously, Even when a small amplitude vibration is input, it is possible to effectively hit the contact rubber mass 46 against the body 16, whereby the vibration damping effect can be advantageously exhibited.

  In particular, in the present embodiment, the contact rubber mass 46 formed of a rubber elastic body is formed separately from the elastic plate 12, so that the design change such as the mass in the contact mass portion and the elasticity of the contact portion is free. The degree can be increased, thereby further improving the intended vibration damping effect.

  Moreover, in the present embodiment, all of the contact rubber masses 46, 46 on the plate portions 42, 44 on both sides across the center of the elastic plate 12 are brought into contact with the body 16 in one stationary state, and Since it is separated from the body 16 in another stationary state, the damping effect is effectively exhibited based on the large mass of the pair of contact rubber masses 46, 46 in the plate portions 42, 44. obtain.

  Next, FIGS. 7 to 8 show a vibration damping device 50 as a fourth embodiment of the present invention.

  Specifically, a pair of elastic plates 12 including a pair of mass portions 14 and 14 according to the present embodiment are provided. The elastic plates 12a and 12b are superposed and fixed in the thickness direction (up and down in FIG. 7) at the center so that they are substantially orthogonal to each other. In short, in this embodiment, the two mass portions 14 are arranged on two straight lines that intersect each other.

  Further, the contact rubber mass 46 is fixed to the surface of the elastic plate 12b located below the central portion where the two elastic plates 12a and 12b are overlapped, so that the contact rubber mass 46 is controlled by the vibration damping device. It is positioned at the approximate center of gravity of 50. As a result, the elastic plate 12 is constituted by a leaf spring extending radially around the abutting rubber mass 46, and the mass portion 14 is provided at the tip portion of the leaf spring.

  In the present embodiment, the abutting rubber mass 46 abuts on the body 16, and the four mass portions 14 are formed by separating the elastic plates 12 a and 12 b from the body 16 so as to extend substantially parallel to the surface of the body 16. One of the stationary states is taken away from the body 16. In the state where each elastic plate 12a, 12b extends substantially parallel to the surface of the body 16, the same standard elastic plate 12 is employed, so that each mass portion of the elastic plate 12a positioned above the overlapping portion is used. 14 and the contact rubber layer 20 attached to the respective mass portions 14 of the elastic plate 12b positioned at the lower side of the overlapping portion. The separation distance in the body 16 is made larger than d2.

  In addition, in a state where the contact rubber mass 46 is in contact with the body 16, a pair of mass portions 14 and 14 that are adjacent to each other in the circumferential direction around the overlapping portion of the pair of elastic plates 12 a and 12 b abut on the body 16. The pair of mass portions 14, 14 opposed to each other with the mass portion 14 in contact with the central portion of the elastic plate 12 sandwiched from the body 16 are allowed to stand still. In this embodiment, since the four mass portions 14, 14, 14, and 14 are provided, there are four types of the above-described stationary states.

  In the vibration damping device 50 configured as described above, as in the first embodiment, based on the unstable stationary state in which all of the contact mass portions of the elastic plate 12 do not contact the body 16 at the same time, Even when a small amplitude vibration is input, the mass portion 14 can be effectively abutted against the body 16, whereby the damping effect can be advantageously exhibited.

  In particular, in this embodiment, in addition to the two mass portions 14 and 14 being provided on two straight lines intersecting each other, the elastic plate 12 is a leaf spring that extends radially around the contact rubber mass 46. Since the mass portion 14 is provided at the tip portion of the leaf springs, many types (5 in the present embodiment) of stationary states are realized, and the body 16 Thus, the mass portion 14 can be brought into contact over a wide range, and the damping effect according to various vibrations can be improved.

  Furthermore, in the present embodiment, the above-described radially extending leaf springs are configured by superimposing them using a pair of elastic plates 12a, 12b of the same standard, thereby simplifying the structure and reducing the structure. Costing can be advantageously achieved. In addition, by separating the elastic plates 12, the separation distances of the mass portions 14 of the elastic plates 12 a and 12 b from the body 16 can be made different in a state where the elastic plates 12 a and 12 b are positioned parallel to the body 16. Accordingly, tuning of the damping effect based on the hitting action can be realized with a simple structure.

  Next, FIG. 9 shows a vibration damping device 60 as a fifth embodiment of the present invention. The vibration damping device 60 has a structure in which the elastic plate 12 having the mass portion 14 is accommodated and disposed in a housing 62 as a vibration input member that is fixed to the body separately from the automobile body 16 as a vibration member. Presents.

  Specifically, the housing 62 includes a rectangular cup-shaped vessel member 64 and a rectangular flat plate-shaped lid member 66. The inner and outer peripheral surfaces of the bottom wall portion 68 and the peripheral wall portion 70 of the container member 64 are flat. The housing 62 is formed using, for example, a hard material such as a metal material such as iron or aluminum alloy, a synthetic resin material such as FRP, or a composite material thereof. In addition, a concave groove 24 that extends linearly in the width direction is provided in the center portion of the bottom wall portion 68. Although not clearly shown in the drawing, the container member 64 is provided with a fixing portion for fixing to the automobile body 16. For example, a structure in which the fixing portion is formed to protrude at a plurality of locations on the outer peripheral surface of the vessel member 64 and provided with fixing bolt insertion holes can be employed.

  The lid member 66 is disposed so as to cover the opening of the instrument member 64 and is fixed to the instrument member 64 with bolts or welding. As a result, the housing 62 as a whole has a long, substantially rectangular box shape, and a rectangular accommodating region 72 is provided inside. The elastic plate 12 having a pair of mass portions 14, 14 similar to those of the first embodiment is accommodated in the accommodating region 72, and the central protrusion 22 is fitted into the concave groove 24 of the bottom wall portion 68. ing.

  In the form in which the elastic plate 12 extends in parallel with the bottom wall portion 68 and the lid member 66 while the central protrusion 22 is in contact with the bottom wall portion 68, each of the thickness direction one side of each mass portion 14 in the elastic plate 12 is sandwiched. The abutting rubber layer 20 is opposed to the bottom wall portion 68 with a predetermined distance, and the additional mass 18 and the lid member 66 on the other side in the thickness direction sandwiching the mass portions 14 of the elastic plate 12 are predetermined. Opposite positions are spaced apart. The separation distance between the contact rubber layer 20 and the bottom wall portion 68 and the separation distance between the additional mass 18 and the lid member 66 are substantially the same. In this form, one of the stationary states is taken. As is clear from this, the entire elastic plate 12 connecting the pair of mass portions 14, 14 can be jumped and displaced independently of the housing 62.

  Further, while the central protrusion 22 is in contact with the bottom wall portion 68, one (other) mass portion 14 is in contact with the bottom wall portion 68 via the contact rubber layer 20, and the other (one) mass portion 14 is in contact with the bottom wall portion 68. The lid member 66 is brought into contact with the additional mass 18. Thereby, two types of stationary states are taken.

  In the present embodiment, in order to obtain an effective damping effect against vibrations in the main vibration input direction of the body 16 (up and down in FIG. 9), a circumferential gap in the housing region 72 of the housing 62 and a height direction The clearance is made large enough to sufficiently separate the elastic plate 12, the mass portion 14, the additional mass 18 and the like from the peripheral wall portion 70 and the lid member 66. In short, it is desirable that the inner peripheral surface and the upper bottom surface of the housing 62 do not interfere with the elastic plate 12, the mass portion 14 and the like when the elastic plate 12 jumps, elastically deforms, resonates, or the like. However, it is desirable that the elastic plate 12 be stably positioned on the body 16 with respect to a predetermined position. Therefore, the peripheral wall portion 70, the lid member 66, and the like of the housing 62 are set to have a size that can function to suppress the movement displacement of the elastic plate 12 within a predetermined range while avoiding interference with the elastic plate 12 as much as possible. It becomes.

  Incidentally, the size of the gap between the housing member 62 and the lid member 66 in the height direction of the accommodating region 72, that is, in the thickness direction (vertical direction) of the elastic plate 12 and the additional mass 18 is set to be comparatively small. However, it can be adopted as a tuning method. That is, in consideration of bending deformation of the elastic plate 12 and jumping displacement, the housing 62 is formed with such a small gap size that the elastic plate 12 and the additional mass 18 come into contact with each other. As a result, the elastic plate 12 is bent and deformed or jumped and displaced, so that not only the bottom wall portion 68 (lower bottom surface) of the housing 62 but also the lid member 66 (upper bottom surface) of the housing 62 is positively affected. You can make it hit. In short, when the elastic plate 12 is deformed or displaced, the elastic plate 12 strikes at the contact mass portions at both ends of the stroke so that the vibration damping effect due to hitting can be applied to the automobile body 16 via the housing 14. On the other hand, it is possible to act more efficiently.

  In the present embodiment, since the vibration damping device 60 is mounted on the surface of the automobile body 16 that extends in the horizontal direction (left and right in FIG. 9), the central protrusion of the elastic plate 12 without vibration input. A specific example in which 22 is fitted in the concave groove 24 and is superimposed on the automobile body 16 through the bottom wall portion 68 of the housing 62 is shown. For example, a surface inclined with respect to the vertical direction of the automobile body 16 is shown. It is also possible to attach to a vertical surface. In such a case, the central protrusion 22 of the elastic plate 12 is separated from the concave groove 24 and is disposed in contact with only the inner surface of the peripheral wall 70 of the housing 62, or the housing 62 You may arrange | position in the state contact | abutted to both the lower bottom face and the surrounding wall inner surface. In any case, it is only necessary that the contact mass portion of the elastic plate 12 strikes the lid member 66 and the bottom wall portion 68 at the time of vibration input.

  In the vibration damping device 60 having the above-described structure, when a large vibration is input to the housing 62 through the automobile body 16 in the main vibration input direction, the elastic plate 12 jumps and is displaced greatly. Thus, the mass portion 14 strikes the lid member 66 via the additional mass 18 or strikes the bottom wall portion 68 via the contact rubber layer 20. Based on this hit, a vibration damping effect on the vibration of the body 16 can be exhibited.

  Accordingly, an unstable stationary state can be realized based on the fact that all of the mass portion 14 and the central protrusion 22 of the elastic plate 12 do not simultaneously contact the bottom wall portion 68 of the housing 62 in the stationary state. Thereby, even when a small amplitude vibration is input, it is possible to easily break the balance of the elastic plate 12 in the accommodation region 72 and effectively hit the mass portion 14 against the bottom wall portion 68 or the lid member 66 of the housing 62. Thus, an excellent damping effect can be obtained.

  In particular, in the present embodiment, the elastic plate 12 including the mass portion 14 is accommodated and disposed in the housing 62, so that it can be stably positioned at the target vibration suppression target portion of the automobile body 16.

  Although the embodiments of the present invention have been described in detail above, these are merely examples, and the present invention is not limited to specific descriptions in these embodiments, and is based on the knowledge of those skilled in the art. The present invention can be implemented with various changes, modifications, improvements, and the like. Further, it goes without saying that such embodiments are all included in the scope of the present invention without departing from the gist of the present invention.

  For example, the shape, size, structure, number, configuration of the elastic plate 12, the mass portion 14, the contact rubber layer 20, the central protrusion 22, the housing 62, etc., and the arrangement with respect to the body 16 are limited to those illustrated. It is not something.

  That is, in the embodiment, the pair of mass portions 14 and 14 may be integrally formed with the elastic plate 12 and a single plate, but as shown in FIG. The metal mass 74 made of a hard metal material may be formed separately from the elastic plate 12 and may be fixed to both ends in the longitudinal direction of the elastic plate 12.

  In the fourth embodiment, the leaf springs extending radially about the contact rubber mass 46 are formed by overlapping two elastic plates 12 having a rectangular flat plate shape in the thickness direction so as to cross each other. Although configured, for example, such a radially extending leaf spring can be formed of a single plate. It is also possible to overlap three or more elastic plates extending in different directions in the thickness direction so as to intersect each other.

  Further, in the fourth embodiment, the contact rubber mass 46 is provided at the center of the radially extending leaf spring. However, the contact rubber mass 46 is not an essential member, for example, at each distal end portion of the radial leaf spring. Only the abutting rubber layer provided may take two or more types of stationary states that are in a contact state and a separated state in different combinations.

  In the fifth embodiment, the central protrusion 22 made of a rubber elastic body fixed to the elastic plate 12 is placed in the concave groove 24 of the bottom wall portion 68 of the housing 62 in order to position the elastic plate 12 with respect to the housing 62. Has been realized. However, the present invention is not limited to this. For example, as shown in FIG. 10, a saddle-shaped center protrusion 76 is formed at the center of the lid member 66 and the elastic plate 12 is pressed at the center. A central recess 78 is formed, and the central recess 78 and the central protrusion 76 are separated in a state where the elastic plate 12 is placed on the bottom wall portion 68 of the housing 62, and vibration is input to be elastic. When the plate 12 jumps or bends from the bottom wall portion 68, the central protrusion 76 is fitted into the central recess 78 so that the elastic plate 12 can be positioned with respect to the housing 62. In this specific example, the protrusion formed on the opposite side of the central recess 78 at the center of the elastic plate 12 is placed on the bottom wall portion 68 of the housing 62, so that the contact mass portions on both sides are provided. Is separated from the bottom wall portion 68, but since the protrusion is incidentally formed along with the press forming of the central recess 78, it functions as a contact mass portion according to the present invention. Not done.

In the specific example shown in FIG. 10, the central recess 78 and the central protrusion 76 may be in contact with the elastic plate 12 placed on the bottom wall portion 68 of the housing 62. Thus, consists the connection support portion comprises a contact point (surface) of the central recess 78 and the center projection 76, by such joint supports, the elastic plate 12 is brought into supporting lifting with respect to the housing 62 and Become. As a result, the entire elastic plate 12 is restricted from jumping and moving independently with respect to the housing 62, and one mass portion 14 is centered on the contact surface of the central protrusion 76 and the central recess 78. And the other mass portion 14 can be brought into contact with the lid member 66 and the bottom wall portion 68 of the housing 62 alternately. Note that FIG. 11 shows a reference example and not an embodiment of the present invention.

That is, in the reference example shown in FIG. 11, a rotation pin 80 as a connection support portion extending in the width direction of the elastic plate 12 is provided at the center of the elastic plate 12, and the rotation pin 80 is fixed to the housing 62. Is supported. Thus, the center of which is supported by the rotation pin 80 spring plate 12 is prevented from being displaced jumping independently of the housing 62, around the rotation pin 80, one of the mass portion 14 and the other The mass portions 14 can be brought into contact with the lid member 66 and the bottom wall portion 68 of the housing 62 alternately.

  Moreover, in the said embodiment, although the support part was comprised by the center protrusion 22 which consists of a rubber elastic body formed separately from the elastic plate 12, as FIG. 12 also shows, press work etc. Thus, the central protrusion 82 can be formed integrally with the elastic plate 12 by projecting the central portion of the elastic plate 12 in one of the thickness directions.

  Further, the positioning means by the central recess 78 of the elastic plate 12 and the central protrusion 76 provided in the housing 62 is not limited to the specific example of FIG. 10, for example, as shown in FIG. By projecting a central projection 76 formed of a rubber elastic body on the bottom wall portion 68 of the housing 62 and fitting the distal end portion of the central projection 76 into a central recess 78 that opens downward in the vertical direction, You may comprise a support part including these center recesses 78 and the center protrusion 76. FIG.

  Further, the contact rubber layer 20 is not provided on the mass portion 14 of the elastic plate 12 as in the above embodiment, but is provided on the housing 62 or when the housing 62 is not provided as shown in FIG. It is also possible to provide the body 16 directly.

  Moreover, in the said embodiment, although the support part was provided in the center of the elastic plate 12, according to the damping effect requested | required, a support part is provided in the position eccentric from the center of the elastic plate 12, and an elastic plate is provided. The one mass portion 14 in the longitudinal direction of the twelve may be positively brought into contact with the vibration suppression target member as compared with the other mass portion 14.

  Incidentally, in order to verify the vibration damping effect according to the vibration damping device 10 of the present embodiment, the following embodiment will be described, but the present invention is not limited to the embodiment.

  First, an experimental apparatus (not shown) is prepared. The experimental apparatus includes a base as a vibration input member. The base has a rectangular flat plate shape and is formed using a rigid material such as iron. Fix both ends of the base to the shaker. A sinusoidal excitation by a vibrator is applied in the thickness direction of the base, and the primary natural frequency of the base is measured by a known laser vibrometer.

  In addition, a vibration damping device 10 tuned to the primary natural frequency of the base is disposed so as to overlap the base. The vibration level obtained by applying a predetermined excitation force to the base with a vibration exciter with the vibration damping device 10 superimposed on the base was measured using a known laser vibrometer.

  In this example, four different vibration levels were measured by varying the excitation force of the base. The results are shown as Example 1, Example 2, Example 3 and Example 4 in order from the smallest excitation force, and each example is shown in different drawings (FIGS. 15 to 18). Further, in each example, the result of measuring the vibration level of the base in a state where the damping device 10 is not disposed on the base is given a number corresponding to each example as a comparative example, and each comparative example Are respectively shown in the drawings in which corresponding examples are shown.

  From the results shown in FIGS. 15 to 18, in any of the vibration damping devices 10 according to the first to fourth embodiments, the vibration level of the natural frequency in question is reduced, and an excellent vibration damping effect is exhibited. It is recognized that

  Therefore, in the vibration damping device 10 having the structure according to the present invention, there are a plurality of types of stationary states in which the pair of mass portions 14 and 14 and the central protrusion 22 are brought into a contact state and a separated state in different combinations. Based on the occurrence, various hitting modes are realized, and it is considered that the desired damping effect can be stably obtained from the small vibration to the large vibration as illustrated.

BRIEF DESCRIPTION OF THE DRAWINGS FIG. The front view which shows the operation | movement of the damping device as a model. The front view which shows the operation | movement different from FIG. 2 in the vibration damping device in model. The front view which shows the state which mounted | wore the motor vehicle body with the damping device as 2nd embodiment of this invention. The longitudinal cross-sectional view which shows the state which mounted | wore the motor vehicle body with the damping device as 3rd embodiment of this invention. VI-VI arrow line view of FIG. It is a longitudinal cross-sectional view which shows the state which mounted | wore the motor vehicle body with the damping device as 4th embodiment of this invention, Comprising: The figure corresponded in the VII-VII cross section of FIG. The bottom view of the damping device in FIG. The longitudinal cross-sectional view which shows the state which mounted | wore the motor vehicle body with the damping device as 5th embodiment of this invention. The longitudinal cross-sectional view which shows the state which mounted | wore the motor vehicle body with the damping device as another specific example of this invention. The longitudinal cross-sectional view which shows the state which mounted | wore the motor vehicle body with the damping device as a reference example of this invention. The longitudinal cross-sectional view which shows the principal part of the state which mounted | wore the motor vehicle body with the damping device as another specific example of this invention. The longitudinal cross-sectional view which shows the principal part of the state which mounted | wore the motor vehicle body with the damping device as another specific example of this invention. The longitudinal cross-sectional view which shows the principal part of the state which mounted | wore the motor vehicle body with the damping device as another specific example of this invention. The graph which shows the result measured about the damping effect of the damping device in FIG. The graph which shows the result measured on the conditions different from FIG. 15 about the damping effect of the damping device. The graph which shows the result measured on the conditions different from FIG.15, 16 about the damping effect of the damping device. The graph which shows the result of having measured about the damping effect of the damping device on the conditions different from FIG.

Explanation of symbols

10: vibration damping device, 12: elastic plate, 14: mass part, 16: automobile body, 20: contact rubber layer, 22: central protrusion

Claims (13)

A plurality of abutting mass portions that abut against the vibration input member are spaced apart from each other, and the plurality of abutting mass portions are connected by a spring member , and can be jumped and displaced as a whole independently of the vibration input member. In addition , all of the plurality of corresponding contact mass portions are not in contact with the vibration input member at the same time in a stationary state, and at least one corresponding contact mass portion is separated from the vibration input member. A vibration damping device characterized in that it is in a stationary state, and two or more types of stationary states are created in which the abutting mass portions are in a contact state and a separated state in different combinations. Wherein the plurality of contact mass unit, respectively, wherein the abutting state with respect to the vibration input member at least one stationary state of the two or more Rutotomoni, at least one stationary state of the two or more vibration damping device according to claim 1 which is separated state in pairs to said vibration input member.   The vibration damping device according to claim 1, wherein a leaf spring is employed as the spring member.   The vibration damping device according to claim 3, wherein the contact mass portion is integrally formed with the leaf spring.   4. The vibration damping device according to claim 1, wherein the contact mass portion is formed separately from the spring member and is fixed to the spring member. 5.   The vibration damping device according to any one of claims 1 to 5, wherein a contact surface of the contact mass portion and the vibration input member is formed of a rubber elastic body.   The vibration damping device according to any one of claims 1 to 6, wherein a plurality of the contact mass portions are respectively arranged on a plurality of straight lines intersecting with each other.   The support portion that is positioned at the center of gravity of the plurality of contact mass portions as a whole and is in contact with the vibration input member in any stationary state is formed. A vibration damping device according to claim 1. The vibration damping device according to claim 8 , wherein the support portion is formed as one of the contact mass portions. The vibration damping device according to claim 8 or 9 , wherein positioning means for engaging the support portion to limit a free displacement is formed in the vibration input member. Said spring member, said support portion being constituted by a plate spring extending radially around the any one of claims 8 to 10 wherein the contact mass portions respectively to the tip portions thereof leaf spring is provided The vibration control device described in 1. Said spring member, said across the support portion is constituted by a single leaf spring which extends linearly on either side, according to claim 11, wherein the contact mass portions at both ends portion of the plate spring is provided Vibration damping device. By providing a rigid housing having a hollow structure that is fixed to the vibration member to be damped, and connecting the plurality of contact mass portions, the spring member is accommodated in the housing, so that the housing The vibration damping device according to any one of claims 1 to 12 , wherein the entire spring member that constitutes a vibration input member and that connects the contact mass portion to the housing is capable of jumping and displacing independently. .

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