JP2009030769A - Vibration absorbing connection rod - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To provide a vibration absorbing connection rod having novel construction for reducing the transmission of vibration due to the displacement of a rod body and for allowing the setting of the dynamic spring constant of a vibration absorbing bush and the mass of the rod body at high degrees of freedom. <P>SOLUTION: The vibration absorbing connection rod 10 comprises a vibration damping device 44 consisting of a hollow-structure housing 46 located on the half periphery parts of supporting cylinder portions 14, 16 at the opposite side to the rod body 12, and an independent mass member 50 stored and arranged in a mass storage void 48 formed in the hollow part of the housing 46 in a non-adhesive and independently displaceable manner. With vibration input in the axially perpendicular direction of the rod body 12, the independent mass member 50 is independently displaced relative to the housing 46 to elastically abut thereon. <P>COPYRIGHT: (C)2009,JPO&INPIT

Description

  The present invention relates to an anti-vibration connecting rod that is preferably used as, for example, an automobile torque rod or suspension rod, and more particularly to a vibration damping that can reduce transmission vibration by contacting an independent mass member with a housing. The present invention relates to an anti-vibration connecting rod provided with the device.

  Conventionally, for example, various vibration control devices have been studied in order to suppress vibration of a vibration suppression target member such as a vehicle body. As one type, a hollow structure housing fixed to the vibration suppression target member has been studied. By disposing an independent mass member that is non-adherent and capable of independent displacement, and making the independent mass member abut against the housing elastically, sliding friction at the time of abutment and energy loss due to collision are utilized. Therefore, there has been proposed a vibration damping device having a structure capable of obtaining a vibration damping effect. An example of such a vibration damping device is Patent Document 1 (Japanese Patent Laid-Open No. 2001-271874).

  In the vibration damping device having the structure shown in Patent Document 1 and the like, since a damping effect can be obtained with respect to vibration over a wide frequency range with a small mass, for example, a power unit of an automobile is mounted on a vehicle body. It is used for vibration control of anti-vibration connecting rods such as torque rods connected to the vehicle and suspension rods connecting wheels to the vehicle body. The anti-vibration connecting rod is provided with a support cylinder part (arm eye) at both longitudinal ends of the rod body formed of a highly rigid material with a long shape, and with an anti-vibration bush attached to the support cylinder part. The anti-vibration bushing is attached to each one of the connection target members to connect the connection target members to each other. For example, as shown in Patent Document 2 (Japanese Patent Laid-Open No. 2005-106293), etc. Yes.

  By the way, in a conventional vibration-proof connecting rod, when a vibration damping device is attached, acceleration noise and road noise transmitted from the power unit or wheel side to the vehicle body deteriorate due to resonance caused by elastic deformation of the rod body. The purpose is to prevent it. Therefore, as shown in Patent Document 1, the vibration damping device is disposed at the central portion in the longitudinal direction of the rod body where the displacement due to the deformation of the rod body is maximum, and the independent mass member with respect to the housing By causing the independent displacement, a vibration damping effect due to the contact between the mass member and the housing is exhibited.

  However, the anti-vibration connecting rod provided with the vibration damping device shown in Patent Document 1 and the like is intended to suppress resonance due to deformation of the rod body as described above. There has been a problem that it is difficult to exert an effective damping effect on vibrations transmitted from one of the members to be connected to the other. That is, since the rod body, which is a rigid body, is elastically attached to the connection target member by the anti-vibration bush, vibration in the direction perpendicular to the axis is input from the connection target member (for example, a power unit of an automobile) to the rod body. Then, the vibration is transmitted to the other connection target member (for example, vehicle body) through the rod body.

  If the rod body is vibrated as a rigid body, the vibration damping device is attached to the central portion in the longitudinal direction, so that the displacement of the vibration damping device becomes insufficient and an effective vibration damping effect is exhibited. It is hard to be done. In particular, in a vibration-proof connecting rod in which a rigid rod body is attached to a member to be connected via a rubber elastic body of a vibration-proof bushing, a mass having the rod body as a mass component and the vibration-proof bushing as a spring component is used. -Rigid body resonance in the spring system is likely to be a problem, and amplification of transmission vibration due to the rigid body resonance of the rod body may be a further problem.

  In order to prevent the transmission vibration from deteriorating due to the rigid resonance of the rod body, for example, by changing the dynamic spring constant of the anti-vibration bushing or the mass of the rod body, the frequency of the rigid resonance of the rod body may be The problem is solved by changing to a low frequency range where it is difficult to cause a problem. However, if the dynamic spring constant of the anti-vibration bushing, the mass of the rod body, etc. are changed, the characteristics of the anti-vibration connecting rod will change, making it difficult to prevent transmission of idling vibrations of automobiles, for example. There is a possibility that problems such as a decrease in strength of the steel may occur. Therefore, it is difficult to say that it is an effective means for solving the deterioration of vibration due to the rigid resonance of the rod body, and a more effective solution means has been demanded.

JP 2001-271874 A JP 2005-106293 A

  Here, the present invention has been made in the background as described above, and the problem to be solved is to reduce the transmission of vibration due to the displacement of the rod body and to reduce the dynamic spring constant of the vibration isolating bush. Another object of the present invention is to provide a vibration-isolating connecting rod having a novel structure capable of setting the mass of the rod body and the like with a high degree of freedom.

  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, according to the present invention, the support cylinder portions are formed at both ends of the rod body, and the vibration isolation bushes are assembled to the support cylinder portions, respectively, and the vibration isolation bushes are connected to each one of the connection target members. The anti-vibration connecting rod, which is connected to each other and connects the members to be connected to form a vibration transmission system, is located in a half-circumferential portion on the opposite side to the rod body side in the support cylinder portion, and has a hollow structure In addition, an independent mass member is accommodated in a mass accommodation space formed in the hollow portion of the housing so as to be independently displaceable without adhesion, and is input in a direction perpendicular to the axis of the rod body. A vibration damping device is configured in which the independent mass member is independently displaced with respect to the housing by elastic vibration and elastically abuts on the housing.

  In the anti-vibration connecting rod having the structure according to the present invention as described above, a vibration damping device is provided in a half-circumferential portion on the opposite side of the rod main body on the circumference of the support cylinder portion, thereby accompanying vibration displacement of the rod main body. Thus, a large acceleration can be applied to the vibration damping device, and a relative jumping displacement of the independent mass member relative to the housing can be advantageously realized. Thereby, this invention can reduce advantageously the vibration transmission between the connection object members by the rod main body elastically supported by the anti-vibration bushing at both ends being displaced as a rigid material.

  In other words, in the vibration damping device using the energy loss due to the contact between the independent mass member and the housing, the independent mass member can be stably struck against the housing in order to effectively achieve the desired vibration damping effect. Is required.

  Accordingly, the present invention provides a rod end that is elastically supported by a displacement of the rod body when the rod body has sufficient rigidity and hardly undergoes elastic bending deformation due to the action of external force. By providing a housing for the vibration damping device at a specific location, which is a half-circumferential portion located outside the rod axial direction, on the circumference of the support cylinder provided at the rod end. The acceleration exerted on the vibration control device can be greatly obtained.

  As a result, when a vibration damping device is provided in the substantially central portion of the rod body, an effective vibration damping effect was not exhibited, and it is effective even for vibration transmitted by displacement of the rod body as a rigid body. A vibration control effect can be obtained. In particular, by preventing the rigid resonance of the rod body, it is possible to advantageously avoid the transmission vibration being amplified by the rigid resonance of the rod body. Therefore, for example, noise during acceleration of the automobile can be reduced or eliminated.

  Further, by adopting the vibration-isolating connecting rod according to the present invention, the deterioration of the transmission vibration due to the rigid resonance of the rod body is reduced or avoided without changing the mass of the rod body or the dynamic spring constant of the vibration-isolating bush. I can do it. Therefore, by changing the mass of the rod body and the dynamic spring constant of the vibration-isolating bushing, avoid problems such as deterioration of vibration transmission in a specific frequency range and deterioration of the strength and durability of the vibration-isolating connecting rod. I can do it.

  In addition, the axial direction of the vibration-isolating connecting rod refers to a direction in which a virtual straight line passing through the axial direction and the radial center of each support tube portion formed at both ends of the rod body extends. Further, the anti-vibration bush is not particularly limited in its specific structure, but is attached to the support cylinder part by being arranged separately on the outer peripheral side of the inner cylinder member attached to the connection target member and the inner cylinder member. The outer cylinder members have a structure in which they are connected to each other by a main rubber elastic body.

  In the vibration-isolating connecting rod according to the present invention, the housing may be provided on the circumference of the support cylinder portion so as to be positioned on the opposite side of the rod body on the central axis of the rod body.

  In this way, by providing the vibration damping device at the axial end of the vibration proof connecting rod, when the vibration is input to the rod body, a larger acceleration is applied to the vibration damping device, and the independent mass member housing It is possible to stably realize the contact by the independent displacement with respect to. As a result, it is possible to advantageously obtain a vibration damping effect using the sliding friction and the energy loss caused by the collision when the independent mass member and the housing are brought into contact with each other.

  Further, in the vibration-isolating connecting rod according to the present invention, the housing may be provided so as to be positioned in a direction orthogonal to the axial direction of the rod body on the circumference of the support cylinder portion.

  Thus, even when the vibration damping device is provided so as to be positioned in a direction orthogonal to the axial direction of the rod body on the periphery of the support cylinder portion, sufficient acceleration is exerted on the vibration damping device. Thus, the desired vibration control effect can be obtained effectively.

  Further, in the vibration proof connecting rod having the structure according to the present invention, the housing has a hollow structure having a cylindrical inner peripheral surface, and the independent mass member has a cylindrical shape corresponding to the inner peripheral surface of the housing. It is desirable that the outer peripheral surface be provided so that the inner peripheral surface of the housing and the outer peripheral surface of the independent mass member are brought into contact with each other by vibration input in a direction perpendicular to the axis of the rod body.

  In the vibration proof connecting rod having such a structure, the contact surfaces of the independent mass member and the housing are both curved surfaces having a substantially cylindrical shape. As a result, a stable contact state between the independent mass member and the housing is exhibited with respect to input vibration in any direction that is perpendicular to the axis of the independent mass member, and an excellent damping effect is exhibited. Further, in addition to the vibration suppression effect based on the energy loss due to the slip or the collision, it is possible to expect the vibration suppression effect based on the energy loss due to the rolling friction of the independent mass member. Furthermore, since the independent mass member is allowed to rotate in the circumferential direction in the housing, durability can be expected to be improved by changing the hitting portion in the circumferential direction.

  Further, in the anti-vibration connecting rod according to the present invention, the dynamic spring constants of the anti-vibration bushes provided at both ends of the rod body are different from each other, and the anti-vibration bush having a smaller dynamic spring constant is provided. It is desirable that the housing is provided on the circumference of the support cylinder portion to be attached.

  According to this, it is advantageous to displace the vibration damping device by attaching the vibration damping device to the end side to which the vibration isolating bushing having a small dynamic spring constant, which is the side that is displaced more greatly at the time of vibration input. The acceleration applied can be increased. Therefore, it is possible to effectively obtain the vibration damping effect due to the contact between the independent mass member and the housing.

  In the present invention, preferably, a bottomed cylindrical base portion is integrally formed with the support cylinder portion, and the opening of the base portion is covered with a lid member, whereby the mass storage space is formed. The housing having the structure is configured.

  Thus, by integrally forming the base portion constituting the housing with the support cylinder portion, the vibration damping device can be easily attached to the support cylinder portion without providing any special fixing means. Further, the mounting work of the vibration damping device to the support cylinder portion can be omitted, and the vibration-isolating connecting rod according to the present invention can be realized with a small number of steps.

  Hereinafter, in order to clarify the present invention more specifically, embodiments of the present invention will be described in detail with reference to the drawings.

  First, FIG. 1 and FIG. 2 show an automotive torque rod 10 as a first embodiment of a vibration-isolating connecting rod according to the present invention. The torque rod 10 has a first rubber bush 18 as a vibration-proof bush and a second arm eye 16 as a support cylinder portion formed at both ends of the rod body 12 as opposed to a first arm eye 14 and a second arm eye 16. The rubber bush 20 is mounted. For example, the first rubber bush 18 attached to the first arm eye 14 is attached to the vehicle body side (not shown), and the second rubber bush 20 attached to the second arm eye 16 is not shown. By being attached to the power unit side, the vehicle body and the power unit are connected to each other via the rod body 12 so that a vibration transmission system is configured. In the following description, the front-rear direction refers to the left-right direction in FIG. 1, which is the vehicle front-rear direction when the torque rod 10 is mounted on the vehicle, unless otherwise specified. Furthermore, the left-right direction refers to the up-down direction in FIG. 2 that is the axial direction of the first arm eye 14 that is substantially left-right in the vehicle-mounted state, and the up-down direction is the substantially vertical up-down direction in the vehicle-mounted state. The vertical direction in FIG. 1 that is the axial direction of the second arm eye 16 is referred to.

  More specifically, as shown in FIGS. 3 and 4, the rod body 12 has a substantially plate shape as a whole. In the present embodiment, the rod body 12 has a substantially constant plate thickness in the left-right direction. And gradually becomes narrower in the vertical direction as it goes to the vehicle rear side (left in FIG. 3). In the present embodiment, the rod body 12 has a longitudinal shape extending linearly in the vehicle front-rear direction.

  The rod body 12 is formed of a metal material such as iron or aluminum alloy, a hard synthetic resin material reinforced with fiber, or the like. In the present embodiment, the rod body 12 is a high rigidity synthetic resin material reinforced with glass fiber. Is formed. Further, as shown in FIG. 3, a pair of reinforcing ribs 22, 22 extending toward both sides of the rod body 12 in the thickness direction are provided at both ends of the rod body 12 in the vertical direction. The rod body 12 is integrally formed so as to extend continuously, and the bending rigidity of the rod body 12 in the plate thickness direction is enhanced. Thereby, the rod main body 12 is a member that can be regarded as a substantially rigid body in which elastic deformation due to the action of an external force is not a problem.

  A first arm eye 14 is formed at one end of the rod body 12 in the longitudinal direction (in the present embodiment, the vehicle longitudinal direction). The first arm eye 14 has a small-diameter cylindrical shape extending in the vertical direction with a central axis orthogonal to the plate thickness direction of the rod main body 12, and is integrally formed with the rod main body 12 in this embodiment.

  As shown in FIGS. 1 and 2, the first arm eye 14 is provided with a first rubber bush 18. The first rubber bush 18 includes a first inner cylinder fitting 24 as an inner cylinder member. The first inner cylinder fitting 24 has a substantially cylindrical shape with a thick and small diameter that extends linearly with a substantially constant cross-sectional shape, and is formed of a highly rigid material such as iron or aluminum alloy.

  Further, the first main rubber elastic body 26 is vulcanized and bonded to the outer peripheral surface of the first inner cylinder fitting 24. The first main rubber elastic body 26 has a thick, substantially cylindrical shape, and is disposed on the same central axis as the first inner cylinder fitting 24. Further, in the present embodiment, flange-like locking portions 28, 28 that extend to the outer peripheral side are formed integrally with the first main rubber elastic body 26 at both axial ends of the first main rubber elastic body 26. . The inner circumferential surface of the first main rubber elastic body 26 having such a structure is vulcanized and bonded to the outer circumferential surface of the first inner cylinder fitting 24 so that the first inner cylinder fitting 24 is integrated with the first inner cylinder fitting 24. It is formed as an integrally vulcanized molded product prepared for

  Then, the integrally vulcanized molded product of the first main rubber elastic body 26 provided with the first inner cylinder fitting 24 is fitted into the first arm eye 14 and fixed. In the mounted state of the integrally vulcanized molded product, the first inner cylinder fitting 24 is disposed on the same central axis as the first arm eye 14 at a predetermined distance on the inner peripheral side of the first arm eye 14. ing. Further, in the present embodiment, the axial dimension of the first main rubber elastic body 26 is larger than the axial dimension of the first arm eye 14, and the first main rubber elastic body 26 has both ends in the axial direction. A pair of integrally formed locking portions 28, 28 are superimposed on the inner peripheral portion of the axial end surface of the first arm eye 14.

  Thus, by attaching the first vulcanized molded product of the first main rubber elastic body 26 to the first arm eye 14, the first inner cylinder fitting 24 and the first arm eye 14 are connected to the first main body 14. A first rubber bush 18 in the present embodiment connected to each other by a rubber elastic body 26 is configured. In the present embodiment, the support cylinder portion and the outer cylinder member are configured by the first arm eye 14.

  In the state where the integrally vulcanized molded product of the first main rubber elastic body 26 is attached to the first arm eye 14, the first main rubber elastic body 26 is connected to the first arm eye 14 and the first arm eye 14. Between the radially opposing surfaces of the inner cylindrical metal fitting 24, it is interposed in a state compressed and deformed in the radial direction. Thereby, the tensile stress which acts on the first main rubber elastic body 26 in the radial direction can be reduced, and the durability of the first main rubber elastic body 26 can be improved.

  Moreover, in this embodiment, although the 1st rubber bush 18 using the 1st arm eye 14 as an outer cylinder member is shown as a vibration proof bush, it formed separately from the 1st arm eye 14. The anti-vibration bush may be attached to the first arm eye 14 later. Specifically, for example, a first inner cylindrical metal fitting 24 having a small diameter cylindrical shape and an outer cylindrical metal fitting as an outer cylindrical member having a large diameter cylindrical shape are disposed on the same central axis, and the first inner metal fitting 24 is arranged. By interposing the first main rubber elastic body 26 between the radially opposite surfaces of the cylindrical metal fitting 24 and the outer cylindrical metal fitting, the first main rubber elastic body 26 is connected to the first inner cylindrical metal fitting 24 and the outer cylindrical metal fitting. The anti-vibration bushes connected to each other may be configured, and the anti-vibration bush may be attached to the first arm eye 14 by press-fitting and fixing the outer cylinder fitting to the first arm eye 14. Further, for example, even if the first main rubber elastic body 26 is vulcanized and bonded to both the first inner cylinder fitting 24 and the first arm eye 14, a vibration isolating bush is configured. good.

  On the other hand, a second arm eye 16 is formed at the other longitudinal end of the rod body 12. 3 and 4, the second arm eye 16 has a large-diameter cylindrical shape extending in the left-right direction with a central axis parallel to the plate thickness direction of the rod body 12. Is formed integrally with the first arm eye 14 on the opposite side. In other words, the second arm eye 16 is formed to extend in a direction orthogonal to the first arm eye 14 at the end opposite to one end of the rod body 12 where the first arm eye 14 is formed. ing. In the present embodiment, the second arm eye 16 has a cylindrical shape larger in diameter than the first arm eye 14.

  The pair of reinforcing ribs 22, 22 formed integrally with the rod body 12 is formed so that one end thereof reaches the outer peripheral surface of the first arm eye 14, and the other end is the first end. The second arm eye 16 is formed to have a length reaching the outer peripheral surface, and is formed integrally with the first and second arm eyes 14 and 16.

  Further, as shown in FIGS. 1 and 2, a second rubber bush 20 is attached to the second arm eye 16. The second rubber bush 20 as a whole has a cylindrical shape that is thicker and larger in diameter than the first rubber bush 18, and has a lower dynamic spring constant than the first rubber bush 18. The second rubber bush 20 has a structure in which a second inner metal fitting 30 as an inner cylinder member and a metal sleeve 32 as an outer cylinder member are connected to each other by a second main rubber elastic body 34. Yes.

  The second inner cylinder fitting 30 has a substantially cylindrical shape with a thick and small diameter that extends linearly with a substantially constant cross-sectional shape, and is made of a highly rigid material such as iron or aluminum alloy. In addition, the axial length of the second inner cylindrical metal fitting 30 is made larger than the axial length of the second arm eye 16. In the present embodiment, the central hole of the second inner cylinder fitting 30 has an oval shape, and the inner diameter is small in the vertical direction.

  The metal sleeve 32 has a thin, large-diameter, generally cylindrical shape having a substantially constant cross-sectional shape, and is formed of the same metal material as that of the second inner cylinder fitting 30. The axial length of the metal sleeve 32 is substantially equal to the axial length of the second arm eye 16, and is shorter than the axial length of the second inner cylinder fitting 30. Further, the outer diameter of the metal sleeve 32 is larger than the inner diameter of the second arm eye 16.

  The second inner cylinder fitting 30 and the metal sleeve 32 are disposed so that the outer circumference side of the second inner cylinder fitting 30 is surrounded by the metal sleeve 32, and the second inner cylinder fitting 30 and the metal sleeve 32 are arranged. Are spaced apart in the radial direction over the entire circumference. In particular, in the present embodiment, the center axis of the second inner cylindrical metal fitting 30 is shifted from the center axis of the metal sleeve 32 to the right side in FIG.

  A second main rubber elastic body 34 is vulcanized and bonded between the second inner cylinder 30 and the metal sleeve 32. The second main rubber elastic body 34 is a rubber elastic body having a thick, generally cylindrical shape as a whole, and its inner peripheral surface is vulcanized and bonded to the outer peripheral surface of the second inner cylindrical metal fitting 30. The outer peripheral surface is vulcanized and bonded to the inner peripheral surface of the metal sleeve 32. A second rubber bushing 20 having a structure in which the second inner cylinder fitting 30 and the metal sleeve 32 are elastically connected by the second main rubber elastic body 34 is formed. In addition, the 2nd main body rubber elastic body 34 in this embodiment is formed as an integral vulcanization molded product which provided the 2nd inner cylinder metal fitting 30 and the metal sleeve 32 integrally.

  In addition, first and second slits 36 and 38 are formed in the second main rubber elastic body 34. The first slit 36 is formed so as to penetrate the second main rubber elastic body 34 in the axial direction on the vehicle front side (right side in FIG. 1) with the second inner cylinder fitting 30 interposed therebetween. It extends in the direction with a predetermined length. Further, the outer peripheral side inner wall surface of the first slit 36 has a wave shape, and the inner peripheral side inner wall surface and the outer peripheral side inner wall surface are brought into contact with each other in a buffering manner.

  Further, the second slit 38 pivots on the second main rubber elastic body 34 on the opposite side to the first slit 36 (left side in FIG. 1 which is the vehicle rear side) across the second inner cylinder fitting 30. It is formed to penetrate in the direction. In addition, the second slit 38 extends in the radial direction from the upper and lower slit portions 40 extending in a predetermined length in the substantially circumferential direction toward the rear (left in FIG. 1) in the radial direction. The front and rear slit portions 42 are integrally provided, and as a whole, have a substantially T shape in a side view. As is clear from FIGS. 1 and 2, the portion located between the upper and lower slit portions 40 and the front and rear slit portions 42 in the second main rubber elastic body 34 is axially compared to the other portions. It extends to both sides and protrudes outward in the axial direction from the metal sleeve 32.

  By forming these slits 36 and 38, the dynamic spring constant in the direction perpendicular to the axis of the second rubber bush 20 is further softened. In the present embodiment, the radial distance between the second inner cylinder fitting 30 and the metal sleeve 32 in the second rubber bush 20 is the same as the first inner cylinder fitting 24 in the first rubber bush 18 and the first distance. The second main rubber elastic body 34 is thicker than the first main rubber elastic body 26 in the radial direction, and is larger than the separation distance in the radial direction of one arm eye 14.

  Further, in the present embodiment, after the vulcanization molding of the second main rubber elastic body 34, the metal sleeve 32 is subjected to a diameter reduction process such as an eight-way drawing so that the compressive force in the radial direction is increased by the second main body. It is applied to the rubber elastic body 34. Thereby, the tensile stress in the radial direction exerted on the second main rubber elastic body 34 is reduced, and the durability of the second main rubber elastic body 34 is improved.

  The second rubber bush 20 is fitted and fixed to the second arm eye 16 by press-fitting and fixing the metal sleeve 32 to the second arm eye 16. Thereby, the second inner cylinder fitting 30 and the second arm eye 16 are elastically connected to each other by the second main rubber elastic body 34 via the metal sleeve 32.

  As described above, the automotive torque rod 10 according to the present embodiment having a structure in which the rubber bushes 18 and 20 are attached to the arm eyes 14 and 16 formed at both ends of the rod body 12 is configured.

  The torque rod 10 for an automobile has the first inner cylinder fitting 24 of the first rubber bush 18 fixed to a vehicle body (not shown) so that one end in the longitudinal direction of the rod body 12 is the first. The rod body 12 is attached to the vehicle body via the rubber elastic body 26, and the second inner cylinder fitting 30 of the second rubber bush 20 is fixed to a power unit (not shown), so that the other end of the rod body 12 in the longitudinal direction. Is attached to the power unit via the second main rubber elastic body 34. As a result, the vehicle body and the power unit are connected to each other by the torque rod 10.

  In addition, the inner cylindrical fittings 24 and 30 of the first and second rubber bushes 18 and 20 are respectively elastic against the first and second arm eyes 14 and 16 formed at both ends of the rod body 12. The arm eyes 14 and 16 are provided by being elastically connected via the bodies 26 and 34 and by attaching the first and second inner cylindrical fittings 24 and 30 to one of the members to be connected. The rod body 12 is attached to the connection target member in a state where both end portions are elastically supported. In the present embodiment, the dynamic spring constants of the first and second rubber bushes 18 and 20 are made different so that the support springs of the rod body 12 are made different at both ends.

  Here, the torque rod 10 having the structure according to the present embodiment is provided with a vibration damping device 44 as shown in FIGS. The vibration damping device 44 includes a hollow housing 46 and an independent mass member 50 accommodated in a mass accommodating space 48 formed in the housing 46.

  The housing 46 is a highly rigid member that is not easily deformed by an external force, and further includes a housing main body 52 as a base portion and a lid plate member 54 as a lid member. The housing main body 52 has a substantially block shape, and is formed of a high-stiffness material such as a hard synthetic resin material reinforced with fiber or a metal material such as iron or aluminum alloy. In this embodiment, the housing main body 52 is integrally formed with the rod main body 12 and the arm eyes 14 and 16, and is formed of a high-strength synthetic resin material reinforced with fibers similar to them.

  In addition, the housing body 52 is formed with a shallow circular fitting recess 56 that opens on one side of the vehicle in the left-right direction (upper side in FIG. 2), and the bottom wall center of the fitting recess 56. A receiving recess 58 is formed in the opening. The housing recess 58 is a circular recess having a smaller diameter than the fitting recess 56 and has a sufficient depth as compared with the fitting recess 56. By forming the fitting recess 56 and the housing recess 58, the housing body 52 has a substantially bottomed cylindrical shape, and its inner peripheral surface has a stepped cylindrical shape with a large diameter on the opening side. Has been.

  The lid plate member 54 is a thin disk-shaped member having an outer diameter substantially equal to the inner diameter of the fitting recess 56, and is formed of a hard synthetic resin material in the present embodiment. The lid plate member 54 may be formed of a metal plate made of iron, aluminum alloy, or the like, and may not necessarily be formed of the same material as the housing body.

  The housing 46 is constituted by the housing body 52 and the lid plate member 54 by the lid plate member 54 being fitted and fixed to the fitting recess 56. Further, the lid plate member 54 is fitted and fixed to the fitting recess 56, whereby the opening of the receiving recess 58 is closed by the lid plate member 54, and the mass receiving space 48 is formed inside the housing 46. Is to be formed. The mass storage space 48 in the present embodiment extends in the left-right direction with a substantially constant circular cross section.

  In addition, the specific structure of the housing 46 and the mass accommodation space 48 is not limitedly interpreted by what is shown in this embodiment. For example, the housing recess 52 is formed on both the left and right sides of the housing body 52, and the housing hole is formed in the bottom wall surface of the housing recess 52 so as to penetrate the housing body 52 in the left-right direction. The mass accommodation space 48 can also be formed by fitting the lid plate member 54 in the fitting recesses 56 and 56 respectively to close the opening portions on both sides of the accommodation hole.

  Further, an independent mass member 50 is disposed in the mass accommodation space 48. In the present embodiment, the independent mass member 50 is formed by partially covering the surface of the mass metal fitting 60 with the contact rubber layer 62. The mass metal fitting 60 has a substantially cylindrical shape, and is formed of a highly rigid metal material such as steel or aluminum alloy. Preferably, a material having a high specific gravity such as steel is employed in order to advantageously obtain a vibration damping effect due to a contact action described later.

  Further, a contact rubber layer 62 is formed on the surface of the mass fitting 60. The contact rubber layer 62 is a thin rubber elastic body, and in this embodiment, the contact rubber layer 62 is fixed so as to cover the side wall surface and the outer peripheral edge portions of both end surfaces in the axial direction. In other words, in the present embodiment, the abutting rubber layer 62 is not formed on the radial center portions of the both axial end surfaces of the mass fitting 60, and the mass fitting 60 is exposed to the outside. In the present embodiment, the contact rubber layer 62 is formed as an integrally vulcanized molded product including the mass metal fitting 60, and the independent mass member 50 in the present embodiment is realized by the integrally vulcanized molded product. .

  Such an independent mass member 50 is accommodated in the mass accommodating space 48. That is, after the independent mass member 50 is inserted into the housing recess 58 formed in the housing body 52, the lid plate member 54 is fitted and fixed to the fitting recess 56, and the independent mass member 50 is fixed. In the accommodated state, the opening of the accommodation recess 58 is closed, whereby the independent mass member 50 is disposed in the mass accommodation space 48 formed inside the housing 46.

  Further, in the present embodiment, in the state where the independent mass member 50 is accommodated in the mass accommodation space 48, the dimensions of the independent mass member 50 having a substantially cylindrical shape in the axial direction and the radial direction are substantially constant. The independent mass member 50 is made smaller in both the axial direction and the radial direction with respect to the inner wall surface of the mass accommodating space 48. It is arranged with a slight gap.

  Further, as is apparent from the above structure, the independent mass member 50 is disposed without being bonded to the housing 46 constituting the wall surface of the mass accommodating space 48, and the independent mass member 50 is attached to the housing 46. On the other hand, relative displacement is possible.

  The vibration damping device 44 having such a structure is formed integrally with the second arm eye 16 by the housing body 52 being integrally formed so as to protrude from the outer peripheral surface of the second arm eye 16 in the rod central axis direction. Are fixed.

  Here, the vibration damping device 44 is provided at a specific position on the circumference of the second arm eye 16. That is, the vibration damping device 44 is provided on the circumference of the second arm eye 16 so as to be positioned on the opposite side of the rod body 12 on the central axis of the torque rod 10. In other words, in the present embodiment, the vibration damping device 44 is provided so as to protrude toward the vehicle front side (right in FIG. 1) on the circumference of the second arm eye 16. In other words, the vibration damping device 44 includes the second rubber bushing 20 that has a smaller dynamic spring constant among both ends of the rod body 12 supported by the first and second rubber bushings 18 and 20. It is provided on the attached side.

  The central axis of the torque rod 10 is defined by a straight line that passes through both the radial and axial centers of the first arm eye 14 and the second arm eye 16. In the present embodiment, the center of the torque rod 10 in the vertical direction and the horizontal direction is extended, and is indicated by a one-dot chain line in FIGS. 1 and 2.

  When the torque rod 10 having such a vibration damping device 44 is mounted on the vehicle, for example, when the automobile is accelerated, the main vibration in the vertical direction that is perpendicular to the axis from the power unit side with respect to the torque rod 10. Is input, and the vibration is transmitted to the vehicle body side via the rod body 12.

  In the torque rod 10, the rod body 12 is a rigid body that does not undergo elastic bending deformation due to the action of an external force, and both end portions of the rod body 12 are first and second rubber bushes 18, 20, respectively. It is elastically supported by. Therefore, when vertical vibration is input to the rod body 12, both end portions of the elastically supported rod body 12 are displaced in the vertical direction, and the rod body 12 swings around the axially intermediate portion. Can be displaced dynamically.

Moreover, the rod main body 12 is displaced more in the axial direction both ends than the axial middle part by the displacement of such a swinging state. This can be easily understood from FIG. That is, d _(a) and d _(b) , which are displacement amounts at the end of the torque rod 10 on the second arm eye 16 side, are compared with d _(c) , which is a displacement amount at the intermediate portion of the rod body 12. It is clear that it is big. In FIG. 5, the outline of the torque rod 10 is indicated by a solid line, and the outline of the torque rod 10 in the maximum displacement state at the time of vibration input is indicated by a two-dot chain line.

  Furthermore, in this embodiment, the dynamic spring constants of the first rubber bush 18 and the second rubber bush 20 are different from each other. That is, in the present embodiment, the first rubber bush 18 has a sufficiently hard dynamic spring constant as compared with the second rubber bush 20. Thereby, the displacement amount of the rod main body 12 at the time of vibration input differs between the end part on the first rubber bushing 18 side and the end part on the second rubber bushing 20 side. The end portion is displaced more greatly than the end portion on the first rubber bush 18 side.

  In the present embodiment, the amount of displacement at both ends is made different by changing the amount of displacement at both ends, but the amount of displacement at both ends can be obtained more greatly. Even when the amounts are the same, the amount of displacement of the rod body 12 is maximized at both ends of the rod body 12.

  On the other hand, the vibration damping device 44 in which the housing 46 is fixed to the second arm eye 16 is displaced in the vertical direction according to the rocking displacement of the rod body 12 by the rod body 12 being displaced up and down. I'm damned.

  Here, in the present embodiment, the vibration damping device 44 is provided at the end of the torque rod 10 on the second rubber bush 20 side, more specifically, on the end of the vehicle arm on the circumference of the second arm eye 16. It has been. As a result, the vibration damping device 44 can obtain a large displacement in the vertical direction associated with the rocking displacement of the rod body 12.

  That is, since the spring characteristics of the first rubber bush 18 and the second rubber bush 20 are different from each other, when vibration is input in the main vibration input direction, the amount of displacement of both ends of the rod body 12 is changed. Are relatively different. In particular, in the present embodiment, as shown in FIG. 5, the amount of displacement in the vertical direction is maximized at the end (front end) of the rod body 12 on the second arm eye 16 side. .

  Therefore, in the torque rod 10, the vibration damping device 44 provided at the end on the second arm eye 16 side can be displaced relatively large in the vertical direction due to the displacement in the vertical direction of the rod body 12. Accordingly, a relatively large acceleration is applied to the vibration damping device 44.

  As a result, the independent mass member 50 that is accommodated in the housing 46 so as to be independently displaceable without being bonded is displaced relative to the housing 46 by the acting inertia force, and is thus displaced with respect to the inner wall surface of the housing 46. It is hit. At this time, since the surface of the independent mass member 50 is covered with the contact rubber layer 62, the mass metal fitting 60 and the housing 46 are brought into elastic contact with each other via the contact rubber layer 62. Yes.

  In addition, a great acceleration can be applied to the vibration damping device 44 by devising the position of the vibration damping device 44 with respect to the torque rod 10. Therefore, the jumping displacement of the independent mass member 50 with respect to the housing 46 is stably realized.

  The contact of the independent mass member 50 with the housing 46 causes energy loss due to sliding friction or collision, so that the vibration suppression effect for vibration transmitted through the rod body 12 is effectively exhibited. ing.

  In short, in the present embodiment, the vibration damping device 44 is provided at the end portion in the axial direction (longitudinal direction) where the displacement amount of the rod body 12 due to vibration input is maximized. 44 is subjected to a large acceleration. And since the acting acceleration is large, the independent displacement of the independent mass member 50 with respect to the housing 46 is effectively generated, and the effective damping effect based on the contact action is stably exhibited. It is like that.

  In the present embodiment, the vibration damping device 44 can be easily disposed at a specific location by integrally forming the housing main body 52 on the outer peripheral surface of the second arm eye 16.

  In addition, by integrally forming a part of the housing 46 with respect to the second arm eye 16, it is possible to stably realize the mounting state of the vibration damping device 44 on the second arm eye 16. Problems such as falling off the second arm eye 16 can be solved.

  Further, since the attachment work of the vibration damping device 44 to the second arm eye 16 is not required, the manufacturing becomes easy, and the housing body 52 is integrally formed to reduce the number of parts and the associated cost. Is also realized.

  Further, as shown in the present embodiment, even when the outer peripheral surface of the second arm eye 16 is a curved surface and the retrofitting of the vibration damping device 44 is relatively difficult, the vibration damping device 44 is moved to the second. The arm eye 16 can be easily provided at a predetermined position on the circumference.

  In the present embodiment, the independent mass member 50 has a columnar shape, and the housing 46 (the mass accommodating space 48) has a cylindrical inner wall surface. The independent mass member 50 is accommodated in the mass accommodating space 48 such that the side wall surface of the independent mass member 50 curved in an arc shape faces the cylindrical inner wall surface of the housing 46. Further, the input direction of the main vibration is a direction orthogonal to the central axis of the independent mass member 50, and when the independent mass member 50 is independently displaced with respect to the housing 46 by the vibration input, the independent mass member 50. The side wall surface of the housing 46 is brought into contact with the cylindrical inner wall surface of the housing 46. Thereby, in addition to the energy loss due to the sliding friction and the collision, the energy loss due to the rolling friction acts, so that the damping effect can be effectively exerted against vibrations in a wider frequency range.

  6 and 7 show actual measurement results obtained by measuring dynamic spring constants in the vertical direction of a mass-spring system in which the rod body 12 is a mass and the rubber bushes 18 and 20 are springs. That is, FIG. 6 shows the first inner cylinder fitting of the first rubber bush 18 when the second inner cylinder fitting 30 of the second rubber bush 20 in the torque rod 10 is vibrated at an acceleration of 1G. The result of measuring 24 dynamic spring constants is shown. Further, FIG. 7 shows the result of measuring the dynamic spring constant under the same conditions as the measurement according to FIG. 6 with the torque rod 10 designed and manufactured corresponding to the actual vehicle mounted on the vehicle. . In these measurements, a load of 3214N was applied in advance toward the rod body 12 side with respect to the second inner cylinder fitting 30. In the graphs shown in FIGS. 6 and 7, the measurement results when the torque rod 10 according to the present embodiment is employed are shown as a solid line as an example, and the vibration damping device 44 is not provided. The measurement result when the torque rod is employed is indicated by a broken line as a comparative example.

  From these measurements, when the torque rod 10 according to the present embodiment is employed, in either the non-mounted state or the mounted state of the vehicle, compared to the case where the torque rod not provided with the vibration damping device is employed. It was also confirmed that the low dynamic spring effect was exhibited and the reduction of transmission vibration could be advantageously realized. In addition, as shown in FIG. 7, it is clarified by actual measurement that the vibration damping effect is effectively exhibited over a wide frequency range even with respect to vibration input to the torque rod 10 from the vehicle side. It was.

  Furthermore, in the measurement result of the comparative example shown in FIG. 7, the dynamic spring constant is high from about 300 Hz to about 650 Hz, and a wider frequency range than the measurement result of the comparative example shown in FIG. 6. Thus, the deterioration of the vibration state has been confirmed. This is considered to be due to the fact that in the state of being mounted on the vehicle, in addition to the external force in the direction perpendicular to the axis, the external force in the twisting direction and the torsional direction acts on the second inner cylindrical fitting 30 in a composite manner. It is done. Therefore, in the torque rod 10 having the structure according to the present embodiment, as shown in the example of FIG. 7, an effective low dynamic spring effect can be obtained in a wide frequency range in the vehicle mounted state, It is possible to advantageously prevent deterioration of vibration.

  Further, in FIG. 6, the remarkably high dynamic spring is generated in the vicinity of 400 Hz, which is the frequency at which the rod main body 12 causes the rigid body resonance, and the dynamic spring constant is also increased in the vicinity of 550 Hz. The increase in the dynamic spring constant at around 550 Hz is due to the fact that a preload is applied to the second inner cylindrical member 34 during measurement, and the second inner cylindrical member 34 is displaced to the rod body 12 side. This is considered to be due to the fact that the second main rubber elastic bodies 34 on both sides of the upper and lower slits 40 are brought into contact with each other. Therefore, in the torque rod 10 having the structure according to the present embodiment, as shown in FIG. 6, not only the low dynamic spring effect at around 400 Hz, which is the main vibration suppression target frequency, but also the low dynamic at around 550 Hz. The spring effect is also exhibited effectively. In short, with the torque rod 10 having the structure according to the present embodiment, it is possible to expect an excellent vibration damping effect in a wide or many frequencies.

  Next, FIGS. 8 and 9 show an automotive torque rod 64 as a second embodiment of the vibration-isolating connecting rod according to the present invention. In addition, in the following description, about the member thru | or site | part substantially the same as said 1st embodiment, description is abbreviate | omitted by attaching | subjecting the same code | symbol.

  That is, in the torque rod 64 having the structure according to the present embodiment, as shown in FIG. 8, the central axis (first and second arm eyes 14) of the rod body 12 is arranged on the circumference of the second arm eye 16. , 16 is provided with a vibration damping device 44 so as to be positioned in a direction perpendicular to the virtual straight line connecting the centers of 16 and 16.

  More specifically, the housing main body 52 having the same structure as that of the first embodiment is positioned above the circumference of the second arm eye 16 under the mounting state of the torque rod 64 on the vehicle. In addition, the second arm eye 16 is integrally formed. Then, the independent mass member 50 is accommodated and disposed in the mass accommodating space 48 formed in the housing main body 52, and the opening of the mass accommodating space 48 is closed by the lid plate member 54, whereby the second A vibration damping device 44 is disposed so as to protrude upward on the circumference of the arm eye 16.

  In the present embodiment, as in the first embodiment, the second inner cylinder fitting 30 and the metal sleeve 32 in the second rubber bush 20 are arranged eccentrically and are shown in FIG. As shown, the vibration damping device 44 is disposed immediately above the central axis of the metal sleeve 32 disposed on the same central axis as that of the second arm eye 16 and the center of the second inner cylinder fitting 30. It is arrange | positioned in the position which shifted | deviated to the vehicle rear side rather than the axis | shaft.

  The same effect as that of the first embodiment can also be obtained in the automobile torque rod having the structure according to the second embodiment. In other words, in the present embodiment, the torque rod 64 elastically supported at both ends is provided with a striking vibration damping device 44 in the vicinity of the end on the second arm eye 16 side where the amount of displacement increases. By increasing the acceleration acting on the vibration device 44, the independent displacement of the independent mass member 50 with respect to the housing 46 can be generated stably. Therefore, based on the abutting action of the independent mass member 50 against the housing 46, the intended vibration damping effect can be exhibited effectively.

  As described above, according to the present invention, it is possible to effectively prevent the rod body 12 that is regarded as a rigid body elastically supported at both ends from deteriorating the transmission vibration due to the rigid body resonance. As described above, such an effect is realized by disposing a mass striking vibration damping device at the rod end where a large displacement occurs in consideration of the vibration mode of the rod body 12 which is a rigid body. That is, in order to suppress resonance due to elastic deformation of the rod body 12, the anti-vibration connecting rod having the conventional structure in which the vibration damping device is provided in the middle portion of the anti-vibration connecting rod is used for the rigid resonance of the rod body 12. In contrast, effective vibration control effects cannot be obtained.

In addition, in the anti-vibration connecting rod having the structure in which the vibration damping device is provided in the axial intermediate portion, the reason why the vibration suppression effect on the rigid body resonance of the rod main body 12 is not effectively exhibited is that in the axial intermediate portion, The main reason is that the amount of displacement is not sufficient and the independent displacement of the independent mass member 50 with respect to the housing 46 does not occur stably. This is because the displacement amount d _{(c) at the} intermediate portion in the axial direction of the rod body 12 shown in FIG. 5 is smaller than the displacement amounts d _(a) and d _(b) at the rod end portions. It is understood from that.

  This is also apparent from the simulation results shown in FIG. That is, FIG. 10 shows the result of calculating the noise in the passenger compartment during simulation of the automobile by simulation for each case where the vibration damping device is attached to A, B, and C in FIG.

  In this simulation, the case where the vibration damping device is mounted at the position A in FIG. 11 means the case where the torque rod 10 having the structure described in the first embodiment of the present invention is used as the vibration-proof connecting rod. Indicates. Further, the case where the vibration damping device is mounted at the position B in FIG. 11 indicates a case where the torque rod 64 having the structure described in the second embodiment of the present invention is adopted as the vibration-proof connecting rod. In addition, the case where the vibration damping device is mounted at the position C in FIG. 11 is a comparison in which a torque rod having a conventional structure in which the vibration damping device is disposed in the middle portion of the rod axis direction is used as the vibration-proof connecting rod. An example is shown.

  According to this simulation result, in the torque rod according to the first embodiment in which the vibration damping device is provided at the position A in FIG. 11, the noise level is remarkably high as shown by the broken line in FIG. It was confirmed that the damping effect on the transmission vibration was effectively exhibited. This is also apparent from a comparison with the calculated value of the noise level in the torque rod without the damping device shown by the solid line in FIG.

  Further, in the torque rod according to the second embodiment in which the vibration damping device is provided at the position B in FIG. 11, as shown by the one-dot chain line in FIG. It was confirmed that the noise level was reduced to the same extent as when the device was provided, and that an effective damping effect on the transmitted vibration was exhibited.

  On the other hand, in the torque rod as a comparative example in which the vibration damping device is provided at the position C in FIG. 11, the noise level is hardly lowered as shown by the two-dot chain line in FIG. The damping effect that should be exhibited by the vibration device is not effectively obtained. This is also clear from the fact that a result almost equal to the simulation result of the torque rod without the vibration damping device indicated by the solid line is obtained.

  In short, from the result of the simulation shown in FIG. 10, the torque rod having the structure according to the present invention in which the vibration damping device is provided for the specific portion where the displacement at the time of the transmission vibration input is large can be obtained. It has been clarified that acceleration noise caused by vibration transmitted to the passenger compartment can be effectively and effectively prevented. On the other hand, it was also confirmed that an effective damping effect could not be obtained when a damping device was provided in the axially intermediate portion of the torque rod.

  From these results, the arrangement of the vibration damping device at a specific portion, that is, the half-circumferential portion opposite to the rod main body on the circumference of the arm eye shown in the present invention is transmitted between the connection target members via the rod main body. It was shown to be extremely effective for the purpose of suppressing vibrations.

  As mentioned above, although some embodiment of this invention has been described, this is an illustration to the last, Comprising: This invention is not limited at all by the specific description in this embodiment.

  For example, in the first and second embodiments, the vibration damping device 44 is disposed only near one end of the torque rods 10 and 64 in the axial direction. However, the damping device 44 is not necessarily provided only on one end side, and the damping device 44 may be provided on both ends.

  Further, it is not always necessary to provide one vibration damping device for one end of the anti-vibration connecting rod, and a plurality of vibration damping devices may be provided at one end. Specifically, for example, by providing a plurality of vibration damping devices smaller than the vibration damping device 44 at one end of the vibration damping connecting rod, a space for mounting the vibration damping connecting rod is required. It is also possible to realize a vibration control device according to the vibration control performance.

  Further, in the first embodiment, an example is shown in which the vibration damping device 44 is provided so as to be positioned on the opposite side of the rod body 12 on the rod central axis on the circumference of the second arm eye 16. In the second embodiment, an example is shown in which the vibration damping device 44 is provided on the circumference of the second arm eye 16 so as to be positioned in a direction orthogonal to the rod central axis. However, the position of the vibration damping device 44 in these embodiments is merely an example, and it is only necessary that the vibration damping device be positioned in the half-circumferential portion on the opposite side of the rod body on the circumference of the support cylinder portion. In addition, when the displacement amount in the both ends of a rod main body differs mutually, in order to acquire a damping effect effectively, a damping device is provided in the edge part by the side with a large displacement amount.

  In the first and second embodiments, the housing main body 52 constituting the housing 46 of the vibration damping device 44 is integrally formed with the second arm eye 16, but for example, a damping body formed as a separate body. The vibration device can be fixedly attached to the second arm eye 14 by retrofitting. By adopting such a retrofitted vibration damping device, various combinations of the required performance can be achieved by changing the combination of the anti-vibration connecting rod and the vibration damping device according to the installation space and the required vibration damping performance. It becomes possible. Further, by attaching the vibration damping device at a specific position indicated by the present invention as a retrofit, the present invention can be applied to the vibration proof connecting rod having a conventional structure.

  In the first and second embodiments, the side wall surface of the independent mass member 50 and the mass accommodation space are provided in a state where the mass accommodation space 48 of the housing 46 and the independent mass member 50 are positioned on the same central axis. Between the inner peripheral wall surfaces of the place 48, a minute gap is formed over the whole, and the central portion of the independent mass member 50 in the left-right width direction (axial direction) is the center of the mass accommodating space 48 in the same direction. In a state of being aligned with respect to the portion, a minute gap is formed between the longitudinal direction end surface of the independent mass member 50 and the bottom wall surface of the mass accommodating space 48 and the wall surface of the lid plate member 54 on the mass accommodating space 48 side. Was formed. However, these gaps formed between the outer wall surface of the independent mass member 50 and the inner wall surface of the mass housing space 48 are not essential constituent elements in the present invention.

  That is, the independent mass member 50 is independently accommodated and disposed in the mass accommodation space 48 without being bonded, so that the independent mass member 50 elastically strikes the inner surface of the mass accommodation space 48 when a vibration is input. It only has to be. Specifically, even if the space between the mass metal fitting 60 and the mass accommodating space 48 is filled with the contact rubber layer 62 without a gap in a stationary state where no vibration is input, the vibration Due to the elastic deformation of the abutting rubber layer 62 at the time of input, a gap is repeatedly generated between the abutting rubber layer 62 and the mass accommodating space 48, whereby the mass fitting 60 is formed on the peripheral wall portion of the mass accommodating space 48. It is only necessary to repeatedly hit against it.

  In the above-described embodiment, the independent mass member 50 is configured by vulcanizing and bonding the contact rubber layer 62 so as to cover the surface of the mass metal fitting 60. However, the independent mass member 50 is not necessarily provided on the surface. The contact rubber layer may not be provided, and the contact between the independent mass member 50 and the housing 46 may be realized elastically. Specifically, for example, when the contact rubber layer is vulcanized and bonded to the inner peripheral wall surface of the cylindrical housing 46, the hard mass metal fitting 60 may be employed as the independent mass member. Is possible.

  Further, in the first and second embodiments, the contact rubber layer 62 is disposed between the contact surfaces of the mass fitting 60 and the housing 46 by being vulcanized and bonded to the surface of the mass fitting 60. The contact rubber layer 62 is not necessarily bonded to the mass metal fitting 60 or the housing 46. For example, a contact rubber layer formed of a thin rubber elastic body that is not bonded to any of the mass fitting 60 and the housing 46 is disposed between the contact surfaces of the mass fitting 60 and the housing 46 by main vibration input. The mass metal fitting 60 and the housing 46 may be elastically brought into contact with each other via a contact rubber layer.

  In the first and second embodiments, the first rubber bush 18 and the second rubber bush 20 have different dynamic spring constants, but the present invention is provided at both ends of the rod. The present invention is also applicable when the dynamic spring constants of the vibration isolating bushing are the same. Even if the dynamic spring constants of the vibration isolating bushing are the same, the rod body is displaced so that both ends of the rod body swing due to the difference in rigidity on the connection target member side, etc., so the acceleration exerted on the vibration damping device is advantageous. Can be obtained.

  Further, the rod body of the vibration-isolating connecting rod to which the present invention is applied does not necessarily extend linearly, for example, it is bent in an L shape, or is partially curved or curved in the axially intermediate portion. May be bent. In such a curved or bent anti-vibration connecting rod, the central axis refers to a straight line connecting the centers of the arm eyes provided at both ends of the rod body as described in the above embodiment.

  In addition, the rod body 12 in the first and second embodiments has a plate shape, but the shape of the rod body and the like should be appropriately designed according to required performance such as durability. However, it is not particularly limited. When other structures are specifically exemplified, a rod-like rod body extending with a circular cross section or a rectangular cross section can be employed.

  In the first and second embodiments, specific examples of the present invention applied to a torque rod of an automobile have been described. However, the present invention is applicable to an automobile in addition to an anti-vibration connecting rod for an automobile such as a suspension rod. Any of the other anti-vibration connecting rods can be applied.

  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.

It is a longitudinal cross-sectional view which shows the torque rod for motor vehicles as 1st embodiment of this invention, Comprising: II sectional drawing of FIG. II-II sectional drawing of FIG. The side view which shows the integrally molded product of the rod main body which comprises the torque rod. IV-IV sectional drawing of FIG. Schematic explaining the vibration input state of the torque rod. The graph which shows the dynamic spring characteristic of the torque rod. The graph which shows the dynamic spring characteristic in the vehicle mounting state of the torque rod. It is a longitudinal cross-sectional view which shows the torque rod for motor vehicles as 2nd embodiment of this invention, Comprising: VIII-VIII sectional drawing of FIG. IX-IX sectional drawing of FIG. The graph which shows the simulation result of the noise at the time of acceleration. FIG. 11 is a layout diagram of a vibration damping device showing the simulation conditions of FIG. 10.

Explanation of symbols

10: Torque rod, 12: Rod body, 14: First arm eye, 16: Second arm eye, 18: First rubber bush, 20: Second rubber bush, 44: Damping device, 46: Housing, 48: Mass storage space, 50: Independent mass member

Claims (6)

Support cylinders are formed at both ends of the rod body, and vibration isolating bushes are assembled to the support cylinders, and the anti-vibration bushes are attached to each one of the members to be connected. In the anti-vibration connecting rod that configures the vibration transmission system by connecting the members to be connected to each other,
A hollow housing is provided in a half-circumferential portion of the support cylinder portion opposite to the rod body side, and an independent mass member is provided with respect to a mass receiving space formed in the hollow portion of the housing. Non-adhesive, non-adhesive housing and arrangement that can be displaced independently, and the independent mass member is independently displaced with respect to the housing and elastically brought into contact with the housing by vibration input in a direction perpendicular to the axis of the rod body. An anti-vibration connecting rod comprising the device.   The anti-vibration connecting rod according to claim 1, wherein the housing is provided on the circumference of the support cylinder portion so as to be positioned on the opposite side of the rod body on the central axis of the rod body.   The vibration-isolating connecting rod according to claim 1, wherein the housing is provided so as to be positioned in a direction orthogonal to the axial direction of the rod body on the periphery of the support cylinder portion.   The housing has a hollow structure having a cylindrical inner peripheral surface, and the independent mass member has a cylindrical outer peripheral surface corresponding to the inner peripheral surface of the housing, and is perpendicular to the axis of the rod body. 4. The anti-vibration connecting rod according to claim 1, wherein the inner peripheral surface of the housing and the outer peripheral surface of the independent mass member are brought into contact with each other by vibration input in a direction.   The housing is provided on the periphery of the supporting cylinder portion to which the vibration isolating bushes provided at both ends of the rod body have different dynamic spring constants and to which the vibration isolating bush having a smaller dynamic spring constant is attached. The anti-vibration connecting rod according to any one of claims 1 to 4, wherein the anti-vibration connecting rod is provided.   A bottomed cylindrical base portion is integrally formed with the support cylinder portion, and an opening of the base portion is covered with a lid member, whereby the housing having the mass accommodation space is configured. Item 6. The anti-vibration connecting rod according to any one of Items 1 to 5.

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