JP2005133861A - Active fluid filled-in type vibration-resistant device - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To provide an active fluid filled-in type vibration-resistant device capable of easily assembling a connecting rod connecting an exciting plate and an armature even though there is a scatter on a relative position of the armature of an actuator against the exciting plate and stably and effectively giving exciting drive force with the actuator. <P>SOLUTION: The vibration-resistant device inserts a drive rod 78 to an inserting hole 104 in a loose fitting state by arranging the inserting hole 104 on the armature 100. Upon preparing a locking member 120 in the vicinity of a projected tip of the drive rod 78, the locking member 120 is locked in an axial direction against a step section 106 arranged on an intermediate section of the inserting hole 104 in an axial direction, and an urging means 124 elastically pushing the locking member 120 to the step section 106 of the armature 100 so as to permit sliding displacement in a perpendicular direction is assembled in the armature 100. <P>COPYRIGHT: (C)2005,JPO&NCIPI

Description

  The present invention is employed in, for example, an automobile engine mount, body mount, vibration control device, or the like, and can exhibit an active or counterbalanced vibration isolation effect against the vibration to be isolated. In particular, a part of the wall portion of the vibration action chamber in which the incompressible fluid is sealed is constituted by a vibration plate, and the vibration plate is driven by the actuator to control the pressure of the vibration action chamber. The present invention relates to an active fluid-filled vibration isolator that can obtain an active vibration isolating effect.

  As a type of anti-vibration device as an anti-vibration coupling body or an anti-vibration support body interposed between members constituting the vibration transmission system, the first mounting member and the second mounting member are connected by a rubber elastic body. In addition, a part of the wall portion is formed of the main rubber elastic body to form a vibration action chamber into which vibration is input, and an incompressible fluid is sealed in the vibration action chamber, while the wall portion of the vibration action chamber A fluid enclosure in which another part of the actuator is constituted by a vibration plate, and an actuator for driving the vibration plate is provided, and the vibration chamber is pressure-controlled by exciting the vibration plate An active vibration isolator of the type is known. For example, the anti-vibration device described in Patent Literature 1, Patent Literature 2, and the like. Such an active fluid-filled vibration isolator is capable of counteracting vibrations by applying an excitation force corresponding to vibration to be vibrated against a member to be vibration-isolated, By actively changing the spring characteristics according to the input vibration and reducing the dynamic spring, etc., it is possible to obtain a positive anti-vibration effect against the vibration. Application is considered.

  By the way, in such an active fluid-filled vibration isolator, since it is necessary to highly accurately control the vibration plate with a frequency and phase corresponding to vibration to be vibrated, as an actuator, for example, As described in the above-mentioned patent documents and the like, vibration means that drives the armature using magnetic force or electromagnetic force generated by energization of the coil is preferably employed. Also, such an actuator is generally connected to the main rubber elastic body by connecting the first mounting member and the second mounting member with the main rubber elastic body for reasons such as the manufacturing process of the vibration isolator. It will be formed separately from the main body of the vibration isolator that forms the vibration action chamber in which a part of the wall is formed by the vibration plate, and the separate body of the actuator is fixed to the second mounting member. On the other hand, the armature is connected and fixed to the vibration plate of the vibration isolator main body via a connecting rod later.

  However, since the vibration plate is elastically connected to the second mounting member via the support rubber elastic body in order to allow the displacement, the variation in the shrinkage amount during the vulcanization molding of the support rubber elastic body. Also, the position of the vibration plate with respect to the second mounting member is set with high accuracy due to variations in the assembly position when the support rubber elastic body is fixed to the second mounting member by caulking, etc. Difficult to do. In addition, since the actuator coil is also fixed to the second mounting member with fixing bolts, etc., the second mounting is caused by component dimensional errors or variations in the assembly position when fixing. It is difficult to set the mounting position on the member with high accuracy. In particular, the coil of the actuator is often fixed to the second mounting member via a separate bracket for mounting the second mounting member to the vibration isolation target member, and when such a separate actuator is interposed, The dimensional error of the separate bracket and the variation in the assembly position with respect to the second mounting member are also superimposed, and it becomes more difficult to ensure the accuracy of the mounting position of the actuator with respect to the second mounting member.

  For this reason, the vibration plate and the actuator to be connected to each other are overlapped by the position error of the vibration plate with respect to the second mounting member and the position error of the coil of the actuator with respect to the second mounting member. A large variation is likely to occur in the relative position to the armature, and it may be difficult to connect the vibration plate and the armature with the connecting rod.

  In order to deal with such a problem, for example, as disclosed in Patent Document 3, a connecting rod is connected to the armature so as to be able to swing, so that the relative displacement between the vibration plate and the armature can be dealt with. It is also possible. However, since the connecting rod transmits the driving force of the armature to the vibration plate, if the connecting rod is inclined with respect to the direction in which the exciting force is transmitted, the connecting rod is swung when the driving force is transmitted. As a result, not only the transmission efficiency of the driving force is lowered, but also vibration in the direction perpendicular to the axis is generated, and the operation of the vibration plate may become unstable.

  In addition, in the actuator disclosed in Patent Document 3, in order to connect the connecting rod to the armature so that the connecting rod can swing, a coil spring that exerts a biasing force on the connecting rod assembled to the armature includes a coil spring. Since the coil spring is disposed between the housing and the connecting rod, the biasing force of the coil spring is constantly exerted on the vibration plate via the connecting rod. For this reason, the position of the armature is determined based on a balance between the support rubber elastic body that elastically supports the vibration plate on the second mounting member and the coil spring, and it is difficult to optimally position the armature. was there. In addition, since the biasing force of the coil spring is always applied to the supporting rubber elastic body, if the biasing force of the coil spring is increased, there is a risk that the supporting rubber elastic body will become loose, and the connecting rod is used as an armature. On the other hand, when the biasing force of the coil spring to be positioned is small, necking of the connecting rod easily occurs, and there is a possibility that the excitation operation becomes unstable. Furthermore, since the biasing force of the coil spring also acts as an elastic supporting force for the second mounting member of the vibration plate, the displacement characteristics of the vibration plate change due to variations in the spring characteristics of the coil spring. As a result, the initial excitation characteristics may not be obtained. In addition, since the coil spring is expanded and contracted as the armature is displaced, it is inevitable that the urging force exerted on the connecting rod and the vibration plate by the coil spring is inevitably changed. There was also a problem that it was difficult to stabilize the characteristics due to changes in the operating characteristics of the rod neck and the displacement characteristics of the vibration plate. Moreover, the vibration accompanying the elastic deformation of the coil spring may be transmitted as it is from the coil housing to the second mounting member, causing abnormal noise.

JP-A-6-264955 JP-A-11-351313 JP 2001-1765 A

  Here, the present invention has been made in the background as described above, and the problem to be solved is that the actuator formed separately from the vibration isolator main body has good workability. In particular, even if the relative position of the armature of the actuator with respect to the vibration plate varies, the connecting rod that connects the vibration plate and the armature can be easily assembled and the actuator can be An object of the present invention is to provide an active fluid filled type vibration isolator having a novel structure capable of stably and efficiently exerting a vibration driving force from an armature to a vibration plate via a connecting rod.

  Hereinafter, embodiments of the present invention made to solve the above-described problems will be described. In addition, the component employ | adopted in each aspect as described below is employable by arbitrary combinations as much as possible. In addition, aspects or technical features of the present invention are not limited to those described below, but are based on the entire specification and drawings, or based on the inventive concept that can be grasped by those skilled in the art from these descriptions. It should be understood that

(Aspect 1 of the present invention)
That is, according to the first aspect of the present invention, the first mounting member and the second mounting member are connected by the main rubber elastic body, and a part of the wall portion is configured by the main rubber elastic body so that the incompressible fluid is formed. Is formed to form a vibration action chamber in which pressure fluctuations are generated based on elastic deformation of the main rubber elastic body when vibration is input between the first mounting member and the second mounting member. Another part of the wall of the vibration working chamber is constituted by a vibration plate, and the vibration plate is elastically supported by the support rubber elastic body so as to be displaceable with respect to the second mounting member. An active type in which an actuator for controlling the pressure of the vibration action chamber by applying a driving force to the vibration plate to displace the vibration plate is disposed on the opposite side of the vibration action chamber with the vibration plate interposed therebetween. In the fluid filled type vibration damping device, the coil is fixedly attached to the second mounting member. The actuator is incorporated in the hollow hole of the coil so as to be displaceable in the axial direction, and the armature is driven and displaced in the vibration displacement direction of the vibration plate by energizing the coil. The drive rod protrudes from the vibration plate toward the armature, and an insertion hole extending in the axial direction is provided to the armature so that the drive rod is inserted into the insertion hole in a loosely inserted state. The locking rod is provided near the projecting tip of the drive rod, and the locking member is locked in the axial direction with respect to the stepped portion provided in the axially intermediate portion of the insertion hole. The armature is prevented from coming out to the side of the vibration plate, and the locking member is elastic so as to allow a sliding displacement in a direction perpendicular to the axis with respect to the step portion of the armature. That incorporated to the armature biasing means for positioning and holding the state of projecting toward the pressurized oscillating plate from the armature to the drive rod by pressing, characterized.

  In the active fluid-filled vibration isolator having the structure according to this aspect, the drive rod is disposed in such a manner that the sliding displacement in the direction perpendicular to the axis with respect to the armature is allowed. Even if a relative displacement between the vibration plate and the armature occurs due to the overlap of the upper position, etc., the relative displacement is absorbed by the sliding displacement between the drive rod and the armature. Thus, the assembly can be easily performed while suppressing the relative inclination of the drive rod and the armature. In addition, since the relative inclination of the drive rod and armature can be suppressed and assembled, the armature's excitation force can be stably and efficiently applied to the drive rod, thereby stabilizing the vibration plate. Thus, it is possible to vibrate efficiently.

  Further, since the urging means is incorporated in the armature, the urging force and the reaction force of the urging means are both applied to the armature, and it is prevented from acting on the supporting rubber elastic body. As a result, the urging force of the urging means can be sufficiently obtained, and since the urging force does not act on the support rubber elastic body, the durability of the support rubber elastic body does not become a problem. Furthermore, since the armature incorporating the biasing means is not directly fixed to the coil housing or the second mounting member, the coil housing or the second mounting member is vibrated due to the deformation of the biasing means. Therefore, the generation of abnormal noise is not a problem.

  In addition, it is conceivable that the urging means is incorporated between the opposing surfaces of the vibration plate and the armature. Then, the armature and the vibration plate are rubbed by the deformation of the coil spring disposed outside the armature, and dust is generated. May occur, and the dust may enter a minute gap between the coil and the armature to cause malfunction. However, in this aspect, since the urging means is incorporated in the armature, such malfunction due to the generation of dust is avoided as much as possible.

  Further, in order to achieve a better sliding displacement between the locking member provided on the drive rod and the stepped portion of the armature, for example, a sliding member made of a low friction material such as polyethylene or polytetrafluoroethylene is used as the sliding member. It may be incorporated on the moving surface. Further, a low friction process may be performed on the sliding surface between the locking member and the stepped portion of the armature.

(Aspect 2 of the present invention)
According to a second aspect of the present invention, in the active fluid-filled vibration isolator according to the first aspect, a relative allowable displacement amount in a direction perpendicular to the axis of the drive rod with respect to the armature is 0.2 mm to
The allowable displacement amount in the direction perpendicular to the axis with respect to the insertion hole of the drive rod and the allowable displacement amount in the direction perpendicular to the axis at the allowable portion of the sliding displacement on the stepped portion of the locking member so as to be within a range of 3 mm. It is characterized by being set.

  In the active fluid-filled vibration isolator constructed according to this aspect, the driving force is more stably transmitted between the driving rod and the armature. That is, if the allowable displacement is too small, there is a possibility that the relative positional deviation between the vibration plate and the armature cannot be sufficiently absorbed. On the other hand, if the gap is too large, it will allow more displacement than necessary, which may cause rattling of the drive rod, and the drive rod's center axis is far from the center axis of the armature. The driving reaction force exerted from the rod becomes an eccentric load with respect to the armature, and there is a possibility that the stability of the operation is lowered. Here, by setting the relative permissible displacement amount in the direction perpendicular to the axis of the arm of the drive rod within the range according to this aspect, the drive rod absorbs the relative displacement between the vibration plate and the armature. Therefore, it is possible to reduce the drive reaction force exerted on the armature as an eccentric load with respect to the armature as much as possible, and to effectively ensure the operation stability.

  In this aspect, the relative permissible displacement amount in the direction perpendicular to the axis of the drive rod with respect to the armature is the distance between the opposed surfaces of the stepped portion inner peripheral surface of the armature and the drive rod or the inner peripheral surface of the armature and the locking member. This is determined by the smaller one of the distances between the opposing surfaces to the outer peripheral surface, and the smaller allowable displacement amount of these two opposing surface distances is set within the allowable displacement amount range shown in this embodiment. It should be.

(Aspect 3 of the present invention)
According to a third aspect of the present invention, in the active fluid-filled vibration isolator according to the first or second aspect, the insertion hole of the armature is positioned on the opposite side of the vibration plate across the stepped portion. The portion is a large-diameter accommodation cavity, and the biasing means is incorporated in the accommodation cavity in the accommodation state.

  In the active fluid-filled vibration isolator having the structure according to this aspect, it is possible to efficiently secure the accommodating area of the urging means, and a sufficiently large armature and a sufficiently large urging force. Means can be obtained in a mutually compatible manner. Furthermore, since a large space for assembling the locking member and the biasing means is ensured at the time of assembly, the assembling work can be easily performed.

(Aspect 4 of the present invention)
According to a fourth aspect of the present invention, in the active fluid-filled vibration isolator according to any one of the first to third aspects, the locking member is screwed to the drive rod, and the amount of screwing is adjusted. Thus, the position of the locking member can be changed and set in the axial direction of the drive rod.

  In the active fluid-filled vibration isolator constructed according to this aspect, the axial position of the drive rod relative to the armature can be easily and accurately set by changing the position of the locking member in the axial direction of the drive rod. It becomes possible to adjust well. Thus, by adjusting the position of the armature in the axial direction with respect to the vibration plate, for example, the armature can be accurately positioned with respect to the coil, or the support rubber elastic body can be initially deformed by a static force exerted on the armature. It is also possible to avoid this, and the vibration isolation characteristics of the active fluid filled vibration isolator can be adjusted and set with high accuracy.

  Further, since the engaging member is maintained in engagement with the step portion of the armature by the biasing means, when the screwing amount of the locking member is adjusted, the driving rod is relatively moved, and the driving rod The position in the axial direction with respect to the armature will be displaced. That is, since the relative position in the axial direction between the urging means and the engaging member does not change, the position of the driving rod can be adjusted without changing the coupling rigidity between the driving rod and the armature while ensuring the urging force of the urging means. It can be done.

  In this aspect, the locking member may be any member that can substantially adjust the axial length of the drive rod that connects the vibration plate and the armature by adjusting the screwing amount. The specific structure of itself and the engagement structure with respect to the drive rod such as screwing are not limited at all. For example, the locking member may be constituted by a nut and screwed to a bolt-structured rod integrally formed at the tip of the drive rod, or the locking member itself may be constituted by a nut with a rod, A drive rod for connecting the vibration plate and the armature may be configured by screwing the rod portion of the stop member to a fixed rod protruding from the vibration plate. Furthermore, since the locking member is not limited to the nut structure, the locking member may have a bolt structure that is screwed into the fixed rod.

(Aspect 5 of the present invention)
Aspect 5 of the present invention is the active fluid-filled vibration isolator according to any one of aspects 1 to 4, wherein the second mounting member has a large-diameter, generally cylindrical shape, and its axial direction. The first mounting member is disposed on one opening side and is separated by the main rubber elastic body that elastically connects the first mounting member and the second mounting member. One opening in the axial direction of the second mounting member is fluid-tightly closed, and the other opening of the second mounting member is fluid-tightly closed with a flexible film. The support rubber elastic body for elastically supporting the vibration plate is provided so as to be divided at both sides in the axial direction at a middle portion in the direction, and the vibration working chamber is formed on one side with the support rubber elastic body interposed therebetween. And a variable volume balance with a part of the wall made of the flexible membrane on the other side On the other hand, a fixing bracket is fixed to the central portion of the flexible film, and the fixing bracket is overlapped and fixed to the vibration plate, and is attached to the vibration plate and the fixing bracket. And one end of the connecting rod is connected, and the coil is disposed on the other opening side of the second mounting member and supported by the second mounting member, The other end of the connecting rod is connected to the armature incorporated in the coil.

  In the active fluid-filled vibration isolator having the structure according to this aspect, by adopting the substantially cylindrical second mounting member, the vibration action chamber and the equilibrium chamber are overlapped in the axial direction inside thereof. Thus, the active fluid-filled vibration isolator according to any one of the first to fourth aspects is formed with good space efficiency. In addition to the fact that the vibration plate is supported by the second mounting member through the supporting rubber elastic body on the outer peripheral portion thereof, and can be stably disposed, the coil of the actuator is also By being coaxially disposed with respect to the vibration working chamber and the equilibrium chamber and stably supported, the driving force transmission efficiency and the operational stability can be improved. As described above, in the active fluid-filled vibration isolator having the structure according to this aspect, each component can be formed efficiently and space efficiency and operability can be improved.

  As is clear from the above description, in the active fluid-filled vibration isolator having the structure according to the present invention, the drive rod protruding from the vibration plate slides in a direction perpendicular to the axis with respect to the armature of the actuator. Therefore, even if there is a variation in the relative position of the armature with respect to the vibration plate, it can be easily assembled and the drive force by the actuator can be applied to the vibration plate. It is possible to exert it stably and efficiently.

  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 shows an automobile engine mount 10 as a first embodiment of the present invention. The engine mount 10 includes a first mounting member 12 as a first mounting member and a second mounting member 14 as a second mounting member that are spaced apart from each other and disposed therebetween. A mount main body 17 elastically connected by an interposed main rubber elastic body 16 is fitted into a bracket 19. In the engine mount 10, the first mounting bracket 12 is attached to a power unit (not shown), while the second mounting bracket 14 is attached to an automobile body (not shown) so that the power unit is supported by vibration isolation against the body. It has become. Further, under such a mounted state, the engine mount 10 has a shared load of the power unit between the first mounting bracket 12 and the second mounting bracket 14 in the mount center axis direction which is the vertical direction in FIG. As a result, the main rubber elastic body 16 is elastically deformed in the direction in which the first mounting bracket 12 and the second mounting bracket 14 approach each other. Further, the main vibration to be vibration-proofed is input between the first mounting bracket 12 and the second mounting bracket 14 in a direction in which the mounting brackets 12 and 14 approach / separate each other. ing. In the following explanation, the vertical direction means the vertical direction in FIG. 1 in principle.

  More specifically, the first mounting member 12 has a truncated conical shape. In addition, an annular plate-shaped stopper portion 18 protruding on the outer peripheral surface is integrally formed at the large-diameter side end portion of the first mounting member 12. Further, a fixed shaft 20 is integrally projected from the large-diameter end toward the upper side in the axial direction. The fixed shaft 20 is formed with a fixing screw hole 22 that opens to the upper end surface. The first mounting bracket 12 is attached to a power unit of an automobile (not shown) by a fixing bolt (not shown) screwed into the fixing screw hole 22.

  On the other hand, the second mounting bracket 14 has a large-diameter, generally cylindrical shape. Further, a step portion 24 is formed at an axially intermediate portion of the second mounting bracket 14, and the upper side in the axial direction is a large diameter portion 26 across the step portion 24, and the lower side in the axial direction is The small diameter portion 28 is used. A thin seal rubber layer 30 is formed on the inner peripheral surface of the large diameter portion 26. Further, a diaphragm 32 made of a thin rubber film as a flexible film is disposed in the opening portion on the lower side in the axial direction, and the outer peripheral edge portion of the diaphragm 32 is in the axial direction of the second mounting bracket 14. By vulcanizing and bonding to the lower opening edge, the lower opening in the axial direction of the second mounting bracket 14 is covered with a fluid-tight cover. Further, a connecting fitting 34 as a fixing fitting having a substantially inverted cup shape is vulcanized and bonded to the center portion of the diaphragm 32.

  The first mounting bracket 12 is positioned so as to be spaced apart upward in the axial direction of the second mounting bracket 14, and the first mounting bracket 12 and the second mounting bracket 14 are made of a main rubber elastic body. 16 is elastically connected.

  The main rubber elastic body 16 has a substantially truncated cone shape as a whole, and a mortar-shaped recess 36 is formed on the end face on the large diameter side. The first mounting bracket 12 is vulcanized and bonded to the end surface on the small diameter side of the main rubber elastic body 16 in a state of being inserted in the axial direction. The stopper portion 18 of the first mounting bracket 12 is overlapped with the small-diameter side end surface of the main rubber elastic body 16 and vulcanized and bonded, and a buffer rubber 38 protruding upward from the stopper portion 18 includes main rubber. It is formed integrally with the elastic body 16. A connecting sleeve 40 is vulcanized and bonded to the outer peripheral surface on the large diameter side of the main rubber elastic body 16.

  The connecting sleeve 40 vulcanized and bonded to the outer peripheral surface on the large-diameter side of the main rubber elastic body 16 is fitted into the large-diameter portion 26 of the second mounting bracket 14 so that the large-diameter portion 26 is reduced in diameter. Thus, the main rubber elastic body 16 is fluidly fitted and fixed to the second mounting bracket 14. As a result, the axially upper opening of the second mounting bracket 14 is covered fluid-tightly by the main rubber elastic body 16, so that the main rubber elastic body is placed inside the second mounting metal 14. Between the opposing surfaces of 16 and the diaphragm 32, a region that is fluid-tightly blocked from the external space is formed, and an incompressible fluid is sealed therein.

  As the incompressible fluid to be enclosed, for example, water, alkylene glycol, polyalkylene glycol, silicone oil or the like can be used, and in particular, to effectively obtain a vibration isolation effect based on the resonance action of the fluid. And a viscosity of 0.1 Pa. A low-viscosity fluid of s or less is preferably employed.

  Further, a partition member 42 and an orifice member 44 are incorporated in the second mounting member 14 and are disposed between the opposing surfaces of the main rubber elastic body 16 and the diaphragm 32.

  The partition member 42 has a support rubber elastic body 46 that spreads with a predetermined thickness, and a vibration plate 48 is vulcanized and bonded to a central portion of the support rubber elastic body 46. The vibration plate 48 has a shallow substantially inverted cup shape, and the outer peripheral edge portion thereof is vulcanized and bonded to the inner peripheral edge portion of the support rubber elastic body 46. An annular outer peripheral metal fitting 50 is vulcanized and bonded to the outer peripheral edge of the support rubber elastic body 46. In addition, the outer peripheral metal fitting 50 is formed with a circumferential groove 52 that extends continuously in the circumferential direction.

  And the axial direction upper side opening part of this outer periphery metal fitting 50 is made into the flange-shaped part 51 extended to radial direction outward, the flange-shaped part 51 is piled up on the step part 24 of the 2nd attachment metal fitting 14, and a step part 24 and the connecting sleeve 40 are clamped and fixed. As a result, the partition member 42 is disposed so as to extend in the direction perpendicular to the axis at the intermediate portion between the opposing surfaces of the main rubber elastic body 16 and the diaphragm 32, and the interior of the second mounting bracket 14 is divided into two sides in the axial direction. I'm coughing. Therefore, on the upper side across the partition member 42, a vibration action in which a part of the wall portion is configured by the main rubber elastic body 16 and pressure fluctuations are generated due to elastic deformation of the main rubber elastic body 16 when vibration is input. A working fluid chamber 54 as a chamber is formed. On the other hand, below the partition member 42, an equilibrium chamber 56 is formed in which a part of the wall portion is constituted by the diaphragm 32 and volume change is easily allowed.

  Further, the orifice member 44 is configured by superimposing the upper and lower thin plates on each other, and the outer peripheral edge portion thereof is overlapped with the flange-like portion 51 of the outer peripheral metal fitting 50, so that the flange-like portion 51 and the main rubber elasticity By being sandwiched between the inner peripheral edge of the large-diameter side end of the body 16, the body 16 is fixedly supported by the second mounting bracket 14 via the outer peripheral bracket 50. As a result, the orifice member 44 is disposed so as to extend in the direction perpendicular to the axis at the intermediate portion between the opposing surfaces of the main rubber elastic body 16 and the partition member 42, and the working fluid chamber 54 is divided into two sides in the axial direction. Yes. Thus, a pressure receiving chamber 58 having a wall portion formed of the main rubber elastic body 16 is formed on the upper side of the orifice member 44. On the other hand, on the lower side of the orifice member 44, a vibration chamber 60 is formed in which a part of the wall portion is composed of a vibration plate 48.

  Further, a circumferential passage 45 extending continuously in the circumferential direction between the overlapping surfaces of the upper and lower thin plates is formed in the outer peripheral edge portion of the orifice member 44. One end of the circumferential passage 45 is connected to the pressure receiving chamber 58, and the other end is connected to the excitation chamber 60. Thus, a first orifice passage 62 that allows the pressure receiving chamber 58 and the vibration chamber 60 to communicate with each other is formed. Note that the first orifice passage 62 is tuned to a medium frequency range such as idling vibration of about 30 to 40 Hz, for example.

  Furthermore, the outer peripheral edge of the orifice member 44 is overlapped with the outer peripheral edge of the partition member 42, and the second orifice is formed by covering the peripheral groove 52 formed in the outer peripheral edge of the outer peripheral metal fitting 50. A passage 65 is formed. The second orifice passage 65 has one end connected to the pressure receiving chamber 58 through the vibration chamber 60 and the first orifice passage 62, and the other end connected to the equilibrium chamber 56. As a result, a second orifice passage 65 that allows the pressure receiving chamber 58 and the equilibrium chamber 56 to communicate with each other is formed. The second orifice passage 65 is tuned to a low frequency region such as an engine shake of about 10 Hz.

  The specific form and tuning of the orifice passage are not limited in any way. In addition to the above-described embodiment, for example, the pressure receiving chamber 58 and the excitation chamber 60 are directly passed through the central portion of the orifice member 44. A first orifice passage in the form of a through hole to be communicated is formed, and the first orifice passage is tuned to a high frequency region such as a booming sound of about 50 to 150 Hz, while the circumferential passage 45 and the outer periphery of the orifice member 44 The second orifice passage may be formed by directly connecting the peripheral grooves 52 of the metal fitting 50 in series.

  Further, the mount body 17 having the above-described structure has a second mounting bracket 14 fitted in a bracket 19, and is attached to a vehicle body (not shown) via the bracket 19.

  The bracket 19 has a thick cylindrical shape. A step surface 64 is formed on the inner peripheral surface of the central portion in the axial direction, and the upper portion of the step surface 64 has a large diameter. A stopper fitting 66 is bolted to the upper end surface of the bracket 19, and a stopper fitting 68 is bolted to the lower end surface. The stopper fitting 66 has a large-diameter cylindrical shape, and has a flange portion 70 that spreads outward at the lower end opening. The flange portion 70 is overlapped with the upper end surface of the bracket 19 and fixed with bolts. Yes. On the other hand, an abutting portion 72 extending inward is formed in the upper end opening, and the stopper portion 18 of the first mounting bracket 12 abuts against the abutting portion 72 via a buffer rubber 38. The stopper function in the rebound direction is demonstrated. Note that an umbrella-shaped brim member 74 is attached to the bolt fixing portion of the first mounting member 12 so as to cover the upper end opening of the stopper member. On the other hand, the stopper metal 68 has an annular plate shape, and is bolted with an inner diameter dimension slightly projecting radially inward at the lower end opening of the bracket 19.

  The second mounting fitting 14 fitted into the bracket 19 is fixed in an axial direction by the flange portion 70 of the stopper fitting 66 and the stopper fitting 68 so that it cannot be pulled out. The bracket 19 is integrally formed with a plurality of leg portions 76 that protrude on the outer peripheral surface and extend downward, and these leg portions 76 are placed on a body of an automobile (not shown) and fixed with fixing bolts. As a result, the engine mount 10 is mounted on the body of the automobile.

  Further, in the mount body 17, the vibration plate 48 provided on the partition member 42 is overlapped and fixed in close contact with the connecting fitting 34 provided on the diaphragm 32. Then, a connecting rod 78 as a drive rod is fixed to the vibration plate 48 and the connection fitting 34, and the connection rod 78 is protruded downward in the axial direction from the vibration plate 48 and the connection fitting 34.

  In addition, a sandwiching rubber layer 80 integrally formed with the diaphragm 32 is attached to the connection fitting 34 over substantially the entire circumference, so that the space between the overlapping surface with the vibration plate 48 is fluid. It is tightly sealed. Further, the vibration plate 48 and the connection fitting 34 are overlapped at each upper bottom portion in the center, and a caulking portion 82 formed integrally with the upper end portion of the connection rod 78 is inserted through these center portions. The vibration plate 48 and the coupling fitting 34 are caulked and fixed in close contact by the caulking portion 82, and the coupling rod 78 penetrates the coupling fitting 34 from the vibration plate 48 and extends outward in the axial direction. It is protruding.

  Further, an electromagnetic drive means as an actuator is provided in the axially lower side of the second mounting member 14 from which the connecting rod 78 is protruded, that is, on the side opposite to the working fluid chamber 54 across the vibration plate 48 and the connecting member 34. 84 is disposed and attached to the bracket 19.

  The electromagnetic driving means 84 includes a coil 86 and a housing 88 fixedly assembled to the coil 86 so as to surround the coil 86. The housing 88 has an outer yoke portion 90 that extends through the entire circumference in an L-shaped cross-section so as to surround the outer peripheral surface and the lower end surface of the coil 86, with a through hole 96 penetrating therethrough. In addition, a cylindrical inner yoke 92 extending to cover the inner peripheral surface of the coil 86 over the entire axial direction is assembled to the inner peripheral surface of the coil 86. The coils 86 and the inner yoke 92 are assembled so that their upper end portions have substantially the same axial height, and are set at a position slightly lower than the upper end portion of the outer yoke portion 90. Each of the outer yoke portion 90 and the inner yoke 92 is made of a ferromagnetic material, and a magnetic pole is formed at the upper end edge portion when the coil is energized.

  On the other hand, the housing 88 is formed with an annular fixing portion 94 extending from the upper end portion of the outer yoke portion 90 to the outer periphery, and the annular fixing portion 94 is superimposed on the lower surface of the bracket 19 and fixed with a fixing bolt. Thus, the central axis of the coil 86 is substantially aligned with the central axis of the mount body 17 and is aligned with the central axes of the second mounting bracket 14 and the vibration plate 48. Further, a lid member 98 is mounted below the housing 88 to prevent dust and the like from entering the through hole 96 of the housing 88.

  The armature 100 is assembled in the through hole 96 of the housing 88 in which the coil 86 is assembled. The armature 100 is formed of a ferromagnetic material having a circular block shape as a whole, and has an outer diameter slightly smaller than the inner diameter of the inner yoke 92 and is fitted into the inner yoke 92 on the same central axis as the coil 86. Thus, relative displacement in the axial direction is possible. Further, the armature 100 has an axial length slightly larger than that of the coil 86, and an upper end portion of the armature 100 has a radially protruding portion 101 whose outer peripheral edge is widened to the vicinity of the inner peripheral edge of the outer yoke 90. Has been. Due to the radial protrusion 101, the magnetic gap in which an effective magnetic attractive force is applied between the outer yoke portion 90 and the inner yoke 92 is adjusted and formed when the coil 86 is energized. Yes. For example, as shown in the figure, effective magnetic attraction force is generated between the radial protrusion 101 and the upper edge of the outer yoke 90 and between the radial protrusion 101 and the upper edge of the inner yoke 92. It is designed to work.

  The armature 100 is formed with an insertion hole 104 that passes through the central axis. The insertion hole 104 has an intermediate portion in the axial direction as a step portion 106, an upper portion in the axial direction across the step portion 106 as a small diameter portion 108, and a lower portion in the axial direction as a large diameter portion 110. Further, an annular plate-shaped bottom cover 112 is fixed to the lower end surface in the axial direction of the armature 100, and an accommodation space 114 is formed by the bottom cover 112 and the large diameter portion 110. The small-diameter portion 108 has a stepped portion 116 formed in an intermediate portion in the axial direction, and the inner diameter dimension thereof is slightly increased over the predetermined length of the upper portion thereof.

  Then, the projecting tip portion 118 of the connecting rod 78 is inserted into the insertion hole 104 of the armature 100 in a loosely inserted state, and the projecting tip portion 118 is projected to the accommodation space 114 of the armature 100. The protruding tip portion 118 has a bolt structure, and a locking nut 120 as a locking member is screwed to the protruding tip portion 118. The outer diameter of the locking nut 120 is larger than the inner diameter of the stepped portion 106. When the locking nut 120 is locked to the stepped portion 106, the connecting rod 78 is moved upward in the axial direction. It is considered impossible to escape. Here, the screwing position of the locking nut 120 with respect to the connecting rod 78 can be finely adjusted by the screwing amount of the locking nut 120 with respect to the connecting rod 78, and a fixed nut screwed from below the locking nut 120. By 122, the locking nut 120 is prevented from rotating, and the screwing position of the locking nut 120 can be fixedly set.

  As shown in FIG. 2, the outer peripheral edge of the connecting rod 78 and the small diameter part 108 of the armature 100 and the outer peripheral edge and the large diameter part 110 of the locking nut 120 are arranged with predetermined gaps α and β, respectively. The connecting rod 78 is displaceable in the direction perpendicular to the axis with respect to the armature 100. The relative allowable displacement in the direction perpendicular to the axis of the connecting rod 78 with respect to the armature 100 is determined by the smaller one of the gaps α and β. In this embodiment, the gap α is Therefore, it is determined by the size of the gap between the outer peripheral edge portion of the connecting rod 78 and the small diameter portion 108 of the armature 100. In addition, as an allowable displacement amount, the range of 0.2 mm-3 mm is employ | adopted suitably.

  Further, a coil spring 124 as an urging means is incorporated in the accommodation space 114 of the armature 100. The coil spring 124 has an outer diameter dimension substantially equal to the outer diameter dimension of the locking nut 120 and is disposed in a compressed state between the bottom cover 112 and the locking nut 120. Thus, an urging force directed upward in the axial direction is always applied. As a result, the locking nut 120 is overlaid on the stepped portion 106 of the armature 100 and is elastically held in this overlaid state. Therefore, the connecting rod 78 is capable of sliding displacement in the direction perpendicular to the axis with respect to the armature 100. The coil spring 124 is preferably processed so as to reduce the generation of dust due to rubbing with the locking nut 120. Therefore, a closed-end end structure is preferable to the open end, and the coil spring 124 is not ground. Also, those subjected to grinding or taper end treatment are preferably employed.

  Under such an assembled state, the armature 100 is elastically positioned and held by the spring characteristic of the support rubber elastic body 46 in the mount body 17. Under this condition, a reaction force is obtained at the contact portion between the armature 100 and the connecting rod 78 by the urging force of the coil spring 124, but the coil spring 124 is disposed in the accommodation space 114 of the armature 100. Therefore, since the reaction force applied to the support rubber elastic body 46 does not act, the durability of the support rubber elastic body 46 does not become a problem. When the main rubber elastic body 16 is elastically deformed by the shared support load of the power unit input between the first mounting bracket 12 and the second mounting bracket 14 with the engine mount 10 mounted on the vehicle. In addition, since the volume change generated in the working fluid chamber 54 is absorbed by the equilibrium chamber 56, the position of the vibration plate 48 and the position of the armature 100 is hardly affected, but due to the characteristics of the diaphragm 32 and the like. If the position of the armature 100 changes slightly, the change is taken into account and the amount of screwing of the locking nut 120 as shown in FIG. It is also possible to adjust the position so that an effective driving force is exerted.

  Although not shown, the engine mount 10 having the structure as described above can control the energization of the coil 86. For example, the engine ignition signal of the power unit is used as a reference signal and vibration is prevented. The energization control can be performed by performing feedback control such as adaptive control using the vibration detection signal of the power member as an error signal, or by using map control based on preset control data. As a result, by applying a magnetic force to the armature 100 and driving it to vibrate in the axial direction, a driving force corresponding to the vibration to be vibrated is applied to the vibration plate 48, thereby causing the working fluid chamber 54 to move. An active vibration isolation effect can be obtained by controlling the internal pressure.

  Therefore, in the engine mount 10 of the present embodiment, the connecting rod 78 protruding from the vibration plate 48 with respect to the armature 100 of the electromagnetic driving means 84 is disposed so as to be capable of sliding displacement in the direction perpendicular to the axis. Therefore, a relative positional shift due to a dimensional error during assembly and a temporary positional shift during operation of the actuator are advantageously absorbed.

  That is, when the electromagnetic driving means 84 is driven, the transmission direction of the driving force from the armature 100 to the connecting rod 78 is alternately changed by the vibration operation, so that the locking nut 120 has a relatively large biasing force. Even when pressed against the step 106, the urging force instantaneously decreases due to the action of the inertial force at the location where the direction of the driving force changes. At that moment, using the elastic force of the support rubber elastic body 46, the connecting rod 78 is slid and displaced, and the alignment with the armature 100 can be advantageously performed.

  The armature 100 and the connecting rod 78 are also temporarily displaced due to irregular elastic deformation of the support rubber elastic body 46 or until the displacement is eliminated by the sliding displacement of the connecting rod 78. And the elastic deformation of the coil spring 124 allows the connecting rod 78 to be tilted. This makes it possible to reduce or avoid the action of a torsional load between the armature 100 and the inner yoke 92. The stability and durability of the armature 100 can be advantageously maintained. In particular, in the present embodiment, the upper opening side of the small diameter portion 108 of the armature 100 is increased in diameter so that the inclination of the connecting rod 78 can be allowed more easily.

  As mentioned above, although embodiment of this invention was explained in full detail, this is an illustration to the last, Comprising: This invention is not interpreted limitedly by the specific description in this embodiment.

  For example, as in the second embodiment shown in FIG. 4, the connecting member 78 is configured by forming the locking member by the nut 126 with the rod and screwing the rod 128 onto the rod 128 protruding from the vibration plate 48. You may do it. In this embodiment, the lock bolt 130 is fitted into the nut 126 with the rod from the lower side in the axial direction, and the lock bolt 130 is brought into contact with the tip of the rod 128 in the screw hole of the nut 126 with the rod. As a result, the tightening position of the nut 126 with the rod relative to the rod 128 is locked. Also in this embodiment, the relative position of the vibration plate 48 and the armature 100 can be adjusted and set by adjusting the screwing amount of the nut 126 with the rod, which is a locking member, into the rod 128.

  Alternatively, as in the third embodiment shown in FIG. 5, a leaf spring 132 having a function as the coil spring 124 as the biasing means and a function as the bottom cover 112 in the first embodiment is employed. Is also possible. According to the present embodiment, the number of parts can be reduced, and it is not necessary to house the urging means in the housing space 114, and the assembling work is facilitated. In the third embodiment shown in FIG. 5, a leaf spring is employed for the connecting rod 78 having the structure according to the second embodiment shown in FIG. 4, but as shown in FIG. As a biasing means in the first embodiment, it is of course possible to use a leaf spring as shown in this embodiment instead of the coil spring 124 and the bottom cover 112. In the present embodiment shown in FIGS. 4 and 5, members and parts having the same structure as in the first embodiment are denoted by the same reference numerals as those in the first embodiment. Therefore, detailed description thereof will be omitted.

  In any of the above embodiments, the diaphragm 32 is disposed below the main rubber elastic body 16, and the equilibrium chamber 56 is formed between the axial lower opening of the main rubber elastic body 16 and the diaphragm 32. However, the diaphragm 32 is disposed so as to cover the main rubber elastic body 16, and the equilibrium chamber 56 is formed on the opposite side of the working fluid chamber 54 with the main rubber elastic body 16 interposed therebetween. It is also possible to apply to a vibration isolator. According to such a structure, the vibration plate 48 is directly exposed without the connection metal fitting 34 interposed therebetween, and therefore the connection rod 78 may be directly fixed to the vibration plate 48.

  The specific structures of the first and second orifice passages are appropriately changed according to the judgment of those skilled in the art depending on the required anti-vibration characteristics and the basic structure of the anti-vibration device, and are not limited in any way. It is not something.

  Further, although the coil 86 in the electromagnetic drive unit 84 is fixed by the housing 88 in this embodiment, it may be fixed directly to the second mounting member 14 without using the housing 88, for example.

  Furthermore, the specific shapes of the armature 100 and the yoke member in the electromagnetic drive means 84 are not limited. For example, the axial height of the inner yoke 92 is set to the same height as that of the outer yoke portion 90. The radially projecting portion 101 of the armature 100 may be projected downward in the axial direction so as to enter between the opposed surfaces of the inner yoke 92 and the outer yoke portion 90, or the inner peripheral surface of the lower end portion of the housing 88 is radially inward. The magnetic path may be formed so that the magnetic pole is formed there, and a magnetic gap may be formed between the magnetic pole and the lower end surface of the armature 100.

  Further, a low-friction sliding sleeve or the like may be interposed at the sliding portion between the inner peripheral surface of the through hole 96 of the housing 88 and the outer peripheral surface of the armature 100.

  In addition, the present invention relates to an anti-vibration device such as a body mount or member mount for automobiles, or a mount or a vibration damper in various devices other than automobiles, and an anti-vibration actuator used in such an anti-vibration device. On the other hand, the same applies.

  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 section showing an engine mount as a first embodiment of the present invention. It is a principal part enlarged view of the engine mount shown in FIG. FIG. 2 is an exploded explanatory view showing an attachment structure of an armature to a connecting rod in the engine mount shown in FIG. 1. It is a longitudinal cross-sectional view which shows the engine mount as 2nd embodiment of this invention. It is a longitudinal cross-sectional view which shows the engine mount as 3rd embodiment of this invention.

Explanation of symbols

DESCRIPTION OF SYMBOLS 10 Engine mount 12 1st mounting bracket 14 2nd mounting bracket 16 Main body rubber elastic body 32 Diaphragm 48 Excitation plate 54 Working fluid chamber 78 Connection rod 86 Coil 88 Housing 100 Armature 106 Step part 114 Housing space 120 Locking nut 122 Fixing nut 124 Coil spring

Claims (5)

The first mounting member and the second mounting member are connected by a main rubber elastic body, and a part of the wall portion is configured by the main rubber elastic body to enclose the incompressible fluid, thereby the first mounting member. Forming a vibration action chamber in which pressure fluctuations are generated based on elastic deformation of the main rubber elastic body when vibration is input between the member and the second mounting member; and another wall portion of the vibration action chamber A part of the vibration plate is configured so that the vibration plate is elastically supported by the support rubber elastic body so as to be displaceable with respect to the second mounting member. An active fluid-filled vibration isolator in which an actuator for controlling the pressure of the vibration action chamber by oscillating and displacing a plate is disposed on the opposite side of the vibration action chamber with the vibration plate interposed therebetween.
The coil is fixedly attached to the second attachment member, and an armature is incorporated in the hollow hole of the coil so as to be displaceable in the axial direction, and the armature vibrates the vibration plate by energizing the coil. The actuator is configured to be driven and displaced in the displacement direction, while a drive rod is projected from the vibration plate toward the armature and an insertion hole extending in the axial direction with respect to the armature is provided. The drive rod is inserted into the insertion hole in a loosely inserted state, a locking member is provided near the projecting tip of the drive rod, and the locking is made with respect to the stepped portion provided in the axially intermediate portion of the insertion hole. By locking the member in the axial direction, the drive rod is prevented from coming off from the armature to the vibration plate side, and the locking member is fixed to the step portion of the armature. A biasing means is incorporated in the armature to elastically press the driving rod so as to allow a sliding displacement in a direction perpendicular to the axis so as to project and position the drive rod from the armature toward the vibration plate. An active fluid-filled vibration isolator.   The allowable displacement amount in the direction perpendicular to the axis of the drive rod with respect to the insertion hole is set so that the relative allowable displacement in the direction perpendicular to the axis of the drive rod with respect to the armature is within a range of 0.2 mm to 3 mm. The active fluid-filled vibration isolator according to claim 1, wherein an allowable displacement amount in a direction perpendicular to the axis at an allowable portion of a slip displacement on the step portion of the stop member is set.   In the insertion hole of the armature, a portion located on the opposite side of the vibration plate across the stepped portion is a large-diameter accommodation cavity, and the biasing means is accommodated in the accommodation cavity. The active fluid-filled vibration isolator according to claim 1 or 2, which is incorporated.   The locking member is screwed to the drive rod, and the position of the locking member can be changed and set in the axial direction of the drive rod by adjusting the screwing amount. 4. The fluid-filled vibration isolator according to any one of 3 above. The second mounting member has a substantially cylindrical shape with a large diameter, and the first mounting member is disposed so as to be spaced apart from one axial side of the first mounting member. One opening in the axial direction of the second mounting member is fluid-tightly closed by the main rubber elastic body elastically connecting the member and the second mounting member, and the other opening of the second mounting member The support rubber elastic body that elastically supports the vibration plate so as to be partitioned on both sides in the axial direction at the axially intermediate portion of the second mounting member is disposed. The variable volume balance is formed in which the vibration working chamber is formed on one side of the support rubber elastic body and a part of the wall portion is formed of the flexible film on the other side. While the chamber is formed, a fixing bracket is fixed to the central portion of the flexible membrane, and the fixing bracket is One end of the connecting rod is connected to the vibration plate and fixed to the vibration plate, and the other opening side of the second mounting member is connected to the vibration plate and the fixing bracket. The coil is disposed on and supported by the second mounting member, and the other end of the connecting rod is connected to the armature incorporated in the coil. 5. The active fluid-filled vibration isolator according to any one of 4 above.

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