JP2006066840A - Solenoid actuator and active vibration-proof device using the same - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To provide a solenoid actuator which generates a vibrating force when a current is applied to its coil and has an improved structure capable of displaying target operating characteristics stably for a long term by alleviating the biased abrasion of a moving member. <P>SOLUTION: The moving member 140 is driven by the action of a magnetic field generated by a current applied to the coil member 104, and on the other hand, slanting support means 148 and 150 are provided so as to support a guide cylindrical member 126 with a cylindrical guide inner surface 128, which guides the external peripheral surface of the moving member 140 in the axial direction of the coil member 104, in such a manner that the guide cylindrical member 126 moves slantingly against the coil member 104. <P>COPYRIGHT: (C)2006,JPO&NCIPI

Description

  The present invention relates to a solenoid actuator that drives a mover by the action of a magnetic field generated by energization of a coil, and an active vibration isolator using the same, and more particularly to an engine mount, body mount, and vibration damper of an automobile. The present invention relates to a solenoid type actuator suitably employed in a vibration isolator such as the above and an active type vibration isolator using the same.

  Conventionally, as a type of vibration isolator, such as a vibration isolator support body or a vibration isolator connected between members constituting a vibration transmission system, or a vibration control apparatus mounted on a vibration member to be vibrated There is known an active vibration isolator in which vibration to be prevented is positively or counterbalanced by applying an excitation force to a vibration isolation target member or vibration isolator. For example, it is the thing of patent document 1.

  Such an active vibration isolator requires an actuator that generates an excitation force, and such an actuator requires high controllability of frequency and phase with respect to the generated excitation force.

  Therefore, as described in Patent Document 1 and Patent Document 2 described above, as an anti-vibration actuator employed in an active vibration isolator, generally, a stator in which a yoke member is assembled around a coil. The electromagnetic path using a solenoid that drives the mover in the axial direction by energizing the coil is provided by providing a mover that is driven by the action of the magnetic field generated by energizing the coil. A solenoid actuator of the type is preferably employed. Such a solenoid-type actuator can highly control the generated excitation force by controlling the energization of the coil.

  By the way, when such a solenoid type actuator is applied to an anti-vibration device as an anti-vibration actuator, for example, the movable element is vibrated and driven in a high frequency range of several tens Hz or more with an amplitude of 1 mm or less. High-precision excitation drive is required. In order to stably realize such a high-accuracy excitation drive, a guide cylinder member having a guide inner surface is disposed in the center hole of the coil, and a mover is inserted and disposed in the guide cylinder member. A guide mechanism that guides the mover in the driving direction by the inner surface is preferably employed.

  However, in such a solenoid type actuator, the tolerance of the parts in manufacturing, the assembly error, or the irregular displacement at the time of the actuator operation of the vibration isolation target member to which the mover is connected is transmitted. There was a risk of being tilted with respect to the driving direction. Here, the guide cylinder member is formed so as to extend in the target driving direction of the mover, and the gap between the mover and the guide cylinder member is very small, so that the mover is slightly tilted. There is a possibility that a single contact state with respect to the guide cylinder member occurs and the mover slides while twisting with respect to the guide cylinder member.

  Such sliding in the one-piece state increases the contact surface pressure of the contact portion with respect to the guide cylinder portion of the mover, and accelerates wear of the contact portion. In general, the surface of the mover has been subjected to various surface treatments such as sliding surface treatment using fluororesin, etc., and surface treatment for rust prevention by plating, etc. When this occurs, the surface treatment layer at the contact portion is peeled off, and the sliding characteristics and rust prevention characteristics due to these surface treatments cannot be maintained over a long period of time. In addition, the weight balance of the mover is lost due to uneven wear, and the operation stability of the solenoid may be hindered.

  In order to cope with such a problem, for example, in Patent Document 3, the inclination of the movable element is adjusted by engaging the engaging protrusion provided on the movable element with the slit provided on the inner surface of the guide and guiding it in the axial direction. A solenoid type actuator that suppresses is disclosed. However, in such a solenoid-type actuator, since the inclined movable element is intended to be corrected in the intended driving direction, the contact surface pressure at the engagement portion is further increased, and the durability of the movable element is increased. There is a risk of lowering.

  For example, Patent Document 4 discloses a solenoid-type actuator that reduces the bias of the mover by providing a bearing member including a plurality of hard spheres and an elastic member at an axial end portion of the guide inner surface. However, in such a solenoid type actuator, only the mover is pivotally supported at the end of the solenoid, and this is insufficient to prevent the tilt of the mover having a predetermined dimension in the axial direction. It was not an effective solution. In addition, there is a problem in the assembly accuracy of the bearing member, and there is a concern that the center axis alignment becomes more difficult due to further superposition of the assembly error of the bearing member.

JP 2004-76819 A JP 2004-153063 A JP-A-11-74118 JP 2002-25820 A

  Here, the present invention has been made in the background as described above, and the problem to be solved is the uneven wear of the mover in the solenoid type actuator that generates the excitation force by energizing the coil. It is an object of the present invention to provide a solenoid-type actuator having an improved structure in which a desired operation characteristic can be stably exhibited over a long period of time.

  The present invention also provides an anti-vibration actuator, an active anti-vibration device, and an active anti-vibration damper having an improved structure, which is configured using such a solenoid-type actuator. Objective.

  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 regarding solenoid type actuator)
In the first aspect of the present invention relating to the solenoid type actuator, a yoke member is assembled around the coil member to form a fixed-side magnetic path, and a mover is disposed in the central hole of the coil member so that the coil member is energized. Solenoid type assembled with a guide cylinder member having a cylindrical guide inner surface for guiding the outer peripheral surface of the mover in the axial direction of the coil member while driving the mover by the action of a magnetic field generated by The actuator is characterized in that tilting support means for tiltingly supporting the guide cylinder member with respect to the coil member is provided.

  In the solenoid type actuator structured according to this aspect, since the guide tube member can be tilted with respect to the coil member, even when the mover is tilted due to an assembly error or actuator operation, etc. The guide cylinder member is tilted so as to follow the inclination of the mover, so that the relative inclination between the mover and the guide cylinder member is kept small, and the contact surface pressure of the mover with respect to the guide cylinder member is kept small. I can do it. Accordingly, it is possible to avoid as much as possible that the movable element is driven and displaced with respect to the guide cylinder member in a one-sided state, thereby reducing uneven wear of the movable element.

  Furthermore, since the guide cylinder member is tilted in accordance with the inclination of the mover, the guide action by the guide cylinder member can be maintained effectively, and the excitation drive of the mover is performed more smoothly.

  That is, a guide cylinder member that guides the mover in the driving direction by allowing the guide cylinder member that has been fixedly arranged with respect to the coil member to guide the mover in the axial direction to be tiltable. It is possible to reduce uneven wear while maintaining the guide function. Note that “tilting” in this aspect means relative displacement in the twisting direction, that is, for example, the central axis of the guide cylinder member is inclined relative to the central axis of the coil member and the yoke member (inclined at a relative angle). Say.

  Here, the tilt support means for tiltably supporting the guide cylinder member with respect to the coil member can be realized with various structures. For example, a sliding guide surface that supports the guide cylinder member so as to be tiltable by elastically supporting the guide cylinder member with respect to the coil member, or a coil guide or a guide cylinder member that guides the guide cylinder member so as to be inclined with respect to the coil member It can be realized by forming. That is, although some suitable aspects as the tilting support means will be exemplified below, it should be understood that the specific structure of the tilting support means is not limited to the structure shown below.

(Aspect 2 of the present invention relating to a solenoid type actuator)
Aspect 2 of the present invention relating to a solenoid actuator is the solenoid actuator according to aspect 1, wherein the guide cylinder member is inserted and arranged with a predetermined gap in a radial direction with respect to the central hole of the coil member. In addition, an elastic support member is disposed between the guide tube member and the coil member and / or the yoke member at both axial ends of the guide tube member, and the guide tube is interposed via the elastic support member. The tilting support means is configured by elastically positioning and supporting the member in the axial direction and the direction perpendicular to the axial direction with respect to the coil member.

  In the solenoid actuator structured according to this aspect, the guide tube member can be tilted with respect to the coil member by elastic deformation of the elastic support member, and is elastic not only in the axial direction but also in the axial direction. Positioning is possible. Thereby, even when a relative displacement in the axial direction relative to the guide cylinder member of the mover occurs, the guide cylinder member is displaced in the axial direction along with the mover, so that the mover and the guide cylinder member The contact surface pressure can be reduced. In addition, since the elastic support member is interposed between the coil member and / or the yoke member and the guide tube member, the inclination angle of the guide tube member is limited in a buffering manner. It is also reduced that vibration and abnormal noise due to the excitation drive are transmitted to the coil member and the yoke member through the guide tube member.

(Aspect 3 of the present invention relating to a solenoid type actuator)
Aspect 3 of the present invention relating to the solenoid type actuator is the solenoid type actuator according to aspect 1 or 2, wherein the guide cylinder member is inserted and arranged with a predetermined gap in the radial direction with respect to the central hole of the coil member. In addition, a support protrusion protruding on the outer peripheral surface is provided at the axially central portion of the guide tube member, and the protrusion tip of the support protrusion is brought into contact with the inner peripheral surface of the coil member to The tilt support means is configured by allowing the guide tube member to tilt with a contact point of the portion with the coil member as a fulcrum.

  In the solenoid type actuator structured according to this aspect, the guide cylinder member can be tilted more easily by providing the support protrusion serving as a tilting fulcrum. As a result, the guide cylinder member can be quickly tilted with respect to the tilt displacement of the mover, and the one-side contact state of the mover with respect to the guide cylinder member can be eliminated or reduced more quickly. The support protrusion may be formed integrally with the guide tube member or may be provided as a separate body. Further, the support protrusions may be provided continuously over the entire circumference of the guide tube member, or may be provided separately from each other at a predetermined interval in the circumferential direction.

  Furthermore, it is more preferable that the solenoid type actuator having the structure according to the present aspect is used in combination with the elastic support member as in the second aspect. According to such an aspect, when the guide tube member is tilted to the maximum allowable amount while the tilt of the guide tube member is easily allowed by the support protrusion, the tilt is buffered by the elastic support member. I can do it.

(Aspect 4 of the present invention relating to a solenoid type actuator)
Aspect 4 of the present invention relating to the solenoid type actuator is the solenoid type actuator according to any one of the aspects 1 to 3, wherein a shock absorbing rubber sleeve is arranged between the radially opposed surfaces of the guide tube member and the central hole of the coil member. The tilting support means is configured by elastically supporting the guide cylinder member via the buffer rubber sleeve.

  In the solenoid type actuator structured according to this aspect, it is possible to dispose a buffer rubber sleeve over a wide range of the outer peripheral surface of the guide cylinder member, and the guide cylinder member is a coil member and / or a yoke member. Can be supported stably.

  In addition, the buffer rubber sleeve in this aspect does not necessarily need to be arrange | positioned covering the whole outer peripheral surface of a guide cylinder member, and may be discontinuous in the circumferential direction of a guide cylinder member. For example, when the cushioning rubber sleeve according to the present aspect is used for the guide cylinder member having the supporting projection as in the aspect 3, the cushioning rubber sleeve having a shape that avoids only the portion where the supporting projection is formed is used. It is also possible.

(Aspect 5 of the present invention relating to a solenoid type actuator)
A fifth aspect of the present invention relating to a solenoid type actuator is the solenoid type actuator according to the first or second aspect, wherein a spherical support having a center of curvature at a substantially central portion of the central hole at both axial end portions of the central hole of the coil member. While forming a concave surface, a spherical fitting convex surface corresponding to the supporting concave surface of the coil member is formed at both axial end portions of the outer peripheral surface of the guide cylinder member, and the fitting convex surface is spherical with respect to the supporting concave surface. The tilting support means is configured by fitting in a slidable manner. In the solenoid type actuator structured according to this aspect, the guide cylinder member can be stably tilted by the guide action of the support concave surface and the fitting convex surface.

(Invention relating to vibration-proof actuator)
The present invention relating to an anti-vibration actuator is an anti-vibration actuator for driving an output member spaced apart so as to be reciprocally displaceable in the axial direction in response to vibration to be anti-vibrated. The solenoid type actuator according to any one of the above aspects is used, the output member is connected to the mover of the solenoid type actuator, and the coil provided in the coil member is adapted to a target vibration. The output member is driven to vibrate by applying a driving voltage having a frequency component to drive the mover in the axial direction.

  In the anti-vibration actuator having the structure according to this aspect, it is possible to reduce the partial wear of the mover and obtain stable operating characteristics over a long period of time based on the above-described effects exhibited by the solenoid actuator. I can do it. Such an anti-vibration actuator can be applied to various types of anti-vibration devices such as engine mounts and body mounts for automobiles and active vibration dampers. The drive voltage having a frequency component may be not only alternating current but also pulsating current, and may be not only analog but also digitally controlled.

(Aspect 1 of the present invention relating to an active vibration isolator)
Aspect 1 of the present invention relating to an active vibration isolator includes a first attachment member attached to one member constituting a vibration transmission system by being connected to each other and a second attachment member attached to the other member. While being connected by the main rubber elastic body, a part of the wall is formed by the main rubber elastic body to form a pressure receiving chamber in which an incompressible fluid is enclosed, and another part of the wall of the pressure receiving chamber And an actuator that exerts a vibration force on the vibration member, and the vibration member is driven by the actuator to actively control the pressure in the pressure receiving chamber. In the active vibration isolator, the vibration isolating actuator is used as the actuator, and a housing for fixedly supporting the coil member in a substantially housed state is fixed to the second mounting member, while the vibration exciter The by concatenating said mover as the output member of the actuator for vibration-proof, that it has to be the the pressurized vibration member vibrating driven by an actuator for vibration-proof, characterized. In the active vibration isolator having the structure according to the present aspect, based on the above-described effect exhibited by the vibration isolating actuator, the partial wear of the mover is reduced, and stable operation characteristics can be obtained over a long period of time. I can do it. Further, if the coil member or the yoke member itself is attached to be tiltable, the mass becomes large and it becomes difficult to align with the mover. However, according to the present invention, only the guide tube member can be tilted. The positioning of the child and the coil member or yoke member can be maintained with high accuracy.

(Aspect 2 of the present invention relating to an active vibration isolator)
Aspect 2 of the present invention relating to an active vibration isolator is an active rod vibration isolator according to aspect 1, wherein the movable element is provided with a through-hole penetrating in the axial direction and projecting from the vibration member. And a relative displacement permissible connecting means for connecting the connecting portion provided in the movable element and the inner rod so as to allow relative displacement in the direction perpendicular to the axis. In the active vibration isolator constructed according to this aspect, even if the movable element is displaced in the direction perpendicular to the axis due to a temporary tilt displacement or assembly error of the vibration member, it can be moved by the relative displacement allowable connecting means. Since the relative displacement between the child and the inner rod in the direction perpendicular to the axis (the direction perpendicular to the displacement direction) is allowed, the influence of the tilt displacement generated in either the mover or the vibrating member is affected. A more stable operation can be realized by avoiding being exerted on the other side.

  In addition, even if a relatively large positional deviation occurs between the vibrating member and the mover due to superimposition of dimensional error of each member or variation in position on the assembly, the shaft between these members Relative displacement in the perpendicular direction is absorbed by the relative displacement permissible coupling means, so that both the members can be easily connected and assembled without exerting excessive force on the vibration member and the mover. I can do it.

  In addition, various structures are employable as a concrete structure of a relative displacement permissible connection means. For example, a protrusion that protrudes inward in the through hole of the mover is formed, and the bottom surface of the protrusion is supported so as to be slidable in the axial direction by a support member provided on the inner rod, or the protrusion It is also possible to support the bottom surface of the mover with a support member by projecting the inner rod downward from the bottom surface of the mover without forming a portion.

(The present invention relating to an active vibration isolator)
The present invention relating to a vibration isolator for active vibration isolation is applied to a vibration isolation target member, and applies an excitation force to the vibration isolation target member to exhibit an active vibration suppression effect. A vibration damper, wherein the vibration-proof actuator is used, and an attachment portion for fixing the vibration-proof actuator to one of the coil member and the mover is fixed to the vibration-proof target member. A mass portion is provided on the other of the movable elements. In the active vibration isolator having the structure according to this aspect, based on the above-described effects exhibited by the vibration isolating actuator, the partial wear of the mover is reduced, and stable operation characteristics are maintained for a long time. Can be obtained.

  As is clear from the above description, in the solenoid type actuator structured according to the present invention, when the guide cylinder member is tiltably supported with respect to the coil member, the movable element is tilted and displaced. In this case, the guide cylinder member is tilted in accordance with the mover, so that the contact surface pressure of the mover with respect to the guide cylinder member can be reduced. As a result, the desired operating characteristics can be obtained over a long period of time by reducing or avoiding the one-side contact state of the mover with respect to the guide tube member and reducing uneven wear of the mover.

  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 automotive engine mount 10 as an active vibration isolator 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 18 elastically connected by the interposed main rubber elastic body 16 is configured to be fitted into a stopper fitting 20. 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. Further, an annular plate-like stopper portion 22 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 24 is integrally projected from the end portion on the large diameter side toward the upper side in the axial direction, and a fixing screw hole 26 that opens to the upper end surface is formed in the fixed shaft 24. 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 26.

  On the other hand, the second mounting bracket 14 has a large-diameter, generally cylindrical shape. In addition, a step portion 28 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 30 across the step portion 28, while the lower side in the axial direction is The small diameter portion 32 is used. Note that a thin seal rubber layer 34 is formed on the inner peripheral surface of the large diameter portion 30. Further, a diaphragm 36 made of a thin rubber film as a flexible film is disposed in the vicinity of the lower opening end of the small-diameter portion 32, and the outer peripheral edge of the diaphragm 36 is the second mounting bracket 14. By being vulcanized and bonded to the inner peripheral surface of the small-diameter portion 32, the lower opening in the axial direction of the second mounting bracket 14 is covered with a fluid-tight cover. Further, a connecting metal fitting 38 is vulcanized and bonded to the central portion of the diaphragm 36.

  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 concave surface 40 is formed on the end surface 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 22 of the first mounting bracket 12 is superimposed on the end surface on the small diameter side of the main rubber elastic body 16 and is vulcanized and bonded so as to be covered with the main rubber elastic body 16. The contact rubber 42 protruding upward from the main rubber elastic body 16 is formed integrally with the main rubber elastic body 16, and a concave groove 44 is formed inside the contact rubber 42. A connecting sleeve 46 is vulcanized and bonded to the outer peripheral surface of the main rubber elastic body 16 on the large diameter side.

  The connecting sleeve 46 vulcanized and bonded to the large-diameter outer peripheral surface of the main rubber elastic body 16 is fitted into the large-diameter portion 30 of the second mounting bracket 14 so that the large-diameter portion 30 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. A liquid chamber 48 is formed between the opposing surfaces of the diaphragm 16 and the diaphragm 36 as a sealed region that is fluid-tightly blocked from the external space, and an incompressible fluid is sealed in the liquid chamber 48.

  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 50 and an orifice member 52 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 36.

  The partition member 50 has a support rubber elastic body 54 that spreads with a predetermined thickness, and a vibration plate 56 as a vibration member is vulcanized and bonded to a central portion of the support rubber elastic body 54. The vibration plate 56 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 54. In addition, on the upper part of the vibration plate 56, a buffer portion 58 is formed in which the support rubber elastic body 54 wraps around and becomes thick.

  Further, an annular outer peripheral metal fitting 60 is vulcanized and bonded to the outer peripheral edge of the support rubber elastic body 54, and a peripheral groove 62 extending in a circumferential direction with a predetermined length is formed on the outer peripheral metal fitting 60. ing. And the axial direction upper side opening part of this outer periphery metal fitting 60 is made into the flange-like part 64 which spreads to radial direction outward, the flange-like part 64 is overlapped with the step part 28 of the 2nd attachment metal fitting 14, and a step part 28 and the connecting sleeve 46 are clamped and fixed. As a result, the partition member 50 is disposed so as to extend in the direction perpendicular to the axis at an intermediate portion between the opposing surfaces of the main rubber elastic body 16 and the diaphragm 36, 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 50, a vibration action in which a part of the wall portion is constituted by the main rubber elastic body 16 and pressure fluctuations are generated due to elastic deformation of the main rubber elastic body 16 at the time of vibration input. A working fluid chamber 66 is formed as a chamber. On the other hand, on the lower side of the partition member 50, an equilibrium chamber 68 is formed in which a part of the wall portion is constituted by the diaphragm 36 and volume change is easily allowed.

  In addition, the orifice member 52 is configured by overlapping the upper and lower thin plates 53 a and 53 b with each other, and the outer peripheral edge portion thereof is overlapped with the flange-like portion 64 of the outer peripheral metal fitting 60. By being sandwiched between the inner peripheral edge of the large-diameter side end of the main rubber elastic body 16, it is fixedly supported by the second mounting bracket 14 via the outer peripheral bracket 60. As a result, the orifice member 52 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 50, and the working fluid chamber 66 is divided into two sides in the axial direction. Yes. Therefore, a pressure receiving chamber 70 in which a part of the wall portion is formed of the main rubber elastic body 16 is formed above the orifice member 52. On the other hand, on the lower side of the orifice member 52, a vibration chamber 72 having a wall portion partially constituted by a vibration plate 56 is formed.

  Further, a circumferential passage 74 extending continuously in the circumferential direction between the overlapping surfaces of the upper and lower thin plates 53a and 53b is formed in the outer peripheral edge portion of the orifice member 52. One end of the circumferential passage 74 is connected to the pressure receiving chamber 70, and the other end is connected to the excitation chamber 72. Thus, a first orifice passage 76 that allows the pressure receiving chamber 70 and the vibration chamber 72 to communicate with each other is formed. The first orifice passage 76 is tuned to a medium frequency range such as idling vibration of about 30 to 40 Hz.

  Furthermore, the outer peripheral edge portion of the orifice member 52 is overlapped with the outer peripheral edge portion of the partition member 50, and the second orifice is formed by covering the peripheral groove 62 formed in the outer peripheral edge portion of the outer peripheral metal fitting 60. A passage 78 is formed. The second orifice passage 78 has one end connected to the pressure receiving chamber 70 through the vibration chamber 72 and the first orifice passage 76, and the other end connected to the equilibrium chamber 68. As a result, a second orifice passage 78 that allows the pressure receiving chamber 70 and the equilibrium chamber 68 to communicate with each other is formed. The second orifice passage 78 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 aspects, for example, the pressure receiving chamber 70 and the excitation chamber 72 are directly passed through the central portion of the orifice member 52. 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 74 and the outer periphery of the orifice member 52 The second orifice passage may be formed by directly connecting the peripheral grooves 62 of the metal fitting 60 in series.

  Further, the mount body 18 having the above-described structure has the second mounting bracket 14 fitted into the stopper bracket 20 and is attached to the body of the automobile (not shown) via the stopper bracket 20. Yes.

  The stopper metal fitting 20 has a large-diameter stepped cylindrical shape, the lower side of which has a larger diameter than the upper side, and the mount main body 18 is inserted from the lower side opening so that the locking step 80 It is locked by press fitting. On the other hand, a contact portion 82 extending inward is formed in the upper opening, and the stopper portion 22 of the first mounting bracket 12 contacts the contact portion 82 via a contact rubber 42. The stopper function in the rebound direction is exhibited. An insertion hole 84 is provided in the contact portion 82 so that an appropriate gap is maintained between the first mounting bracket 12 and the fixed shaft 24, and the first mounting bracket 12 is perpendicular to the axis. Relative displacement is allowed. In addition, a collar member 86 on the umbrella that extends so as to cover the insertion hole 84 of the stopper fitting 20 is attached to the fixed shaft 24 of the first attachment fitting 12.

  The second mounting bracket 14 fitted in the stopper fitting 20 is locked by the locking step portion 80 of the stopper fitting 20 and is press-fitted and fixed so that it cannot be pulled out. Further, a plurality of leg portions 88 projecting on the outer peripheral surface and extending downward are fixed to the stopper fitting 20, and these leg portions 88 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 18, the vibration plate 56 provided on the partition member 50 is overlapped and fixed in close contact with the connection fitting 38 provided on the diaphragm 36. Then, a drive rod 90 as an inner rod is fixed to the vibration plate 56 and the connection fitting 38, and the drive rod 90 is protruded downward in the axial direction from the vibration plate 56 and the connection fitting 38.

  Note that the connecting metal 38 is provided with a sandwich rubber layer 92 formed integrally with the diaphragm 36 over substantially the entire circumference, so that the space between the overlapping surface with the vibration plate 56 is fluid. It is tightly sealed. Further, the vibration plate 56 and the coupling fitting 38 are overlapped at each upper bottom portion in the center, and a caulking portion 94 formed integrally with the upper end portion of the drive rod 90 is inserted through these central portions. The vibration plate 56 and the coupling fitting 38 are caulked and fixed in close contact by the caulking portion 94, and the drive rod 90 penetrates the coupling fitting 38 from the vibration plate 56 and extends outward in the axial direction. The vibration plate 56 and the coupling fitting 38 are integrated with each other, and a recess 96 that opens toward the armature 140 described later is formed. Further, in the vicinity of the peripheral wall portion 98 of the recess 96, a buffer rubber portion 100 is integrally formed with the diaphragm 36 so as to cover the peripheral wall portion 98.

  Further, an axially lower side of the second mounting bracket 14 from which the drive rod 90 is projected, that is, on the side opposite to the working fluid chamber 66 with the vibration plate 56 and the coupling bracket 38 interposed therebetween, is a vibration-proof actuator. An electromagnetic vibrator 102 is disposed and supported by the second mounting bracket 14.

  FIG. 2 shows a cross-sectional view of the electromagnetic exciter 102, and FIG. 3 shows a plan view. The electromagnetic exciter 102 includes a solenoid coil 104 as a coil member, and a yoke member made of a ferromagnetic material extending substantially over the entire circumference in a U-shaped cross-section so as to surround the outer peripheral surface and upper and lower end surfaces of the solenoid coil 104. A yoke 106 is included. The solenoid coil 104 and the yoke 106 constitute a stator in which a fixed magnetic path is formed in coil electromagnetic conduction, and a solenoid actuator is constituted by the stator and an armature 140 described later.

  More specifically, the solenoid coil 104 is provided so that a cover member 112 made of a nonmagnetic material covers the outer periphery of the coil 110 with respect to the coil 110 wound around the bobbin 108 made of a nonmagnetic material. . The bobbin 108 has a substantially cylindrical shape in which the vicinity of both end portions in the axial direction spreads in a flange shape, and a through hole penetrating in the axial direction at the center is a central hole 114 of the solenoid coil 104. The cover member 112 is resin-molded after the coil 110 is wound around the bobbin 108, for example. Further, the cover member 112 is integrally formed with a power supply port 116 that protrudes to the outside from an opening formed through the yoke 106, and power is supplied to the coil 110 through a terminal provided inside the power supply port 116. It comes to be supplied.

  On the other hand, the yoke member 106 has an upper yoke 106a disposed so as to cover the upper portion of the solenoid coil 104, and a lower portion extending in an L-shaped cross section so as to surround the outer peripheral surface and the lower end surface of the solenoid coil 104. The yoke 106b is configured. The solenoid coil 104 is disposed so as to cover the solenoid coil 104 in a state where the outer peripheral side end portion of the upper yoke 106a and the upper end portion of the lower yoke 106b are in contact with each other, and the solenoid coil 104 is energized by these upper yoke 106a and lower yoke 106b. The fixed-side magnetic path through which the magnetic flux generated by the flow is configured. As a result, the inner peripheral side edge portions of the upper through hole 118 and the lower through hole 120 penetrating through the central portions of the upper yoke 106a and the lower yoke 106b are respectively formed as the upper magnetic pole 122 and the lower magnetic pole 124, and the coil Magnetic poles are formed in the electromagnetic field to 110. The inner diameter of the upper through hole 118 and the lower through hole 120 is slightly smaller than the inner diameter of the center hole 114 of the solenoid coil 104, and the upper magnetic pole 122 and the lower magnetic pole 124 are slightly inward from the center hole 114. It is made to protrude.

  In the center hole 114 of the solenoid coil 104, a guide sleeve 126 as a guide cylinder member is arranged so as to cover the upper and lower inner peripheral edge openings formed by the upper yoke 106a and the lower yoke 106b. It is installed. The guide sleeve 126 has an outer diameter that is slightly smaller than the inner diameter of the center hole 114 of the solenoid coil 104, and a cylindrical guide as a smooth guide inner surface having an inner diameter that slightly protrudes from the inner surface of the magnetic pole of the lower through hole 120. It has a cylindrical shape having a surface 128.

  The material of the guide sleeve 126 is not limited as long as it is a non-magnetic material, but a low-friction material is preferably employed in order to obtain a smooth guiding action. Furthermore, since the inside of the central hole 114 of the solenoid coil 104 is likely to be in a high temperature state due to heat generated by energization of the coil 110, a material having excellent heat resistance that is less likely to be deformed even when exposed to a high temperature state is more preferable. Used for. For example, nonmagnetic metal materials such as stainless steel, aluminum, titanium, copper, and nickel, and resin materials such as polyethylene, polytetrafluoroethylene, nylon 66, and phenol resin can be suitably employed.

  On the other hand, an engagement groove 130 is formed on the outer peripheral edge of the yoke 106 (lower yoke 106b) disposed so as to cover the solenoid coil 104. 14 is fitted and locked so that the electromagnetic exciter 102 is attached so as to cover the lower end opening of the second mounting bracket 14. Yes. As described above, in the present embodiment, the yoke 106 is the housing 134 that fixedly supports the solenoid coil 104 in the accommodated state, and the electromagnetic exciter 102 is not connected via a separate member such as a bracket. Since it is directly fixed to the second mounting bracket 14, the positional deviation during assembly of the vibration plate 56 and the central axis of the coil 110 is reduced. In addition, between the yoke 106 of the electromagnetic exciter 102 and the second mounting bracket 14, a pressing rubber 136 formed by a diaphragm 36 extending downward is sandwiched, so that the electromagnetic excitation is performed. The backlash of the vessel 102 is prevented. As a result, the central axis of the coil 110 is substantially aligned with the central axis of the mount body 18 and is aligned with the central axes of the second mounting bracket 14 and the vibration plate 56. Also, a lid member 138 is bolted below the housing 134 to prevent dust and the like from entering the lower through hole 120. Note that a cushioning rubber may be provided at a portion facing the lid member 138 and the lower end surface of the armature 140 so that the armature 140 abuts the lid member 138 in a buffering manner.

  An armature 140 as a mover is assembled in the upper and lower through holes 118 and 120 of the housing 134 in which the solenoid coil 104 is assembled. The armature 140 is formed of a generally circular block-shaped ferromagnetic material as a whole, has an outer diameter slightly smaller than the inner diameter of the guide sleeve 126, and is inserted into the guide sleeve 126 so as to be inserted into the coil 110. It is assembled so as to be capable of relative displacement in the axial direction on substantially the same central axis.

  More specifically, the armature 140 has an axial length dimension extending over the upper and lower magnetic poles 122 and 124, and a peripheral groove 142 that opens on the outer peripheral surface is formed near the upper magnetic pole 122. ing. The upper end portion and the lower end portion in the axial direction of the armature 140 serve as a magnetic force acting portion. For example, as shown in the figure, the upper end edge portion of the circumferential groove 142 of the armature 140 and the upper magnetic pole 122 of the upper yoke 106a. A magnetic gap in which an effective magnetic attractive force is applied is formed between the lower end edge in the axial direction of the armature 140 and the lower magnetic pole 124 of the lower yoke 106b. . In addition, the outer peripheral surface of the armature 140 is subjected to low friction treatment and rust prevention treatment with various known surface treatment agents.

  As shown in FIG. 4, the guide sleeve 126 into which the armature 140 is inserted has notches 144 and 146 formed along the entire circumference with respect to the outer peripheral edge portions at both ends in the axial direction. O-rings 148 and 150 as elastic support members are interposed between the notches 144 and 146 and the upper yoke 106a and the lower yoke 106b. As a result, the guide sleeve 126 is separated from the solenoid coil 104 and the yoke 106 with a predetermined gap in both the radial direction with respect to the central hole 114 of the solenoid coil 104 and the axial direction with respect to the upper yoke 106a and the lower yoke 106b. And is elastically positioned and supported. The O-rings 148 and 150 are elastically deformed, so that the guide sleeve 126 can be relatively displaced with respect to the solenoid coil 104 and the yoke 106 within the gap, and the central axis of the guide sleeve 126 is the solenoid coil 104. The center hole 114 can be tilted and displaced relative to the axial direction. As is clear from this, tilting support means for tiltably supporting the guide sleeve 126 with respect to the solenoid coil 104 is configured by these O-rings 148 and 150, and component tolerances, assembly errors, or support rubber elastic bodies are formed. Even when the armature 140 is tilted due to irregular elastic deformation of 54, the guide sleeve 126 can be tilted and displaced in accordance with the tilt of the armature 140.

  Note that the allowable value of the tilt angle: α of the guide sleeve 126 is a specific shape such as the solenoid coil 104, the guide sleeve 126, and the armature 140, the radial clearance between the guide sleeve 126 and the solenoid coil 104, the solenoid coil 104, The armature 140 can be appropriately set according to the size (particularly the axial dimension) of the armature 140, but in order to follow the inclination of the armature 140 as much as possible, for example, as an automobile engine mount as in the present embodiment. In the case of a general structure that is adopted, it is desirable that tilting of 0.05 degrees or more with respect to the central axis of the solenoid coil 104 is allowed, and more preferably 0.1 degrees or more is allowed. It is preferable. On the other hand, it is desirable that the allowable amount of the tilt angle: α is such that the armature 140 does not interfere with the solenoid coil 104 or the yoke 106, and is 0.3 ° or less with respect to the central axis of the solenoid coil 104. It is preferably set to 0.15 degrees or less.

  Further, the armature 140 is formed with an insertion hole 152 as a through hole penetrating the central axis. An inward projecting portion 154 as a connecting portion projecting inward is formed slightly above the axial center portion of the insertion hole 152, and the upper side in the axial direction has a small diameter across the inward projecting portion 154. The lower portion in the axial direction is a large-diameter portion 158.

  The drive rod 90 is inserted into the insertion hole 152 of the armature 140 in a loosely inserted state with a gap, and the lower end portion of the drive rod 90 protrudes downward from the inward protruding portion 154 of the armature 140. . An annular support member 160 having an outer diameter that is slightly larger than the inner diameter of the inward protrusion 154 is externally inserted at the protruding lower end of the drive rod 90, and is screwed to the tip of the drive rod 90. The bolt 162 is supported so that it cannot be pulled out of the drive rod 90. The support member 160 is locked from the lower surface with respect to the inward projecting portion 154 of the armature 140, so that the armature 140 is locked so as not to be able to be pulled out downward from the support member 160 in the axial direction.

  Further, an annular pressing member 164 having an outer diameter larger than the inner diameter of the inner protrusion 154 is extrapolated on the opposite side of the support member 160 across the inner protrusion 154 in the drive rod 90. The holding member 164 is overlaid on the upper surface of the inward projecting portion 154. Further, the pressing member 164 is elastically deformed by a rubber ring 168 externally inserted into the driving rod 90 in a state of being sandwiched between a step surface 166 formed at an intermediate portion in the axial direction of the driving rod 90 and the upper surface of the pressing member 164. A downward biasing force is exerted in the axial direction.

  In this way, the pressing member 164 and the support member 160 are overlapped from above and below with respect to the inward projecting portion 154 of the armature 140 and are held in contact with each other, and the armature 140 is fixedly positioned in the axial direction. . Thus, the driving rod 90 and the armature 140 are connected in a substantially fixed state by the elasticity of the rubber ring 168 so that the driving force applied to the armature 140 is applied to the driving rod 90 by energization of the coil 110. It has become. The armature 140 and the vibration plate 56 are connected via the drive rod 90, so that the vibration plate 56 serves as an output member of the electromagnetic vibrator 102 as a vibration-proof actuator.

  Further, a predetermined gap is formed between the support member 160, the pressing member 164, the drive rod 90, and the axially opposed surfaces of the inner peripheral surface of the armature 140. Then, by adjusting the tightening force of the rubber ring 168 on the inward projecting portion 154, an external force in the axial direction exceeding the static friction force generated between the support member 160 and the pressing member 164 and the inward projecting portion 154 is generated. When applied to the armature 140, relative sliding displacement in the direction perpendicular to the axis of the armature 140 with respect to the drive rod 90 is allowed, and the inwardly projecting portion 154, the support member 160, and the pressing member 164 are allowed. The rubber ring 168 constitutes a relative displacement allowable connecting means for connecting the armature 140 and the drive rod 90 so as to allow relative displacement in the axial direction. Thereby, the relative displacement between the drive rod 90 and the armature 140 due to a dimensional error in manufacturing of each member, a positioning error at the time of assembling, and the like can be advantageously absorbed. On the other hand, positioning can be performed stably in the direction perpendicular to the axis, and a temporary shaft misalignment during operation of the actuator is advantageously absorbed, so that stable operating characteristics can be obtained.

  It should be noted that the relative displacement amount of the armature 140 with respect to the drive rod 90 in the direction perpendicular to the axis is between the support member 160, the pressing member 164 or the outer peripheral edge of the drive rod 90 and the axially opposed surface between the inner peripheral surface of the armature 140. Although it is defined by the distance, a range of 0.2 mm to 3 mm is suitably employed as the allowable displacement amount. Further, in order to better realize the sliding displacement of the armature 140, for example, a sliding member made of a low friction material such as polyethylene or polytetrafluoroethylene is incorporated in these sliding surfaces, or a low friction treatment is performed. May be.

  Although not shown, the engine mount 10 having the above-described structure can control the energization of the coil 110. 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, a magnetic force is applied to the armature 140 to vibrate and drive downward in the axial direction, and the energization of the coil 110 is stopped and the restoring force of the supporting rubber elastic body 54 is applied to the vibration plate 56. Thus, a driving force corresponding to the vibration to be vibrated can be applied, so that an active vibration isolating effect by controlling the internal pressure of the working fluid chamber 66 can be obtained.

  Therefore, in the engine mount 10 of the present embodiment, when the armature 140 is tilted due to component tolerance, assembly error, or tilt of the vibration plate 56 due to irregular elastic deformation of the support rubber elastic body 54. In addition, the guide sleeve 126 can be tilted in accordance with the tilt displacement of the armature 140 by elastic deformation of the O-rings 148 and 150. As a result, the contact surface pressure of the armature 140 with respect to the guide sleeve 126 is reduced, and uneven wear due to the one-sided contact state of the armature 140 is reduced, so that the armature 140 is guided in a desired driving direction while being applied to the armature 140. It is possible to maintain the sliding characteristics and rust prevention characteristics due to the surface treatment over a long period of time.

  Further, particularly in the present embodiment, the both ends in the axial direction of the cylindrical guide surface 128 of the guide sleeve 126 are chamfered to increase in diameter outward in the axial direction, and the armature 140, the guide sleeve 126, and the like. Even when a relative tilt displacement occurs between the two, the occurrence of wear and noise due to galling is reduced. Further, the upper notch 144 and the lower notch 146 in contact with the O-rings 148 and 150 of the guide sleeve 126 are smoothly chamfered so that the O-rings 148 and 150 can be prevented from being damaged. Has been.

  In addition, in the present embodiment, since the relative displacement in the direction perpendicular to the axis of the drive rod 90 and the armature 140 is enabled by the support member 160 and the pressing member 164 as the relative displacement permissible connecting means, the vibration plate Even when a relative positional deviation occurs between the armature 140 and the driving rod 90 due to a temporary inclination or an assembly error of 56, the positional deviation is absorbed by the relative displacement permissible connecting means, and the driving rod The influence on 90 is avoided or reduced, and more stable axial excitation drive is possible.

  As mentioned above, although one Embodiment of this invention has been illustrated, various aspects are employable as a specific aspect of a tilting support means. Below, some preferable structures as a solenoid type actuator provided with a tilting support means will be exemplified, but the tilting support means in the present invention is not limited to the following modes. In the solenoid type actuator described below, members and parts having the same structure as those of the first embodiment described above are denoted by the same reference numerals as those of the first embodiment. Therefore, detailed description thereof will be omitted.

  First, FIG. 5 shows an electromagnetic exciter 180 as a second embodiment. In the present embodiment, a support protrusion 182 that extends over the entire circumference is formed integrally with the guide sleeve 126 at a substantially central portion in the axial direction of the guide sleeve 126. The support protrusion 182 is brought into contact with the center hole 114 of the bobbin 108 which is the inner peripheral surface of the coil member. According to such an aspect, the guide sleeve 126 is tilted about the support protrusion 182 as a fulcrum, and a stable tilting operation can be performed. Furthermore, in this embodiment, since the guide sleeve 126 is elastically supported via the O-rings 148 and 150, the transmission of the hitting sound and vibration to the yoke 106 is reduced. Note that the support protrusions 182 do not necessarily have to be continuous over the entire circumference of the guide sleeve 126, and may be formed separately from each other at a predetermined interval in the circumferential direction. It may be formed as a separate body without being formed.

  Next, FIG. 6 shows an electromagnetic exciter 190 as a third embodiment. In the present embodiment, an elastic sleeve 192 as a shock absorbing rubber sleeve is disposed between the radially opposing surfaces of the guide sleeve 126 and the center hole 114 of the bobbin 108. The elastic sleeve 192 has a substantially cylindrical shape having an axial dimension slightly larger than that of the guide sleeve 126, and O-rings 194 and 196 are integrally formed at both ends in the axial direction. The elastic sleeve 192 is inserted into the central hole 114 of the bobbin 108 so as to enclose the guide sleeve 126, so that the guide sleeve 126 is elastic with respect to the yoke 106 and the coil 110 via the elastic sleeve 192. It is supported by. According to such an embodiment, since the elastic sleeve 192 is disposed over substantially the entire outer peripheral surface of the guide sleeve 126, the guide sleeve 126 can be stably supported and the armature 140 can be added. It is also possible to advantageously absorb vibrations caused by vibration drive.

  FIG. 7 shows an electromagnetic exciter 200 as a fourth embodiment. In the electromagnetic exciter 200, the fitting convex surfaces 204 formed on the guide sleeve 126 are fitted to the supporting concave surfaces 202 formed at both end portions in the axial direction of the center hole 114 of the bobbin 108. The fitting convex surface 204 is slidable on a spherical surface. The support concave surface 202 has a spherical shape with the center of curvature of the central hole 114 of the bobbin 108 as the center of curvature, and the fitting convex surface 204 has a shape corresponding to the support concave surface 202 and is integrally formed on the outer peripheral surface of the guide sleeve 126. Is formed. According to such an aspect, a more stable tilting operation can be performed by the guiding action of the support concave surface 202 and the fitting convex surface 204.

  As mentioned above, although embodiment of this invention was explained in full detail, these are illustrations to the last, Comprising: This invention is not limited at all by the specific description in this embodiment.

  For example, the elastic support member is not limited to the O-ring, and a rubber sleeve such as the elastic sleeve 192 described above may be used, or a disc spring or the like may be used. Furthermore, the elastic support member does not need to be provided over the entire circumference of the guide sleeve 126, and may be provided separately at a predetermined interval.

  In addition to the O-rings 148, 150, 194, and 196, like the electromagnetic vibrators 180, 190, and 200 as the second to fourth embodiments, the support protrusion 182 and the elastic sleeve 192 are provided as tilting support means, respectively. When the support concave surface 202 and the fitting convex surface 204 are provided, these O-rings 148, 150, 194, 196 are not necessarily required.

  Further, the specific shapes of the armature 140 and the upper and lower yokes 106a and 106b in the electromagnetic vibrator 102 are not limited in any way. For example, the lower end portion of the lower yoke 106b in the above-described embodiment extends further inward. Thus, a magnetic pole may be formed between the lower end portion of the armature 140 by forming a magnetic pole in the inwardly extending portion.

  Further, the specific aspect of the relative displacement allowable connecting means for allowing the relative displacement in the axial direction between the armature 140 and the drive rod 90 is not limited to the above-described aspect. For example, by using a coil spring instead of the rubber ring 168 and disposing it in a compressed state between the stepped surface 166 of the drive rod 90 and the upper end surface of the pressing member 164, the armature 140 is more positively supported. The coil spring may be arranged in a compressed state between the stepped surface 166 of the drive rod 90 and the upper end surface of the inward protruding portion 154 of the armature 140 without using the pressing member 164. You may install. Further, as a means for supporting the armature 140 so as not to be able to come out from the driving rod 90 in the axial direction downward, for example, a male screw is formed at the tip portion of the driving rod 90 and an outer diameter such as the supporting member 160 is used instead of the supporting member 160. It is also possible to support the armature 140 by screwing a nut member having a size.

  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.

  For example, as an active vibration damper to which the present invention is applied, specifically, as an attachment portion made of a metal plate or the like on the opening side of the housing 134 in the electromagnetic vibrator 102 shown in the above-described embodiment. A housing that includes the coil 110 while elastically connecting the vibration plate and connecting the vibration plate and the armature 140 while the vibration plate is fixedly attached to a vibration member to be controlled as an attachment portion. The housing 134 including the coil 110 can be made to act as a mass that is actively excited to the vibrating member by energizing the coil 110 by elastically coupling and supporting the 134 to the vibrating member. .

  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 longitudinal cross-sectional view which shows the electromagnetic vibrator used for the engine mount shown in FIG. FIG. 3 is a plan view showing the electromagnetic vibrator shown in FIG. 2. It is a principal part enlarged view of the electromagnetic exciter shown in FIG. It is a longitudinal cross-sectional view which shows the electromagnetic vibrator as 2nd embodiment in this invention. It is a longitudinal cross-sectional view which shows the electromagnetic vibrator as 3rd embodiment in this invention. It is a longitudinal cross-sectional view which shows the electromagnetic vibrator as 4th embodiment in 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 56 Excitation board 68 Equilibrium chamber 70 Pressure receiving chamber 72 Excitation chamber 90 Drive rod 102 Electromagnetic exciter 104 Solenoid coil 106 Yoke 108 Bobbin 110 Coil 114 Center hole 126 Guide sleeve 134 Housing 140 Armature 148 O-ring 150 O-ring 152 Insertion hole 160 Support member 164 Holding member 180 Electromagnetic exciter 182 Support protrusion 190 Electromagnetic exciter 192 Elastic sleeve 194 O-ring 196 O-ring 200 Electromagnetic exciter 202 Support concave surface 204 Fitting convex surface

Claims (9)

A yoke member is assembled around the coil member to form a fixed-side magnetic path, and a mover is disposed in the central hole of the coil member, and the mover is acted upon by a magnetic field generated by energization of the coil member. In a solenoid type actuator assembled with a guide cylinder member having a cylindrical guide inner surface for guiding the outer peripheral surface of the mover in the axial direction of the coil member,
A solenoid type actuator provided with a tilting support means for tiltably supporting the guide cylinder member with respect to the coil member.   The guide cylinder member is inserted and arranged with a predetermined gap in the radial direction with respect to the central hole of the coil member, and the guide cylinder member and the coil member and / or at both axial ends of the guide cylinder member By disposing an elastic support member between the yoke member and elastically positioning and supporting the guide tube member with respect to the coil member in the axial direction and the direction perpendicular to the axis via the elastic support member. The solenoid actuator according to claim 1, wherein the tilt support means is configured.   The guide cylinder member is inserted and arranged with a predetermined gap in the radial direction with respect to the central hole of the coil member, and a support protrusion that protrudes on the outer peripheral surface is provided at a central portion in the axial direction of the guide cylinder member. In addition, by allowing the projecting tip of the support protrusion to abut on the inner peripheral surface of the coil member, the guide cylinder member can be tilted with the contact point of the support protrusion as a fulcrum. The solenoid actuator according to claim 1 or 2, wherein the tilt support means is configured.   The tilting support means is provided by disposing a buffer rubber sleeve between the radially opposed surfaces of the guide cylinder member and the central hole of the coil member and elastically supporting the guide cylinder member via the buffer rubber sleeve. The solenoid type actuator according to any one of claims 1 to 3, wherein the actuator is configured.   A spherical supporting concave surface having a center of curvature at the substantially central portion of the central hole is formed at both axial end portions of the central hole of the coil member, while at the axial end portions of the outer peripheral surface of the guide cylinder member, 3. The tilting support means is configured by forming a spherical fitting convex surface corresponding to the supporting concave surface, and fitting the fitting convex surface to the supporting concave surface so as to be slidable in a spherical manner. Solenoid type actuator. An anti-vibration actuator that drives the output member, which is spaced apart so as to be reciprocally displaceable in the axial direction, to vibrate in response to vibration to be vibrated,
The solenoid type actuator according to any one of claims 1 to 5, wherein the output member is connected to the mover of the solenoid type actuator, and the coil is provided for the coil member. An anti-vibration actuator characterized in that the output member is driven to vibrate by applying a driving voltage having a frequency component corresponding to vibration to drive the mover in the axial direction. The main rubber elastic body connects the first mounting member attached to one member constituting the vibration transmission system by being connected to each other and the second mounting member attached to the other member by the main rubber elastic body. A part of the wall portion is formed by the body to form a pressure receiving chamber in which the incompressible fluid is sealed, and another part of the wall portion of the pressure receiving chamber is configured by a vibration member, and the vibration member In an active vibration isolator provided with an actuator that exerts an excitation force and actively controlling the pressure of the pressure receiving chamber by driving the excitation member with the actuator.
The vibration-proof actuator according to claim 6 is used as the actuator, and a housing that fixedly supports the coil member in a substantially housed state is fixed to the second mounting member, while the vibration-proof member is fixed to the vibration-proof member. An active type vibration isolating apparatus, wherein the vibration isolation actuator is driven to vibrate by being coupled to the movable element as the output member of the actuator for a motor.   A through-hole penetrating in the axial direction is provided in the mover so that the inner rod protruding from the vibration member is inserted into the through-hole, and the connecting portion provided in the mover and the inner rod are connected in the direction perpendicular to the axis. The active vibration isolator according to claim 7, further comprising a relative displacement permissible coupling means for coupling the relative displacements of the two. An active type vibration damping device that exerts an exciting force on the vibration isolation target member to exert an active vibration suppression effect by being attached to the vibration isolation target member,
An anti-vibration actuator according to claim 6, wherein an attachment portion for fixing to the anti-vibration target member is provided on one of the coil member and the mover in the anti-vibration actuator, and the coil member and the movable member are movable. An active vibration isolator having a mass provided on the other side of the child.

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