JP2005239084A - Active fluid inclusion type engine mount - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To provide an engine mount having an improved structure in which active vibration-proof effect by excitation of an excitation member is effectively exhibited relative to small amplitude vibration of middle to high frequency area such as idling vibration or the like with no problem of large size of an actuator and a flowing amount of fluid through an orifice passage is advantageously ensured relative to low frequency large amplitude vibration such as engine shake or the like, thereby, vibration-proof effect by the orifice passage can be effectively exhibited. <P>SOLUTION: The active vibration-proof effect is exhibited based on excitation displacement of the excitation member 76 by energization to a solenoid type actuator 116 at inputting of idling vibration. An elastic stopper projection part 94 projected from the excitation member 76 is abutted on an abutment member 122 at a left position outwardly form the excitation member 76 and a displacement amount of the excitation member 76 is shock-absorbingly restricted. <P>COPYRIGHT: (C)2005,JPO&NCIPI

Description

  The present invention relates to an active vibration isolator capable of exhibiting an anti-vibration effect that is positive or counterbalanced with respect to vibration to be vibrated, and in particular, one of wall portions of a pressure receiving chamber in which an incompressible fluid is sealed. The present invention relates to an active fluid-filled engine mount in which an active vibration isolating effect is obtained by controlling the pressure in a pressure receiving chamber by driving the excitation member with an actuator and controlling the pressure in the pressure receiving chamber. It is.

  Conventionally, as a kind of engine mount that allows the power unit to be supported in a vibration-proof manner on a support frame such as a body, the first mounting member is elastic with respect to one opening of the second mounting member having a cylindrical shape. And a vibration receiving member disposed in the other opening of the second mounting member and connected by a support rubber elastic body to receive pressure between the opposing surfaces of the first mounting member and the vibration member. While forming a chamber, a flexible film is disposed so as to cover the outside of the main rubber elastic body, and an equilibrium chamber is formed on the opposite side of the main pressure rubber chamber across the main rubber elastic body. 2. Description of the Related Art A fluid-filled engine mount having a structure in which an orifice passage communicating with an equilibrium chamber is provided and an electromagnetic actuator that applies a vibration force to a vibration member is mounted is known.

  In such an engine mount, the use of an electromagnetic actuator makes it possible to control the driving force exerted on the vibration member with high accuracy, and to provide an active vibration isolation effect based on the pressure control of the pressure receiving chamber. It can be obtained advantageously. In addition, a pressure receiving chamber is formed inside the main rubber elastic body, while an equilibrium chamber is formed outside the main rubber elastic body, so that the space between the opposing surfaces of the first mounting member and the second mounting member It is possible to keep the distance small, especially in the active fluid-filled engine mount, where the mount size is likely to be a problem for assembling electromagnetic actuators. There is an advantage that the elastic center can be lowered.

  By the way, in an engine mount for automobiles, a high damping effect is required for low-frequency large-amplitude vibrations such as engine shakes, while low-dynamic springs are used for medium to high-frequency small-amplitude vibrations such as idling. Vibration isolation effect due to characteristics is required.

  Therefore, conventionally, in general, the orifice passage that connects the pressure receiving chamber and the equilibrium chamber is tuned to a low frequency range corresponding to an engine shake to obtain a high damping effect, while in the middle to high frequency range such as idling vibration. A low dynamic spring characteristic is realized by an active vibration isolation effect by exciting the vibration plate with an electromagnetic actuator.

  However, in the active fluid-filled engine mount having the conventional structure as described above, a part of the wall portion of the pressure receiving chamber is constituted by a support rubber elastic body that elastically supports the vibration member. Since the vibration member has a relatively soft spring characteristic so that the vibration member can be actively vibrated efficiently, the vibration member and the supporting rubber elastic body when inputting low-frequency large-amplitude vibration such as engine shake When the pressure in the pressure receiving chamber is exerted on the vibration member, the vibration member and the elastic rubber body are easily displaced or deformed. When the vibration member or the support rubber elastic body is displaced or deformed, the pressure fluctuation in the pressure receiving chamber is absorbed correspondingly, and it is difficult to secure a sufficient amount of fluid to flow through the orifice passage. There is a possibility that it is difficult to sufficiently obtain a target damping effect for low-frequency large-amplitude vibration, which is exhibited based on the fluid action of the fluid that is caused to flow in the passage.

  Note that, as described in Patent Document 1 and the like, a stopper mechanism that restricts excessive displacement of the vibration member has been proposed. However, such a conventional stopper mechanism is effective in, for example, a sudden step climbing. Therefore, the elastic member is merely protected by preventing excessive displacement of the vibration member caused by a large load exerted on the support rubber. Therefore, before such a stopper function is exhibited, the pressure fluctuation in the pressure receiving chamber is absorbed by a considerable displacement of the vibration member, so that the amount of fluid that can flow through the orifice passage should be effectively secured. There was no reduction in the vibration proofing effect against the engine shake in the low frequency range.

  In order to solve the above-described problem, Patent Document 2 discloses an active fluid-filled vibration-proof support device having a structure in which a support rubber elastic body is always in contact. However, in the structure disclosed in this prior application, the intermediate portion in the free length direction of the support rubber elastic body is directly pressed against the abutting member. With such a structure, the spring of the support rubber elastic body becomes hard. In addition, the actuator requires a large excitation force, leading to an increase in size and weight of the actuator, which may cause problems such as an increase in power consumption. Furthermore, the spring itself of the support rubber elastic body becomes large, the stroke of the vibration member becomes small, and the target active vibration isolation effect may be lowered.

JP 2000-55110 A JP 2002-340081 A

  Here, the present invention has been made in the background as described above, and the problem to be solved is a medium to high frequency range such as idling vibration without causing a problem such as enlargement of the actuator. The active vibration isolation effect due to the vibration of the vibration member is effectively exhibited against small amplitude vibrations of the engine, and the amount of fluid flow through the orifice passage is reduced against low frequency large amplitude vibrations such as engine shakes. It is an object of the present invention to provide an engine mount having an improved structure that can be advantageously secured and can effectively exhibit a vibration-proofing effect by an orifice passage.

  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)
In other words, according to the first aspect of the present invention, a first mounting member to be attached to one of a power unit and a vehicle body of an automobile is used, and a second mounting member having a substantially cylindrical shape to be attached to the other of the power unit and the vehicle body. The first mounting member and the second mounting member are connected to each other by a main rubber elastic body so that the one opening of the second mounting member is fluid-tight. The cover is covered and a vibration member is disposed in the other opening of the second attachment member, and the vibration member is connected to the second attachment member with a support rubber elastic body. The other opening of the second mounting member is fluid-tightly covered to form a pressure receiving chamber in which an incompressible fluid is sealed between the main rubber elastic body and the vibration member, while the first mounting The one opening in the member and the second mounting member A rubber elastic film extending between the edge and the outer edge of the main rubber elastic body is spaced apart from the outer edge of the main rubber elastic body so that the rubber elastic film is located on the opposite side of the pressure receiving chamber. Forming an equilibrium chamber in which a part of the wall portion is formed and enclosing the incompressible fluid, and providing an orifice passage for communicating the pressure receiving chamber and the equilibrium chamber with each other. An electromagnetic actuator is disposed on the electromagnetic actuator, the housing of the electromagnetic actuator is fixed to the second mounting member, and the output member of the electromagnetic actuator is connected to the vibration member so that the vibration member In an active fluid-filled engine mount that actively controls the pressure of the pressure receiving chamber by exerting an excitation force on the orifice, the orifice passage is tuned to the frequency range of the engine shake, An abutting member spaced apart from the material is fixedly provided with respect to the second mounting member, and an elastic stopper projecting portion projecting from the vibration member toward the corresponding contacting member is provided, and the electromagnetic In a non-energized state of the actuator, a predetermined gap is formed between the elastic stopper protrusion and the facing surface of the contact member, and when idling vibration is input, the excitation by energizing the electromagnetic actuator is performed. Active vibration isolation effect is demonstrated based on the vibration displacement of the member, and when the engine shake is input, the elastic stopper protrusion abuts on the corresponding contact member, and the displacement amount of the vibration member is limited in a buffering manner. It is characterized by being adapted.

  In the active fluid-filled engine mount structured according to this aspect, by providing an elastic stopper protrusion that protrudes from the vibration member, it is elastic when a large amplitude vibration such as an engine shake is input. The displacement of the vibrating member is suppressed by the stopper projection, and an efficient pressure fluctuation is induced in the pressure receiving chamber, whereby the flow of the incompressible fluid flowing through the orifice passage tuned to the frequency range of the engine shake. The amount is ensured effectively, and the high attenuation effect by the orifice passage is effectively exhibited. On the other hand, when a small amplitude vibration such as idling vibration is input, a gap is formed between the elastic stopper protrusion and the abutting member, so that an active vibration isolation effect due to the vibration displacement of the vibration member by the electromagnetic actuator is obtained. Is effectively exhibited without being inhibited.

(Aspect 2 of the present invention)
According to a second aspect of the present invention, in the active fluid-filled engine mount according to the first aspect, the elastic stopper protrusion is formed integrally with the support rubber elastic body. In the active fluid-filled engine mount having the structure according to this aspect, the elastic stopper protrusion is formed integrally with the support rubber elastic body, so that the elasticity of the support rubber elastic body can be effectively used, and the number of parts can be increased. In addition, an elastic stopper protrusion protruding from the vibration member can be obtained without increasing the number of assembly steps.

(Aspect 3 of the present invention)
According to a third aspect of the present invention, in the active fluid-filled engine mount according to the first or second aspect, the contact member is formed by the electromagnetic actuator. In the active fluid-filled engine mount structured according to this aspect, it is not necessary to prepare a separate abutting member. Therefore, the number of parts and assembly man-hours can be reduced, and the engine mount including the electromagnetic actuator can be reduced. An increase in the axial size can be avoided.

(Aspect 4 of the present invention)
According to a fourth aspect of the present invention, in the active fluid-filled engine mount according to any one of the first to third aspects, the elastic stopper protrusion and the contact member are in a non-energized state with respect to the electromagnetic actuator. The size of the gap between the opposing surfaces of the T is such that 0 <T ≦ 2.0 mm. By setting such a gap size, it is possible to effectively realize both high vibration-proof performance against engine shake and idling vibration in a general automobile engine mount.

  As is apparent from the above description, in the active fluid-filled engine mount having the structure according to the present invention, an elastic stopper portion protruding from the vibration member is provided, and the elastic stopper is provided when the electromagnetic actuator is not energized. By forming a predetermined gap between the protrusion and the abutting member, it is possible to prevent low-amplitude vibration in the middle to high frequency range such as idling vibration without causing problems such as an increase in the size of the actuator. This effectively suppresses the vibration of the vibrating member and the deformation of the supporting rubber elastic body against low-frequency, large-amplitude vibrations such as engine shake, while effectively demonstrating the active vibration isolation effect of the vibrating member. Therefore, the flow rate of the incompressible fluid flowing through the orifice passage tuned to the frequency range of the engine shake is advantageously secured, and the vibration isolation effect by the orifice passage is effectively exhibited. Rukoto is to become possible.

  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 has a structure in which a first mounting bracket 12 as a first mounting member and a second mounting bracket 14 as a second mounting member are elastically connected by a main rubber elastic body 16. The first mounting bracket 12 is attached to a power unit of an automobile (not shown), while the second mounting bracket 14 is attached to a body of an automobile (not shown), thereby supporting the power unit against vibration against the body. ing. Also, under such a mounted state, between the first mounting bracket 12 and the second mounting bracket 14, the shared load of the power unit and the main vibration to be damped are both substantially shafts of the engine mount 10. It is input in the direction (vertical direction in FIG. 1). In the following description, in principle, the vertical direction refers to the vertical direction in FIG.

  More specifically, the first mounting bracket 12 is constituted by a main rubber inner fitting 18 and a diaphragm inner fitting 20, and the second mounting fitting 14 is constituted by a main rubber outer barrel fitting 22 and a diaphragm outer barrel fitting 24. Has been. The main rubber inner metal fitting 18 and the main rubber outer cylinder fitting 22 are vulcanized and bonded to the main rubber elastic body 16 to form a first integral vulcanized molded product 28, while the diaphragm inner metal fitting 20 and the diaphragm outer cylinder fitting are made. 24 is vulcanized and bonded to a diaphragm 30 as a rubber elastic film to form a second integral vulcanized molded product 32. The first and second integral vulcanized molded products 28 and 32 are mutually connected. It is combined.

  Here, the main rubber inner metal fitting 18 constituting the first integrally vulcanized molded product 28 has a substantially truncated cone shape in the reverse direction. In addition, a fitting recess 34 is formed on the upper end surface (large-diameter side end surface) of the main rubber inner metal fitting 18, and a screw hole 36 is formed in the bottom surface of the fitting recess 34.

  Furthermore, the main rubber outer tubular fitting 22 includes a tubular wall portion 38 having a substantially large-diameter cylindrical shape, and a flange-shaped portion 40 that expands radially outward at the lower end portion in the axial direction of the tubular wall portion 38. Are integrally formed, and the upper end portion in the axial direction of the cylindrical wall portion 38 is a tapered cylindrical portion 42 that gradually expands as it goes upward in the axial direction. Thus, a circumferential groove 45 is formed on the outer peripheral side of the main rubber outer tube fitting 22 so as to open to the outer peripheral surface and extend in the circumferential direction with a length of a little less than one round. Further, the main rubber inner metal fitting 18 is spaced apart on the substantially same central axis so as to be spaced above the main rubber outer cylinder fitting 22, and the reverse outer tapered outer surface of the main rubber inner metal fitting 18 and the taper in the main rubber outer cylinder fitting 22. The inner peripheral surface of the cylindrical portion 42 is spaced from and opposed to each other, and the opposing surfaces of the main rubber inner metal fitting 18 and the main rubber outer cylinder metal fitting 22 are elastically connected by the main rubber elastic body 16. ing.

  The main rubber elastic body 16 has a large-diameter frustum shape as a whole, and a main rubber inner metal fitting 18 is coaxially arranged and vulcanized and bonded to the central portion thereof. The tapered tubular portion 42 of the main rubber outer tubular fitting 22 is overlapped and vulcanized and bonded to the outer peripheral surface of the side end portion. As a result, the main rubber elastic body 16 is formed as a first integral vulcanized molded article 28 including the main rubber inner metal fitting 18 and the main rubber outer cylinder fitting 22 as described above.

  On the other hand, the diaphragm inner metal fitting 20 constituting the second integrally vulcanized molded product 32 has a thick disk shape. In addition, a fitting convex portion 46 is formed on the lower surface of the diaphragm inner metal member 20, and an insertion hole 48 is formed so as to penetrate the forming portion of the fitting convex portion 46. Further, the diaphragm inner fitting 20 is integrally formed with a mounting plate portion 50 protruding upward, and a bolt insertion hole 52 is provided at the central portion of the mounting plate portion 50.

  Further, the diaphragm outer tube fitting 24 has a thin-walled and large-diameter cylindrical shape, and a mounting plate portion 54 that extends radially outward is integrally formed in the axially upper opening portion. . A plurality of insertion holes are formed in the mounting plate portion 54, and fixing bolts 56 are press-fitted into the insertion holes, respectively. Furthermore, an annular plate-shaped flange-shaped portion 58 that extends outward in the radial direction is integrally formed in the axially lower opening of the diaphragm outer tube fitting 24. An annular caulking piece 60 that projects downward in the axial direction is integrally formed on the outer peripheral edge.

  A diaphragm inner fitting 20 is disposed on substantially the same central axis so as to be spaced apart upward in the axial direction of the diaphragm outer tubular fitting 24, and the diaphragm inner fitting 20 and the diaphragm outer tubular fitting 24 are separated by the diaphragm 30. It is connected.

  The diaphragm 30 is formed of a thin rubber film and has a substantially annular shape extending in the circumferential direction with a curved cross-sectional shape having a large slack so that elastic deformation can be easily allowed. The inner peripheral edge of the diaphragm 30 is vulcanized and bonded to the outer peripheral edge of the diaphragm inner metal fitting 20, and the outer peripheral edge of the diaphragm 30 is in the axially upper opening of the diaphragm outer cylindrical metal fitting 24. It is vulcanized and bonded. Thus, the diaphragm 30 is formed as a second integral vulcanized molded product 32 including the diaphragm inner fitting 20 and the diaphragm outer tube fitting 24.

  Thus, the second integral vulcanized molded product 32 is assembled on the first integral vulcanized molded product 28 from above, and the diaphragm inner metal fitting 20 is attached to the main rubber inner metal fitting 18. The diaphragm outer tube fitting 24 is fixed to the main rubber outer tube fitting 22, and the diaphragm 30 is spaced apart from the main rubber elastic body 16, so that the outer peripheral surface of the main rubber elastic body 16 is fixed. Is disposed so as to cover the entire surface.

  That is, the diaphragm inner metal fitting 20 is directly superimposed on the upper surface of the main rubber inner metal fitting 18, and the fitting convex portion 46 of the diaphragm inner metal fitting 20 is fitted into the fitting concave portion 34 of the main rubber inner metal fitting 18. And the main rubber inner metal fitting 18 are aligned on the same central axis. Particularly in this embodiment, the diaphragm inner metal fitting is obtained by the engaging action of the engaging outer peripheral surface 62 and the engaging inner peripheral surface 64 formed in a notch shape on the outer peripheral surfaces of the fitting convex portion 46 and the fitting concave portion 34. 20 and the main rubber inner metal fitting 18 are positioned relative to each other even in the circumferential direction, and the insertion hole 48 of the diaphragm inner metal fitting 20 and the screw hole 36 of the main rubber inner metal fitting 18 are aligned.

  As shown in FIG. 1, in a state where the main rubber inner metal fitting 18 and the diaphragm inner metal fitting 20 are overlapped, the connecting bolt 66 passes through the insertion hole 48 of the diaphragm inner metal fitting 20, and the screw hole of the main rubber inner metal fitting 18. 36 is screwed. Thus, the main mounting bracket 12 is configured by connecting and fixing the main rubber inner metal fitting 18 and the diaphragm inner metal fitting 20 with the connecting bolt 66.

  On the other hand, the diaphragm outer tubular fitting 24 is externally inserted from the upper side in the axial direction with respect to the main rubber outer tubular fitting 22. Further, the outer peripheral edge of the flange-like portion 40 is overlapped in the axial direction with respect to the flange-like portion 58 of the diaphragm outer tubular fitting 24 at the lower end of the main rubber outer tubular fitting 22, The opening edge portion of the tapered tubular portion 42 is overlapped with the inner peripheral surface of the diaphragm outer tubular fitting 24 in the radial direction.

  Then, the caulking piece 60 of the diaphragm outer tube fitting 24 is caulked and fixed to the outer peripheral edge portion of the flange-like portion 40 of the main rubber outer tube fitting 22, whereby the main rubber outer tube fitting 22 and the diaphragm outer tube fitting 24 are mutually connected. It is fixed and assembled. In addition, seal rubber integrally formed with the main rubber elastic body 16 or the diaphragm 30 is interposed in the overlapping portion of the main body rubber outer cylindrical metal fitting 22 with the diaphragm outer cylindrical metal fitting 24 at both upper and lower end portions, respectively. Is sealed. As a result, the circumferential groove 45 formed in the main rubber outer cylinder fitting 22 is fluid-tightly covered with the diaphragm outer cylinder fitting 24, and the diameter of the cylindrical wall portion 38 of the main rubber outer cylinder fitting 22 and the diaphragm outer cylinder fitting 24 is thereby increased. An annular passage 68 that extends continuously between the direction-opposing surfaces in the circumferential direction with a predetermined length or over the entire circumference is formed.

  Further, a partition plate fitting 70 and a lid member 72 are assembled to the lower opening of the main rubber outer tube fitting 22. The lid member 72 has a vibrating plate 76 as a vibrating member vulcanized and bonded to the center portion of the elastic rubber body 74 having a substantially annular plate shape, and an annular holding bracket 78 on the outer peripheral portion thereof. Are vulcanized and bonded, and the vibration plate 76 and the annular holding metal fitting 78 are elastically connected by a support rubber elastic body 74.

  The vibration plate 76 has a disk shape, and an annular connecting portion 80 that protrudes upward is integrally formed on the outer peripheral edge thereof. In addition, a drive shaft 82 extending downward is integrally formed at the central portion of the vibration plate 76, and a tip portion of the drive shaft 82 is a male screw. The vibration plate 76 includes the annular coupling portion 80 and the drive shaft 82, and is integrally formed of a hard material such as metal or synthetic resin.

  On the other hand, the annular holding fitting 78 is integrally formed with a mounting plate 86 and a positioning projection 88 that spread in a flange shape with respect to the upper and lower openings of the cylindrical portion 84 having a cylindrical shape. An annular press-fit portion 90 that protrudes further downward is integrally formed at the peripheral edge portion.

  A vibration plate 76 is disposed on substantially the same central axis so as to be spaced inward in the radial direction of the annular holding bracket 78, and spread between the radial facing surfaces of the annular holding bracket 78 and the vibration plate 76. Thus, the supporting rubber elastic body 74 is disposed. Further, the inner and outer peripheral edges of the supporting rubber elastic body 74 are vulcanized and bonded to the opposing surfaces of the annular connecting portion 80 of the vibration plate 76 and the cylindrical portion 84 of the annular holding bracket 78, respectively. A space between the plate 76 and the annular holding bracket 78 is fluid-tightly closed by a support rubber elastic body 74. A stopper rubber 92 is formed in the vicinity of the annular connecting portion 80 of the vibration plate 76 so as to cover the annular connecting portion 80, and the amount of movement of the vibration plate 76 in the approaching direction to the partition plate fitting 70 is reduced. In addition to being limited in terms of buffering, impact and hitting sound at the time of contact are reduced. Further, in the present embodiment, the height of the stopper rubber 92 is different in the circumferential direction of the annular connecting portion 80, and even when the stopper rubber 92 is brought into contact with the divider plate fitting 70, An appropriate gap is ensured between them to prevent the vibration chamber 106 described later from being shut off. Thereby, it is reduced that the suction force which goes to the partition plate metal fitting 70 side with respect to the vibration board 76 with the water pressure of an incompressible fluid is reduced.

  In the vicinity of the outer peripheral edge of the vibration plate 76, an elastic stopping protrusion 94 as an elastic stopper protrusion is formed to protrude downward. The elastic restraining protrusion 94 is formed of a rubber elastic body, and in particular in the present embodiment, is integrally formed with the support rubber elastic body 74. As shown in FIG. 2, the elastic stopping protrusion 94 is formed in a circular peripheral wall shape in which the support rubber elastic body 74 rises downward at the lower outer peripheral edge of the vibration plate 76. In the present embodiment, the elastic restraining projection piece 94 has an inner diameter dimension larger than the outer diameter dimension of the guide sleeve 130 positioned facing the vibration plate 76, and the radial thickness dimension is the proximal end. The taper has a tapered cross-sectional shape that gradually decreases from the portion toward the lower protruding tip portion. Further, a cut-out radial concave groove 96 extending continuously in the radial direction is formed at at least one location on the circumference on the protruding front end surface of the elastic restraining projection piece 94.

  On the other hand, the partition plate fitting 70 has a thin disk shape, and its outer diameter dimension is set to a size that reaches the middle portion in the radial direction of the mounting plate portion 86 in the annular holding fitting 78. Further, the central portion of the partition plate fitting 70 is projected upward in a substantially plateau shape, and a plurality of orifice through holes 98 are provided therethrough. Further, a plurality of locking pieces 100 project upward from the circumference located near the outer peripheral edge portion of the partition plate fitting 70.

  The partition plate fitting 70 is aligned in the direction perpendicular to the axis by the locking piece 100, and is attached to the flange-like portion 40 of the main rubber outer tube fitting 22 assembled thereto at the lower opening of the diaphragm outer tube fitting 24. On the other hand, the outer peripheral edge is overlapped and assembled. Further, a lid member 72 is assembled from the lower side of the partition plate fitting 70 to the lower opening of the diaphragm outer tube fitting 24, and the mounting plate portion 86 of the annular holding fitting 78 in the lid member 72 is a main rubber outer tube fitting. 22 and the partition plate fitting 70 are superposed on each other, and the respective outer peripheral edges thereof are caulked and fixed by caulking pieces 60 of the diaphragm outer tube fitting 24.

  As a result, the lower opening of the diaphragm outer cylinder 24 is fluid-tightly covered with the lid member 72, so that the incompressible fluid is between the opposing surfaces of the main rubber elastic body 16 and the lid member 72. Is formed. A part of the wall of the pressure receiving chamber 102 is constituted by the main rubber elastic body 16, and the elasticity of the main rubber elastic body 16 is input when vibration is input between the first mounting bracket 12 and the second mounting bracket 14. Based on the deformation, a vibration is input to cause a pressure fluctuation.

  In addition, a partition plate fitting 70 is disposed in the pressure receiving chamber 102, and the pressure receiving chamber 102 sandwiches the partition plate fitting 70 and the vibration input chamber 104 on the main rubber elastic body 16 side and the lid member 72 side. The vibration input chamber 104 and the vibration chamber 106 are communicated with each other through an orifice through hole 98.

  Furthermore, the main rubber elastic body 16 and the diaphragm 30 are fixed to the first mounting bracket 12 and the second mounting bracket 14 at the inner peripheral edge and the outer peripheral edge, respectively, so that the main rubber elastic body 16 and the diaphragm are fixed. Between the 30 opposing surfaces, an equilibrium chamber 108 in which an incompressible fluid is sealed is formed. That is, the equilibrium chamber 108 is configured by the diaphragm 30 having a part of the wall that is easily deformable, and the volume change is easily allowed based on the elastic deformation of the diaphragm 30. The incompressible fluid sealed in the pressure receiving chamber 102 and the equilibrium chamber 108 is a vibration required for the automobile engine mount 10 to have a vibration isolation effect based on a resonance action of a fluid that flows through an orifice passage 114 described later. In order to obtain efficiently in the frequency range, generally 0.1 Pa. A low-viscosity fluid of s or less is preferably employed.

  Furthermore, the pressure receiving chamber 102 and the equilibrium chamber 108 formed on the upper side have an annular passage 68 formed in the second mounting bracket 14 and a communication hole 110 formed at one end in the circumferential direction, and a circumferential direction. The other end is connected through a communication hole 112 formed in the main rubber elastic body 16, thereby allowing the pressure receiving chamber 102 and the equilibrium chamber 108 to communicate with each other to allow fluid flow between the chambers 102, 108. An orifice passage 114 is formed with a predetermined length. The orifice passage 114 has an anti-vibration effect based on a resonance action of a fluid that is caused to flow inside based on a pressure difference caused between the pressure receiving chamber 102 and the equilibrium chamber 108 when vibration is input. The passage cross-sectional area and the passage length are appropriately set and tuned so as to be effectively exhibited in the frequency range of large amplitude vibration.

  On the other hand, an electromagnetic exciter 116 as an electromagnetic actuator is disposed on the opposite side of the pressure receiving chamber 102 across the lid member 72. In the electromagnetic exciter 116, a coil 120 is fixedly assembled in a substantially cup-shaped housing 118, and upper and lower yokes 122 made of a ring-shaped ferromagnetic material are disposed around the coil 120, respectively. 124 is fixedly assembled to form a magnetic path. Specifically, the upper yoke 122 and the lower yoke 124 are made of a ferromagnetic material and are magnetically connected via the housing 118, and cooperate with a magnetic path extending so as to surround the coil 120 in the longitudinal section. To form. In this magnetic path, a magnetic gap is formed between the upper yoke 122 and the lower yoke 124 in the inner peripheral portion of the coil 120, and a slider 126 as an output member is disposed at a position corresponding to the magnetic gap. Has been. Then, when the coil 120 is energized, a magnetic pole is formed between the opposing surfaces of the upper and lower yokes 122 and 124, and an axial driving force toward the lower yoke 124 is exerted on the slider 126. ing.

  A cylindrical inner peripheral surface 128 as a guide hole penetrating the center is formed in the upper yoke 122 that forms the magnetic path, and the guide sleeve 130 is elastically positioned on the cylindrical inner peripheral surface 128. Has been installed. The slider 126 is slidably assembled in the guide sleeve 130 and is driven in the axial direction while being guided by the guide sleeve 130.

  The slider 126 has a substantially cylindrical shape as a whole and is slidable on the guide sleeve 130 on the outer peripheral surface. On the inner peripheral surface, an annular engagement protrusion 132 faces inward. The protrusion is formed.

  The electromagnetic exciter 116 is caulked together with the annular holding bracket 78 and the like by overlapping the flange portion 134 formed at the opening peripheral edge of the housing 118 with the mounting plate portion 86 of the annular holding bracket 78 in the lid member 72. The piece 60 is caulked and fixed to the second mounting bracket 14. Thereby, the electromagnetic exciter 116 is assembled on the same central axis so that the sliding central axis of the slider 126 substantially coincides with the central axes of the first and second mounting brackets 12 and 14. .

  In addition, a drive shaft 82 of the vibration plate 76 is inserted into the electromagnetic vibrator 116 assembled in this way from above on the central axis, and the drive shaft 82 is engaged with the engagement protrusion of the slider 126. The part 132 is inserted. Further, a coil spring 136 is extrapolated to the drive shaft 82 and is disposed across the opposing surfaces of the vibration plate 76 and the engaging projection 132 of the slider 126. A positioning nut 138 is screwed to the tip portion inserted through the engaging protrusion 132. Then, the positioning nut 138 is screwed into the drive shaft 82, and the coil spring 136 is compressed with the vibration plate 76 via the engagement protrusion 132 of the slider 126, so that the slider is moved with respect to the drive shaft 82. 126 is fixedly positioned in the axial direction. In this embodiment, the collar member 140 is attached to both ends of the coil spring 136 to reduce wear due to friction between the coil spring 136 and other members. Thus, the drive shaft 82 and the slider 126 are connected in a substantially fixed state in the axial direction by the urging force of the coil spring 136, and the driving force applied to the slider 126 by energizing the coil 120 is driven. It extends to the shaft 82.

  In short, the mounting position of the slider 126 in the axial direction with respect to the vibration plate 76 elastically positioned and supported by the support rubber elastic body 74 with respect to the second mounting bracket 14 is determined by screwing the positioning nut 138 into the drive shaft 82. By adjusting the amount, it can be changed and set, thereby making it possible to finely adjust the distance between the magnetically acting opposing surfaces of the slider 126 with respect to the lower yoke 124. In this embodiment, the lock bolt 142 is tightened from the lower side in the axial direction with respect to the positioning nut 138, and the lock bolt 142 is in contact with the tip of the drive shaft 82 in the screw hole of the positioning nut 138. As a result, the tightening position of the positioning nut 138 relative to the drive shaft 82 is locked.

  Note that a slight gap is formed between the outer peripheral edge of the positioning nut 138 and the facing surface of the slider 126, and the slider 126 is allowed to slide in a direction perpendicular to the drive shaft 82. Thus, the positioning nut 138 is overlaid and held in contact. Thus, relative displacement between the drive shaft 82 and the slider 126 due to a dimensional error in manufacturing of each member or a positioning error during assembly can be advantageously absorbed, and the slider 126 can be coiled. Positioning relative to 120 can also be performed stably in the direction perpendicular to the axis. In addition, a temporary axis deviation (relative displacement in the direction perpendicular to the axis) during actuator operation is also advantageously absorbed, and stable operation characteristics can be obtained. In addition, as an allowable amount of the relative displacement in the direction perpendicular to the axis, a range of 0.2 mm to 3 mm is preferably employed.

  A through hole 144 is formed in the center of the bottom wall portion of the housing 118 of the electromagnetic exciter 116, and a lower yoke 124 that is positioned opposite to the slider 126 and exerts a magnetic force is exposed to the outside. At the same time, the internal space of the electromagnetic exciter 116 in which the slider 126 is disposed can be directly opened to the outside through the center hole 146 of the lower yoke 124. Then, by inserting a tool such as a hexagon wrench into the opening of the central hole 146 of the lower yoke 124 through this opening, the above-described lock bolt 142 and positioning nut 138 are operated to position the slider 126 from the outside. It can be adjusted.

  Further, as shown in FIG. 3, the center hole 146 of the lower yoke 124 is a large diameter portion 148 having an enlarged diameter near the opening, and is positioned inward in the axial direction of the opening as an annular stepped portion. The step surface 150 is formed. An annular locking groove 152 that extends continuously in the circumferential direction is formed on the inner peripheral surface of the large diameter portion 148. The large-diameter portion 148 is assembled with a lid plate fitting 154.

  The lid plate metal 154 has a disk shape, and a rubber layer 156 is formed on one surface over the entire surface and is vulcanized and bonded. The rubber layer 156 is formed of a buffer rubber portion 158 at the center portion and an annular seal rubber portion 160 at the outer peripheral portion that is slightly thicker than the buffer rubber portion 152. The lid plate metal 154 is fitted into the large-diameter portion 148 of the lower yoke 124, and the C-shaped retaining ring 162 is fitted into the large-diameter portion 148 from the outside of the lid plate metal 154 to be locked in the locking groove 152. It is installed.

  As a result, the outer surface of the cover plate fitting 154 is pressed by the C-shaped retaining ring 162, and the outer peripheral portion of the cover plate fitting 154 is in contact with the stepped surface 150 via the annular seal rubber portion 160. The central hole 146 formed in the lower yoke 124 of the electromagnetic exciter 116 is covered with a fluid-tight cover at the large-diameter portion 148 formed in the opening. Further, the center portion of the cover plate metal fitting 154 is opposed to the front end surface of the drive shaft 82 of the vibration plate 76 at a predetermined distance downward in the axial direction. As a result, when a large vibration load is input between the first mounting bracket 12 and the second mounting bracket 14 and an excessive pressure is induced in the pressure receiving chamber 102, the tip of the drive shaft 82 becomes the buffer rubber portion. By abutting the lid plate metal 154 via 158, the displacement amount of the vibration plate 76 is limited in a buffering manner.

  Furthermore, in the electromagnetic exciter 116 assembled as described above, as shown in FIG. 2, the upper yoke 122 that forms the magnetic path is used as a contact member, and the electromagnetic exciter 116 is assembled. In FIG. 2, the elastic restraining protrusion 94 protrudes from the vibration plate 76 and is fixed to the second mounting member 14.

  That is, the upper surface in the axial direction of the upper yoke 122 is arranged to be opposed to the protruding front end surface of the elastic restraining protruding piece 94 provided on the vibration plate 76 in the axial direction with a predetermined distance therebetween. The upper surface is a flat surface 164 extending in the direction perpendicular to the axis. The elastic restraining protrusion 94 and the upper yoke 122 are opposed to each other with a predetermined gap: T in a non-energized state of the electromagnetic exciter 116. The gap: T is a general passenger car as in this embodiment. In the engine mount for the above, it is desirable that 0 <T ≦ 2.0 mm, and more preferably 0 <T ≦ 0.8 mm. When the gap T is too large, the elastic restraining protrusion 94 does not contact the upper yoke 122 or contacts even when a large amplitude vibration such as an engine shake is input to the pressure receiving chamber 102. This is because the vibration plate 76 is already displaced considerably at the time, and the pressure change in the pressure receiving chamber 102 is absorbed, so that a sufficient amount of incompressible fluid flowing through the orifice passage 114 cannot be secured. On the other hand, when T ≦ 0 and the elastic damping protrusion 94 is in contact or compressed from the beginning, the excitation force applied from the electromagnetic vibrator 116 to the vibration plate 76 is elastically stopped. Since the vibration is absorbed by the piece 94 and the vibration driving force is not efficiently applied to the vibration plate 76, the intended active vibration isolation effect is hardly exhibited.

  In the engine mount 10 having the above-described structure, a cylindrical bracket 166 is further inserted with respect to the electromagnetic vibrator 116. The cylindrical bracket 166 has a flange-shaped portion 168 at the upper end opening, and the flange-shaped portion 168 includes the flange-shaped portion 40 of the main rubber outer tube fitting 22, the mounting plate portion 86 of the annular holding bracket 78, and the housing 118. The flange portion 134 and the diaphragm outer tube fitting 24 are caulked and fixed by a caulking piece 60. A mounting plate 170 is formed at the lower end opening of the cylindrical bracket 166, and a plurality of mounting holes (not shown) are formed in the mounting plate 170.

  Thus, although the engine mount 10 is not shown, the mounting plate portion 50 of the first mounting bracket 12 is attached to the power unit with a fixing bolt inserted into the bolt insertion hole 52, while the second mounting bracket 14 is attached between the power unit and the body by being attached to the vehicle body with a fixing bolt via the cylindrical bracket 166. When vibration is input between the first mounting bracket 12 and the second mounting bracket 14 in such a mounting state, the elastic body 16 elastically deforms between the pressure receiving chamber 102 and the equilibrium chamber 108. A fluid flow is generated through the orifice passage 114 on the basis of the pressure difference caused by the fluid, and a passive vibration-proofing effect is exhibited on the basis of a fluid action such as a resonance action of the fluid. Further, by controlling the energization to the coil 120 at a frequency or phase according to the vibration to be damped and driving the oscillating plate 76 by the electromagnetic oscillating device 116, the orifice through hole 98 from the oscillating chamber 106 is driven. By applying pressure fluctuation to the vibration input chamber 104 through and actively controlling the pressure fluctuation in the vibration input chamber 104, an active vibration isolation effect can be obtained against the input vibration.

  Therefore, in the engine mount 10 according to the present embodiment, the amount of displacement of the vibration plate 76 is buffered by the elastic restraining protrusion 94 protruding from the vibration plate 76, so that it is as low as an engine shake. When high frequency vibration is input, the displacement of the vibration plate 76 and the deformation of the support rubber elastic body 74 are restricted, and the incompressible fluid flowing through the orifice passage 114 tuned to the frequency range of the engine shake vibration. By effectively securing the amount of flow of the target, the intended high damping effect can be exhibited effectively. On the other hand, since a predetermined gap: T is provided between the elastic restraining projection piece 94 and the upper yoke 122, the elastic restraining projection piece 94 inhibits the excitation operation of the vibration plate 76 by the electromagnetic vibrator 116. Therefore, an active vibration isolating effect due to the vibration displacement of the vibration plate 76 can be exerted on medium to high frequency small amplitude vibration such as idling vibration and booming noise. Furthermore, by projecting the elastic restraining protrusion 94 from the vibration plate 76, it is possible to effectively obtain the intended vibration isolation effect without causing problems such as an increase in the size of the actuator.

  That is, in the engine mount 10 of this embodiment, in addition to the elastic restraining protrusion 94 projecting from the vibration plate 76 instead of the radial intermediate portion that is the free length of the support rubber elastic body 74, the electromagnetic excitation In a non-energized state, the elastic restraining projection piece 94 is positioned apart from the upper yoke 122 as an abutting member so that the displacement limiting force by the elastic restraining projection piece 94 does not act. It is configured. As a result, adverse effects caused by the provision of the elastic restraining projection piece 94 can be avoided for small-amplitude vibrations in the middle to high frequency range such as idling vibrations, and under the initial spring characteristics of the support rubber elastic body 74. When the vibration plate 76 is vibrated efficiently by the electromagnetic exciter 116, the pressure control of the pressure receiving chamber 102 can be efficiently realized, and a desired active vibration isolation effect can be obtained. I can do it. On the other hand, when a low-frequency large-amplitude vibration such as an engine shake is input, the displacement limiting function of the vibration plate 76 is exhibited based on the contact of the elastic stopping projection piece 94 with the upper yoke 122. That is, the displacement of the vibration plate 76 and the deformation of the support rubber elastic body 74 are limited, and passive pressure fluctuations accompanying vibration input are efficiently induced in the pressure receiving chamber 102, thereby The relative pressure fluctuation of the equilibrium chamber 108 is generated, and the amount of fluid flow through the orifice passage 114 is advantageously ensured, and the high damping effect by the orifice passage 114 can be effectively obtained.

  Further, in the engine mount 10 of the present embodiment, the orifice passage 114 is formed around the main rubber elastic body 16, so that the degree of freedom in design is low, and the orifice passage 114 communicates with the pressure receiving chamber 102 and the equilibrium chamber 108. Although there are cases where it is difficult to perform effective tuning for engine shake or the like such as the opening direction of the holes 110 and 112, in the engine mount 10 of the present embodiment, the displacement of the vibration plate 76 and the deformation of the support rubber elastic body 74 are difficult. By limiting, it is possible to advantageously secure the flow amount of the incompressible fluid flowing through the orifice passage 114 and obtain an effective high damping effect.

  In addition, since the elastic stopping projection piece 94 is formed of a rubber elastic body, occurrence of hitting sound and vibration upon hitting can be suppressed. In particular, the elastic stopping projection piece 94 in the present embodiment has a tapered shape, and a non-linear characteristic is imparted with respect to the load-deflection characteristic, and the hitting sound and vibration are further effectively reduced. Further, since the elastic restraining protrusion 94 in this embodiment is integrally formed with the support rubber elastic body 74, there is no increase in the number of special members or manufacturing steps.

  Furthermore, in the engine mount 10 of this embodiment, since the contact member is constituted by the yoke member of the actuator, there is no need to provide a special contact member, and the number of parts and the number of manufacturing processes are further increased. Effectively suppressed. In addition, the axial dimension of the engine mount can be reduced as compared with the case where a separate contact member is disposed between the actuator and the vibration member.

  In addition, in the engine mount 10 of the present embodiment, the housing 118 of the electromagnetic exciter 116 is caulked and fixed to the second mounting bracket 14, and a rubber elastic body or a synthetic resin material is formed at the caulking site. It is not intervening, and has a laminated structure of metals. As a result, the relative positional relationship between the mount and the actuator in the axial direction can be set with high accuracy, and the clearance between the elastic stopper projection and the contact member can be set with high accuracy, and the desired effect can be achieved. Can be obtained more advantageously under high reliability.

  More specifically, when the electromagnetic exciter 116 is energized to cause the slider 126 to vibrate, the slider 126 generally returns to its initial position (axial position under a non-energized state). Without any change, the vibration displacement occurs between the lowest attracted point and the position in the middle of the return to the initial position at a period and phase corresponding to the frequency of the alternating current to be fed. The displacement amount of the vibration displacement varies depending on the characteristics of the coil 120, the mass of the slider 126, the sliding characteristics, the spring characteristics of the coil spring 136 and the supporting rubber elastic body 74, and the lowest point at the time of vibration is Assuming 0.8 mm downward from the initial position, the slider 126 reciprocates in the axial direction within a 0.4 mm stroke range from the initial position 0.4 mm downward to the 0.8 mm downward position. The vibration is displaced. In such a stroke range, it is desirable to set the elastic stopping projection piece 94 so as not to hit the opposing flat surface 164. Specifically, the value of the distance T between the lower end surface of the elastic stopping projection 94 and the flat surface 164 of the electromagnetic exciter 116 is set to 0.8 mm at the initial position of non-energization. Accordingly, it is possible to completely avoid the adverse effects caused by the elastic restraining protrusion 94 and efficiently drive the vibration plate 76 to effectively obtain an active vibration isolation effect. Note that if the value of the distance T is set too large, the effect of limiting the displacement of the vibration plate 76 at the time of target shake input will not be exhibited.

  On the other hand, when an engine shake at the time of stepping over is input, the vibration member is passively displaced larger than the above-described active vibration as the pressure in the pressure receiving chamber 102 increases instantaneously. I'm damned. The amount of displacement depends on the spring characteristics of the main rubber elastic body 16, the volume of the pressure receiving chamber 102, the size of the vibration member, the spring characteristics of the support rubber elastic body 74, and the like. If it is displaced to a position lowered by 2.2 mm at the maximum, if it is not energized (vibrated state), the vibrating member should be displaced downward by 2.2 mm from the reference position (initial position). It becomes. Accordingly, if T is set to 0.8 mm as described above at the initial position, it is easily displaced up to 0.8 mm. However, beyond that, the elastic restraining projection piece 94 comes into contact with the upper yoke 122 and thereafter. The spring of the elastic restraining protrusion 94 acts to suppress the displacement of the vibration member elastically. As a result, the pressure fluctuation in the pressure receiving chamber 102 is efficiently generated, and an anti-vibration effect (damping action) based on the fluid flow through the orifice passage 114 is exhibited.

  Further, when the engine shake is input in the vibration state, the amount of displacement of the vibration member from the initial position downward is (2.2 + 0.4) to (2.2 + 0.8). Therefore, in this case, a more effective displacement suppression effect is exhibited.

  In designing practically, appropriate tolerances are set in consideration of the material of the support rubber elastic body to be used, the accuracy of molding of the support rubber elastic body and each metal fitting, etc. In consideration of the tolerance, the initial value of the distance T between the opposing surfaces between the elastic stopper protrusion and the contact member is set from the dimensions of each member. However, since the tolerance is generally 1.0 mm or less and less than 0.8 mm if sufficiently controlled, the above-described effects can be exhibited sufficiently stably.

  As mentioned above, although one Embodiment of this invention was explained in full detail, this is an illustration to the last, Comprising: This invention is not limited at all by the specific description in this Embodiment.

  Needless to say, the specific mode of the elastic stopper protrusion is not limited in any way. For example, the elastic stopper protrusion may be formed in a shape that is continuous in the circumferential direction of the vibration plate 76 or a spring different from the support rubber elastic body 74. It may be formed from another member having a constant value and fixed below the vibration plate 76. Various forms of the abutting member can be employed. For example, a member prepared separately may be disposed at a position facing the elastic stopper protrusion without using the upper yoke 122.

  In addition, the specific shape of the elastic stopper protrusion and the distance between the opposing surfaces of the elastic stopper protrusion and the contact member can be set as appropriate in consideration of the required characteristics of the mount, spring characteristics, actuator output characteristics, etc. It is. For example, when the spring characteristics per initial of the elastic stopper protrusion are sufficiently softened and the vibration stroke of the vibration member by the actuator is sufficiently small, the opposing surface of the elastic stopper protrusion and the contact member When the distance is set to a slight distance and the vibration member is vibrated by the electromagnetic actuator, the elastic stopper protrusion is substantially always brought into contact with the contact member. The vibration member may be displaced by vibration based on elastic deformation.

  In addition, the present invention is not limited to the automobile engine mount having the shape as illustrated, but can also be applied to a so-called cylindrical mount, etc., in a body mount or a member mount for an automobile, or in various devices other than an automobile. The present invention can be similarly applied to a vibration isolator such as a mount or a vibration damper.

  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. It is a principal part enlarged view of the engine mount shown in FIG.

Explanation of symbols

DESCRIPTION OF SYMBOLS 10 Engine mount 12 1st attachment metal fitting 14 2nd attachment metal fitting 16 Main body rubber elastic body 30 Diaphragm 70 Partition plate metal fitting 72 Cover member 74 Support rubber elastic body 76 Excitation plate 82 Drive shaft 94 Elastic stop protrusion 98 Orifice through-hole 102 Pressure receiving chamber 106 Excitation chamber 108 Equilibrium chamber 114 Orifice passage 116 Electromagnetic exciter 118 Housing 120 Coil 122 Upper yoke 124 Lower yoke 126 Slider 154 Lid plate metal fitting

Claims (4)

The first mounting member to be attached to one of the power unit and the vehicle body of the automobile is spaced apart from one opening side of the second mounting member having a substantially cylindrical shape attached to the other of the power unit and the vehicle body. The first mounting member and the second mounting member are connected with a rubber elastic body to cover the one opening of the second mounting member in a fluid-tight manner, and the second mounting member A vibration member is disposed in the other opening, and the vibration member is connected to the second mounting member with a support rubber elastic body, thereby the other opening of the second mounting member is A fluid-tight cover is formed to form a pressure receiving chamber in which an incompressible fluid is sealed between the rubber elastic body and the vibration member, and the one of the first mounting member and the second mounting member. Rubber bullets that spread across the periphery of the opening By disposing the membrane outwardly of the main rubber elastic body, a part of the wall portion is formed by the rubber elastic film on the side opposite to the pressure receiving chamber with the main rubber elastic body interposed therebetween. An equilibrium chamber in which a compressive fluid is sealed is formed, an orifice passage that communicates the pressure receiving chamber and the equilibrium chamber with each other is provided, and an electromagnetic actuator is disposed outside the excitation member. The pressure receiving chamber is formed by fixing a housing of the electromagnetic actuator to the second mounting member and connecting an output member of the electromagnetic actuator to the vibration member to exert a vibration force on the vibration member. In an active fluid-filled engine mount that actively controls the pressure of
While tuning the orifice passage to the frequency range of the engine shake,
An abutting member spaced apart from the vibration member is fixedly provided to the second mounting member, and an elastic stopper protrusion that protrudes from the vibration member toward the contact member is provided. In the non-energized state of the electromagnetic actuator, a predetermined gap is formed between the elastic stopper protrusion and the opposing surface of the contact member, and when idling vibration is input, the electromagnetic actuator is energized. An active vibration isolation effect is exhibited based on the vibration displacement of the vibration member, and at the time of engine shake input, the elastic stopper protrusion comes into contact with the corresponding contact member to buffer the displacement amount of the vibration member. Active fluid-filled engine mount, characterized in that it is limited in nature.   The active fluid-filled engine mount according to claim 1, wherein the elastic stopper protrusion is formed integrally with the support rubber elastic body.   The active fluid-filled engine mount according to claim 1, wherein the contact member is formed by the electromagnetic actuator. The size T of the gap between the elastic stopper protrusion and the facing surface of the contact member under a non-energized state of the electromagnetic actuator: T is 0 <T ≦ 2.0 mm. 4. The active fluid-filled engine mount according to any one of 3 above.

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