JP2009052591A - Fluid filled engine mount - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To provide a fluid filled engine mount having a new structure, surely switching a second orifice passage between the shut-off state and the communicating state based on stable displacement of a valve element to obtain excellent vibration proof effect, and advantageously restraining the generation of hammering sound due to mutual knocking of members. <P>SOLUTION: Opposite parts brought into close contact to each other with the drive of the valve element 84 caused by a solenoid actuator 54 are provided in a filling area of an incompressible fluid, a recessed part 89 filled with the incompressible fluid is formed open to the opposite surface on one of the opposite parts, and a projecting part 95 projected on the opposite surface is formed on the other of the opposite parts, thereby constituting a damping mechanism having a dash pot structure in which the projecting part 95 enters the recessed part 89 on the other displacement side of the communicating position and the shut-off position of the valve element 84. <P>COPYRIGHT: (C)2009,JPO&INPIT

Description

  The present invention relates to an engine mount that supports a power unit in a vibration-proof manner with respect to a vehicle body, and more particularly to a fluid-filled engine mount that exhibits a vibration-proofing effect based on the flow action of a fluid sealed inside.

  Conventionally, as a kind of engine mount that is mounted between the power unit and the vehicle body and supports both of them for anti-vibration connection or anti-vibration support, the first mounting member and the second mounting member are connected to each other with a rubber elastic body. Then, a pressure receiving chamber in which a part of the wall portion is configured by a main rubber elastic body and an equilibrium chamber in which a part of the wall portion is configured by a flexible film that is easily deformed are formed. There is known a fluid-filled engine mount having a structure in which an incompressible fluid is sealed in and an orifice passage is provided to allow the two chambers to communicate with each other. In such a fluid-filled engine mount, a vibration isolation effect can be obtained by using a fluid action such as a resonance action of a fluid that flows through the orifice passage. For example, application to an engine mount for automobiles has been studied. Yes.

  By the way, in the above-described fluid-filled engine mount, vibrations in different frequency ranges are input in accordance with the running state, etc., so that any effective anti-vibration effect can be provided for a plurality of vibrations in different frequency ranges. It is desirable to be demonstrated. However, there is a problem that the vibration-proofing effect based on the fluid action of the fluid flowing through the orifice passage is effectively exhibited only in a relatively narrow frequency range in which the orifice passage is tuned in advance.

  Therefore, in order to solve such a problem, for example, in Patent Document 1 (Japanese Patent Laid-Open No. 59-151537), a first orifice passage and a second orifice passage are respectively provided in a partition member that partitions the pressure receiving chamber and the equilibrium chamber. The second orifice passage is tuned to a frequency range higher than that of the first orifice passage, and the second orifice passage is switched between the communication state and the cutoff state using a valve body that is driven and displaced by a solenoid actuator. Such a fluid-filled engine mount has been proposed. According to such an engine mount, a compression coil spring that biases the valve body in the direction opposite to the drive displacement direction by the solenoid is provided, and by controlling the energization to the solenoid according to the traveling state, The valve body is switched. And the anti-vibration effect based on the flow action of each fluid through the 1st orifice passage and the 2nd orifice passage is each exhibited effectively, and the anti-vibration effect with respect to the vibration of a plurality of frequency ranges is acquired.

  By the way, in the fluid filled engine mount described in Patent Document 1, in order to stably switch the communication state and the shut-off state of the second orifice passage with the valve body, the valve body is surely set to the open position and the closed position, respectively. It is effective to hold the positioning. Therefore, a contact-type stopper mechanism is generally employed at the displacement end of the valve body.

  However, when such a valve body stopper mechanism is employed, a hitting sound generated upon contact with the valve body stopper mechanism is likely to be a problem. Particularly, in the solenoid actuator, the driving force gradually increases as the mover approaches the solenoid. Therefore, if the output of the solenoid actuator is set so that a sufficient driving force can be obtained at the initial stage of driving the solenoid valve, which is positioned and held by the coil spring, a very large drive is achieved at the position where the valve body contacts the stopper mechanism. The force would act on the valve body, and there was a problem that a loud sound was generated.

  In order to cope with the contact sound of the valve body, for example, a buffer rubber may be provided between the contact surfaces.

  However, if the buffer rubber is provided in the displacement direction of the valve body, the movable region of the valve body is limited. In addition, a special part, its device, and a process for assembling are newly required to dispose the buffer rubber. In addition, it is difficult to obtain sufficient impact absorption with the shock absorbing rubber, and it is difficult to ensure the durability of the impact control effect.

JP 59-151537

  Here, the present invention has been made in the background as described above, and the problem to be solved is that the shut-off state and the communication state of the second orifice passage are based on the stable displacement of the valve body. A fluid-sealed structure with a novel structure that can be switched over reliably to obtain an excellent vibration-proofing effect and also suppress the occurrence of sound that causes problems due to contact with other members when the valve body is displaced To provide an engine mount.

  Hereinafter, the aspect of this invention made | formed in order to solve such a subject is described. In addition, the component employ | adopted in each aspect as described below is employable by arbitrary combinations as much as possible. Further, aspects or technical features of the present invention are not limited to those described below, but are described in the entire specification and drawings, or an invention that can be understood by those skilled in the art from those descriptions. It should be understood that it is recognized based on thought.

  That is, the feature of the present invention is that the first mounting member attached to one of the power unit and the vehicle body and the second mounting member attached to the other of the power unit and the vehicle body are connected by the main rubber elastic body. In addition, on both sides of the partition member supported by the second mounting member, a pressure receiving chamber in which a part of the wall is made of a main rubber elastic body and a part of the wall are made of a flexible film Form equilibrium chambers, enclose the incompressible fluid in the pressure receiving chamber and the equilibrium chamber, and form the first and second orifice passages in the partition members that allow the pressure receiving chamber and the equilibrium chamber to communicate with each other. The second orifice passage is tuned to a higher frequency range than the first orifice passage, and the valve body is displaced between a communication position for communicating the second orifice passage and a blocking position for blocking. Urging means for urging the valve body toward one of the communication position and the shut-off position and holding the valving element at the position; and the other of the communication position and the shut-off position of the valve body against the urging force of the urging means. In a fluid-filled engine mount provided with a solenoid actuator that is driven and held at such a position, a stopper that defines a displacement end of the valve body driven by the solenoid actuator to the other side of the communication position and the cutoff position by contact While providing a mechanism, an opposing part that is brought close to each other as the valve element is driven by a solenoid actuator is provided in the incompressible fluid sealing region, and one of the opposing parts opens to the opposing surface and is incompressible. A valve that is driven by a solenoid actuator, forming a recess filled with fluid, and forming a protrusion protruding on the opposite surface at the other of the opposite portions In fluid-filled engine mount constructed the damping mechanism of the dashpot structure protrusion enters the recess in the other displacement end of the communicating position and the blocking position of the.

  In such a fluid-filled engine mount having a structure according to the present invention, the valve body is displaced from one side to the other against the biasing force of the biasing means by energization of the solenoid, so that the stopper mechanism By abutting, the other displacement end of the valve body is defined. As a result, the communication state or blocking state of the second orifice passage is stably maintained.

  In the fluid-filled engine mount according to the present invention, a recess filled with an incompressible fluid is formed in one of the opposed parts that are brought close to each other when the valve body is driven by the solenoid actuator, and the opposed part A protrusion is formed on the other of the two, and a damp-pot structure damping mechanism is formed in which the protrusion enters the recess on the other displacement side of the communicating position and the blocking position of the valve body driven by the solenoid actuator. Accordingly, when the valve body is positioned on the other displacement side, the solenoid actuator is based on the fluid flow resistance, the shearing shearing action, the viscous action, etc. exhibited by the protrusion entering the recess. , The acceleration displacement of the valve body on the other displacement side where the output is larger than that on the one displacement side is suppressed. As a result, the speed and power when the valve body strikes against the stopper is suppressed, and problematic hitting noise is effectively prevented.

  Therefore, in the fluid-filled engine mount having the structure according to the present invention, the shut-off state and the communication state of the second orifice passage accompanying the contact of the valve body with the stopper mechanism are stabilized, and the valve body is a stopper mechanism. The prevention of the occurrence of a hitting sound which becomes a problem when hitting the sound can be achieved at a high level.

  In the fluid-filled engine mount according to the present invention, the valve body is formed of a ferromagnetic material, and the valve body is displaceably disposed on the fluid flow path through the second orifice passage in the partition member. An urging means is disposed between the wall portion constituting the flow path and the valve body to urge the valve body toward one of the communication position and the blocking position, while a solenoid is disposed around the valve body in the partition member. A structure in which a solenoid actuator including the valve body, the solenoid, and the biasing means is incorporated into the partition member may be employed. According to such a structure, the housing for accommodating and arranging the solenoid actuator is realized by the existing partition member, and it is not necessary to provide a new one. Therefore, the cost can be advantageously reduced by reducing the number of parts. obtain. In addition, since the solenoid and the valve body are prevented from protruding outward from the second mounting member, the mount can be advantageously made compact.

  In the fluid-filled engine mount according to the present invention, the valve body has a bottomed cylindrical shape, and the protrusion is formed at the opening edge of the valve body, and the valve member is driven by the solenoid actuator in the partition member. Accordingly, a structure in which a recess is provided at a position where the protrusion approaches may be adopted. According to such a structure, the opposed parts that are brought close to each other when the valve body is driven by the solenoid actuator are circumferentially formed by the opening edge of the bottomed cylindrical valve body and the partition member opposed to the opening edge. Largely secured. As a result, the intended damping action by the dashpot structure can be stably obtained.

  Further, in the fluid filled engine mount according to the present invention, a coil spring is employed as the biasing means, and one end of the coil spring is accommodated inside the valve body, and the coil spring is provided by the peripheral wall portion of the valve body. Positioned in the direction perpendicular to the axis, the other end of the coil spring is supported by the partition member, and the valve body is urged toward one of the communication position and the blocking position from the opening of the peripheral wall to the bottom. Such a structure may be adopted. According to such a structure, since the coil spring is employed as the biasing means, and the coil spring is positioned in the direction perpendicular to the axis with respect to the valve body, the biasing means is realized with a simple structure. At the same time, it is advantageously supported by the valve body, and the urging force by the urging means can be applied to the valve body more reliably.

  Further, in the fluid-filled engine mount according to the present invention, the partition member is provided with a valve housing region in which the valve body is housed and disposed on the fluid flow path through the second orifice passage, and an opening is formed in the valve housing region. Close the second orifice passage by closing the fluid flow communication hole with the valve body, and open the communication hole by separating the valve body from the wall of the valve housing area by energizing the solenoid. Thus, a structure in which the second orifice passage is in a communication state may be employed. According to such a structure, the dedicated housing region for housing and arranging the valve body is formed in the partition member, so that the valve body is more stably disposed in the partition member and the second orifice passage is blocked. The communication state is more highly controlled. In addition, by changing the design and shape of the valve accommodating region and the communication hole, the cross-sectional area and length of the fluid passage through the second orifice passage are changed in design. It is possible to further improve the ease of tuning of the orifice passage and the degree of freedom.

  In the fluid-filled engine mount according to the present invention, a valve seat is provided on one displacement side of the communication position and the shut-off position of the valve body in the valve housing region, and a communication hole is formed in the valve seat. Is used to define the displacement end of one of the communicating position and shutoff position of the valve body by overlapping the valve seat, and the second orifice passage is shut off by closing the communication hole with the valve body. May be. According to such a structure, the urging force by the urging means is stably applied to the valve seat on one displacement side of the valve body, and the valve body is superimposed on this valve seat, and the communication hole is closed. As a result, the second orifice passage is blocked, so that a mode in which the valve body is positioned in the blocked state of the second orifice passage and held in this position can be realized more advantageously.

  In the fluid-filled engine mount according to the present invention, the valve body is urged by the urging means from the pressure receiving chamber side of the second orifice passage toward the equilibrium chamber side in the valve accommodating region, while the urging means The valve body abuts against the wall portion of the valve housing area on the displacement side of the urging direction due to the pressure to close the communication hole, and the pressure in the pressure receiving chamber and the equilibrium chamber is exerted on each surface in the displacement direction of the valve body. A structure is adopted in which the communication hole is in communication with the valve body against the urging force of the urging means due to the negative pressure generated in the pressure receiving chamber at the time of vibration input. Also good. According to such a structure, when a shocking or heavy load vibration is input and an excessive negative pressure is generated in the pressure receiving chamber, the valve body is displaced by the action of the negative pressure. The communication hole that constitutes a part of the fluid flow path of the second orifice passage becomes a communication state, and the pressure receiving chamber and the equilibrium chamber are short-circuited through the communication hole. As a result, the overnegative pressure state of the pressure receiving chamber is eliminated, and the generation of abnormal noise accompanying the generation of cavitation bubbles due to the maintenance of the overnegative pressure state is advantageously suppressed.

  That is, in the fluid-filled engine mount according to the present structure, a valve body having a structure in which the relative pressure between the pressure receiving chamber and the equilibrium chamber is exerted on each surface in the displacement direction is adopted. In addition to the valve body, there is no need to provide a special short-circuit mechanism for short-circuiting the pressure-receiving chamber and the equilibrium chamber under the overnegative pressure state of the pressure-receiving chamber. Accordingly, in this structure, as shown in, for example, US Pat. No. 6,921,067, a valve body having a structure in which the pressure in the pressure receiving chamber and the equilibrium chamber is hardly exerted on one surface in the displacement direction of the valve body is employed. As a result, as compared with a fluid-filled engine mount having a conventional structure in which the valve body is not equipped with a short-circuit function, an increase in the number of parts can be suppressed and an improvement in the vibration isolation effect can be achieved.

  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 embodiment of the fluid-filled engine mount 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 connected by a main rubber elastic body 16. . The first mounting bracket 12 is attached to a mounting member on the power unit side of the automobile (not shown), and the second mounting bracket 14 is attached to a mounting member on the body side of the automobile (not shown). Accordingly, the power unit is elastically supported via the engine mount 10 with respect to the vehicle body.

  1 shows the state of the engine mount 10 alone before being mounted on the vehicle, but in the mounted state on the vehicle, the shared support load of the power unit due to the suspension of the power unit is the mount axial direction ( 1, the first mounting bracket 12 and the second mounting bracket 14 are displaced toward each other in the mount axis direction, and the main rubber elastic body 16 is elastically deformed. . In addition, under such a mounted state, main vibrations to be vibrated are input substantially in the mount axis direction. In the following description, unless otherwise specified, the vertical direction refers to the vertical direction in FIG.

  More specifically, the first mounting member 12 has a truncated truncated cone shape or a cylindrical shape. Further, the central portion of the first mounting bracket 12 is provided with a screw hole 18 opened to the upper end surface, and a member on the power unit side (not shown) is screwed and fixed to the screw hole 18 via a fixing bolt. The first mounting bracket 12 is fixedly attached to the power unit.

  In addition, the second mounting bracket 14 has a large-diameter, generally cylindrical shape, and an annular outer flange-shaped portion 20 that extends outward in the direction perpendicular to the axis is formed at the upper end portion. An inner flange-like portion 22 extending inward in the direction perpendicular to the axis is formed at the lower end portion. A bracket bracket (not shown) is fixed to the second mounting bracket 14, and the bracket bracket is fixed to a vehicle body side member (not shown), so that the second mounting bracket 14 is fixed to the vehicle body. It can be fixedly attached to.

  The first mounting bracket 12 and the second mounting bracket 14 are disposed on the same central axis, and the first mounting bracket 12 is disposed on the outer flange-shaped portion 20 side of the second mounting bracket 14. The opening is opposed to the opening end face at a predetermined distance in the axial direction. A main rubber elastic body 16 is interposed between the first mounting bracket 12 and the second mounting bracket 14.

  The main rubber elastic body 16 is a thick rubber elastic body having a generally truncated truncated cone shape as a whole, and has a large-diameter recess having an inverted mortar shape opening downward in the axial direction at the lower end central portion. 24 is formed. The rubber elastic body 16 is vulcanized and bonded to the upper end portion of the main rubber elastic body 16 so that the portion from the axially intermediate portion to the lower end portion of the first mounting bracket 12 is embedded. An intermediate portion in the axial direction of the second mounting member 14 or an inner peripheral surface of the upper end portion is overlapped and vulcanized and bonded to the outer peripheral surface of the portion. Thus, the main rubber elastic body 16 is formed as an integrally vulcanized molded product integrally including the first mounting bracket 12 and the second mounting bracket 14, and one of the second mounting brackets 14 (FIG. 1, the upper opening is fluid-tightly closed by the main rubber elastic body 16. A thin seal rubber layer 26 integrally formed with the main rubber elastic body 16 is formed on the inner peripheral surface of the second mounting member 14 from the intermediate portion in the axial direction to the lower end portion. . The outer peripheral edge of the opening end surface of the large-diameter recess 24 in the main rubber elastic body 16 is positioned on the inner side in the direction perpendicular to the inner peripheral surface of the seal rubber layer 26, so that the main rubber elastic body 16 and the seal rubber An annular step portion 28 having an annular shape is formed at the boundary portion of the layer 26.

  In addition, a partition member 30 is assembled in the opening portion on the lower side in the axial direction of the second mounting bracket 14. The partition member 30 has a substantially circular block shape as a whole, and includes a partition member main body 32 and an upper plate fitting 34. The partition member 30 is preferably made of a material that is not magnetized.

  The partition member main body 32 has a substantially circular block shape, and is formed of a hard synthetic resin material in the present embodiment. In addition, a first locking groove 36 and a second locking groove 38 that extend in the circumferential direction are spaced apart from each other in the axial direction on the outer peripheral surface of the substantially central portion in the axial direction of the partition member main body 32. Is formed.

  Further, a circumferential groove 40 is formed in the outer peripheral surface of the partition member main body 32 so as to be opened. The circumferential groove 40 includes a pair of groove portions extending in the circumferential direction by a predetermined length on both sides of the partition member body 32 straddling the first and second locking grooves 36 and 38 in the axial direction. The partition member main body 32 is connected to each other by a connection hole (not shown) extending on the tunnel at one place on each circumference of the groove portion. In addition, a communication window 44 is formed through the upper end surface of the partition member main body 32 at the end opposite to the connection hole in the upper groove, which is one end in the circumferential direction of the circumferential groove 40.

  In addition, a shallow concave bottom recess 42 that opens to the lower end surface is formed in the central portion of the partition member main body 32. Further, the end of the circumferential groove 40 that is the other circumferential end of the circumferential groove 40, penetrates the portion that forms the circumferential wall portion of the lower recess 42 in the partition member main body 32 at the end opposite to the connection hole in the lower groove. Thus, a communication window 46 is formed. That is, the circumferential groove 40 and the lower recess 42 are connected to each other through the communication window 46.

  Further, a central recess 48 that opens upward is formed in a central portion above the lower recess 42 of the partition member main body 32. Thereby, in the central portion of the partition member main body 32, the portion between the bottom surface of the central recess 48 and the bottom surface of the lower recess 42 has a thin disk shape, and by this disk-shaped portion, A valve seat 50 according to the present embodiment is formed. A communication hole 52 made up of a plurality of through-holes spaced apart in the circumferential direction is provided in the radially intermediate portion or the outer peripheral portion of the valve seat 50.

  A coil member 54 as a solenoid is provided on the peripheral wall portion of the central recess 48 in the partition member main body 32. The coil member 54 includes an upper yoke 55, a lower yoke 56, and a coil 58. The upper and lower yokes 55 and 56 are formed using a ferromagnetic material such as iron, and the upper yoke 55 has a substantially annular plate shape with a circular hole in the center portion, The side yoke 56 has a cylindrical shape integrally provided with an inner flange-shaped portion extending inward in the direction perpendicular to the axis at the lower end portion of the cylindrical portion extending in the axial direction. The coil 58 is wound around the synthetic resin bobbin having a cylindrical shape continuously extending in the circumferential direction with a rectangular opening outward in the radial direction so as to fill the recess of the bobbin. By doing so, it has a substantially cylindrical shape as a whole. Such a lower yoke 56 is disposed along the stepped wall portion of the central recess 48, and the lower end portion of the bobbin of the coil 58 is axial with respect to the inner flange portion of the lower yoke 56. In addition, the outer peripheral portion of the coil 58 is overlapped with the cylindrical portion of the lower yoke 56 in a direction perpendicular to the axis. Further, the outer peripheral edge portion of the upper yoke 55 is fitted into the upper peripheral wall portion of the central recess, and the upper yoke 55 is overlapped with the upper end portion of the bobbin of the coil 58 and the upper end portion of the lower yoke in the axial direction. ing. As a result, the coil member 54 is substantially coaxial with the partition member main body 32 at the peripheral wall portion of the central recess 48 so that the upper yoke 55 and the lower yoke 56 surround the coil 58 except for the inner peripheral wall portion. It is arranged. In particular, the inner peripheral wall portion (surface) of the coil 58 and the inner peripheral edge portion (surface) of the lower yoke 56 are aligned in the direction perpendicular to the axis and extend in the axial direction, and constitute the peripheral wall surface of the central recess 48. ing. Thereby, the central recess 48 extends in a central portion of the partition member main body 32 with a substantially constant circular cross section in the axial direction.

  Further, the upper end portion of the upper yoke 55 is positioned at substantially the same height as the upper end portion of the outer peripheral portion provided around the central recess 48 of the partition member main body 32. Further, the inner peripheral edge portion of the upper yoke 55 extends inward in the direction perpendicular to the inner peripheral wall portion of the coil 58 and the inner peripheral edge portion of the lower yoke 56, and the radial intermediate portion or the outer periphery of the valve seat 50 is extended. Opposed to the part in the axial direction.

  The partition member main body 32 is provided with a lead wire 60, one end of the lead wire 60 is connected to the coil 58 inside the partition member main body 32, and the other end of the lead wire 60 is connected to the other end of the lead wire 60. The partition member main body 32 extends from the outer peripheral surface of the partition member main body to the outside and is connected to the power supply device 62. As a result, the coil 58 can be energized from the power supply device 62 through the lead wire 60. For example, a power source of an electric system of an automobile to be mounted can be suitably used as the power source device 62.

  On the upper surface of the partition member main body 32 and the upper surface of the upper yoke 55, an upper plate metal fitting 34 is superimposed. The upper plate fitting 34 has a thin and substantially disk shape, and is a highly rigid member formed of a metal material such as a steel plate. The outer diameter of the upper plate metal 34 is substantially equal to the outer diameter of the partition member main body 32. Further, a through hole 64 is provided in a substantially central portion of the upper plate metal 34 in the thickness direction (up and down in FIG. 1), and a notch-like communication is provided on the outer peripheral portion of the upper plate metal 34. A window 66 is formed. Here, the through hole 64 is made smaller than the size of the opening end surface of the central recess 48 of the partition member main body 32.

  Such an upper plate metal fitting 34 is arranged coaxially with the partition member main body 32 and overlapped on the upper surface of the partition member main body 32, whereby the partition member 30 is configured. Further, the partition member main body 32 and the upper plate metal fitting 34 are positioned in the circumferential direction by positioning means (not shown), and the communication window 66 of the upper plate metal fitting 34 is formed at one end of the circumferential groove 40 of the partition member main body 32. It is positioned at a position where it projects in the axial direction with the formed communication window 44. As such positioning means, for example, a protrusion is provided at a predetermined position in the circumferential direction on one of the upper end portion of the partition member main body 32 and the upper metal plate 34, and a through hole is provided at a predetermined position in the circumferential direction on the other side. A locking mechanism is preferably employed that is provided so as to restrict the displacement in the circumferential direction of the partition member main body 32 and the upper plate metal fitting 34 by inserting the protrusion into the through hole.

  In particular, in the assembly of the partition member main body 32 and the upper plate metal member 34, the opening of the central recess 48 of the partition member main body 32 is covered with the central part of the upper plate metal member 34, so that the central part of the partition member 30 is covered. The valve seat 50, the inner peripheral edge of the lower yoke 56, the inner peripheral wall of the coil 58, and the upper metal fitting 34 cooperate to form a valve housing area 68 that extends in a substantially constant circular cross section in the axial direction. Yes.

  A valve seat 50 is positioned at one end (downward in FIG. 1) in the axial direction of the valve housing area 68, and the valve housing area 68 and the lower side are communicated through a communication hole 52 formed in the valve seat 50. The recesses 42 are in communication with each other.

  The other end in the axial direction (upper in FIG. 1), which is positioned opposite to the valve seat 50 in the valve accommodating region 68 in the axial direction, is located at the inner peripheral portion of the upper yoke 55 and further above the center of the upper metal plate 34. The valve housing region 68 is communicated with the upper outer side of the upper plate metal 34 through the inner hole 65 of the upper yoke 55 and the through hole 64 of the upper plate metal 34.

  The partition member 30 is inserted in the axial direction from the lower opening of the second mounting bracket 14, and the outer peripheral portion of the upper plate bracket 34 is overlapped with the annular stepped portion 28 of the second mounting bracket 14, thereby separating the partition. An axial insertion end of the member 30 with respect to the second mounting bracket 14 is defined. Further, the second mounting bracket 14 is subjected to diameter reduction processing such as eight-way drawing from the outside, and the cylindrical portion from the axially intermediate portion to the lower end of the second mounting bracket 14 is an upper plate bracket. 34 and the partition member body 32 are fixed to the second mounting member 14 on the basis of being fitted and fixed to the upper end portion of the partition member main body 32 or a portion reaching the intermediate portion in the axial direction. In addition, the inner flange-like portion 22 provided at the lower end in the axial direction of the second mounting bracket 14 becomes the first locking groove of the partition member main body 32 as the second mounting bracket 14 is deformed by the diameter reduction processing. The partition member 30 is positioned and fixed in the axial direction with respect to the second mounting member 14.

  Below the partition member 30, a diaphragm 70 as a flexible film is disposed. The diaphragm 70 is formed of a thin rubber film having a sufficient slack and has a substantially circular dome shape. In addition, a fixing fitting 72 is vulcanized and bonded to the outer peripheral edge of the diaphragm 70. The fixing fitting 72 has a thin, substantially cylindrical shape, and an inner flange-like portion 74 extending inward in the radial direction is formed at an upper end portion thereof. Further, the outer peripheral edge of the diaphragm 70 is vulcanized and bonded to the inner peripheral surface or the lower end edge of the fixing bracket 72 in the axial direction, and the axial intermediate portion or the upper inner peripheral surface of the fixing bracket 72. A thin seal rubber layer 76 integrally formed with the diaphragm 70 is vulcanized and bonded over the entire surface.

  The fixing bracket 72 is extrapolated from the lower end portion of the partition member 30 in the axial direction, and the fixing bracket 72 is subjected to diameter reduction processing so that the fixing bracket 72 is fitted and fixed to the lower portion of the partition member 30 in the axial direction. Thus, the diaphragm 70 is fixedly assembled to the partition member 30. The axial insertion end of the fixing bracket 72 with respect to the partition member 30 is defined by the outer peripheral portion of the diaphragm 70 overlapping the outer peripheral side of the lower end portion of the partition member main body 32. Further, with the deformation of the fixing bracket 72 due to the diameter reduction processing, the inner flange-shaped portion 74 formed at the upper end portion of the fixing bracket 72 is engaged with the second locking groove 38 of the partition member main body 32. Thus, the diaphragm 70 is positioned and fixed in the axial direction with respect to the partition member 30 and the second mounting member 14. As is clear from the above description, in this embodiment, the diaphragm 70 is fixedly supported by the second mounting bracket 14 via the partition member 30, and below the second mounting bracket 14. Is closed fluid-tightly by the partition member 30 and the diaphragm 70.

  In this way, the partition member 30 and the diaphragm 70 are assembled into an integrally vulcanized molded product of the main rubber elastic body 16 having the first and second mounting brackets 12 and 14, so that the axial direction sandwiching the partition member 30 is interposed. On one side (the upper side in FIG. 1), a part of the wall portion is configured by the main rubber elastic body 16 in the region where the large diameter recess 24 of the main rubber elastic body 16 is closed by the partition member 30. A pressure receiving chamber 78 is formed in which pressure fluctuations are generated when vibration is input. In addition, on the other side in the axial direction with respect to the partition member 30 (downward in FIG. 1), a part of the wall portion is formed in the inner region of the fixing bracket 72 where the opening of the fixing bracket 72 is closed by the partition member 30. An equilibrium chamber 80 is formed which is configured by the diaphragm 70 and easily allows volume change. The pressure receiving chamber 78 and the equilibrium chamber 80 are filled with an incompressible fluid. For example, water, alkylene glycol, polyalkylene glycol, silicone oil, or the like is employed as the incompressible fluid to be enclosed. In order to effectively obtain a vibration isolation effect based on a fluid action such as a resonance action of the fluid. It is desirable to employ a low viscosity fluid of 0.1 Pa · s or less. Further, the incompressible fluid is sealed in the pressure receiving chamber 78 and the equilibrium chamber 80, for example, the partition member 30 for the integrally vulcanized molded product of the main rubber elastic body 16 including the first and second mounting brackets 12 and 14. Or the diaphragm 70 is preferably realized by performing the assembly in an incompressible fluid. More preferably, the partition member 30 and the diaphragm 70 are simultaneously assembled in an integrally vulcanized molded product of the main rubber elastic body 16 in an incompressible fluid, so that the inside of the large-diameter recess 24, the fixing bracket 72, etc. The problem of air remaining is eliminated, and the generation of bubbles in the pressure receiving chamber 78 and the equilibrium chamber 80 due to the residual air is suppressed.

  As the partition member 30 is assembled to the second mounting bracket 14, the upper outer peripheral surface of the partition member 30 is attached to the second mounting bracket 14 via the seal rubber layer 26 attached to the second mounting bracket 14. By being fluid-tightly superimposed on the inner peripheral surface, the upper groove portion of the circumferential groove 40 of the partition member 30 is closed fluid-tightly. Further, as the fixing bracket 72 of the diaphragm 70 is assembled to the partition member 30, the lower outer peripheral surface of the partition member 30 is connected to the inner peripheral surface of the fixing bracket 72 via the seal rubber layer 76 attached to the fixing bracket 72. By overlapping fluid tightly, the lower groove portion of the circumferential groove 40 of the partition member 30 is closed fluid tightly. As a result, the inner peripheral surface of the second mounting bracket 14, the inner peripheral surface of the fixing bracket 72, and the wall surface of the circumferential groove 40 cooperate to extend the outer peripheral portion of the partition member 30 by a predetermined length in the circumferential direction. One orifice passage 82 is formed. One end of the first orifice passage 82 is connected to the pressure receiving chamber 78 through the communication window 44 of the partition member main body 32 and the communication window 66 of the upper plate member 34, and the other end of the first orifice passage 82 is connected. The end portion is connected to the equilibrium chamber 80 through the communication window 46 of the partition member main body 32. Thereby, the pressure receiving chamber 78 and the equilibrium chamber 80 are communicated with each other through the first orifice passage 82, and fluid flow through the first orifice passage 82 is allowed between the two chambers 78, 80. It has become.

  Further, the valve accommodating region 68 provided in the partition member 30 is communicated with the pressure receiving chamber 78 through the through hole 64 of the upper plate member 34, and is communicated with the equilibrium chamber 80 through the communication hole 52 of the partition member main body 32. In the same manner as the pressure receiving chamber 78 and the equilibrium chamber 80, an incompressible fluid is sealed in the valve accommodating region 68. Here, a valve fitting 84 as a valve body is accommodated in the valve accommodating area 68.

  The valve fitting 84 is formed using a ferromagnetic material such as iron or silicon steel, and has a cylindrical tubular portion 86 extending in the axial direction and a shaft so as to close the lower end portion of the tubular portion 86. It includes a disc-shaped valve plate portion 88 extending in a right angle direction, and has a bottomed cylindrical shape as a whole. The outer diameter dimension of the valve fitting 84 is slightly smaller than the inner diameter dimension of the coil 58 or the lower yoke 56 which is the horizontal dimension of the valve accommodating region 68. Further, with respect to the height dimension extending in the mount axis direction (up and down in FIG. 1), the height dimension of the valve fitting 84 is made smaller by a predetermined size than the height dimension of the valve accommodating region 68. . Further, a through hole 90 is provided in the central portion of the valve plate portion 88 in the thickness direction.

  The valve fitting 84 is inserted in the axial direction from the opening of the central recess 48 constituting the valve accommodating region 68, and the tubular portion 86 of the valve fitting 84 extends along the peripheral wall portion of the valve accommodating region 68. It is installed. Thereby, the valve fitting 84 is positioned and arranged substantially coaxially with the coil housing 54 provided around the valve housing area 68 and the valve housing area 68. A minute gap is formed over the entire circumference between the peripheral wall portion of the valve accommodating region 68 (the inner peripheral wall portion of the coil member 54) and the tubular portion 86 of the valve fitting 84, and the existence of such a gap. The axial displacement or the like of the valve fitting 84 is preferably permitted by the above, but the size of the gap, that is, the peripheral wall portion of the valve accommodating region 68 is set so that the fluid flow through the gap is hardly generated. A separation distance between the cylindrical portions 86 is set.

  Further, the valve plate portion 88 of the valve fitting 84 is axially opposed to the valve seat 50 disposed at one end (downward in FIG. 1) of the valve accommodating region 68 in the axial direction. The opening end portion of the cylindrical portion 86 of the metal fitting 84 is opposed to the lower end portion on the inner peripheral side of the upper yoke 55 arranged at the other end portion (in FIG. 1) in the axial direction of the valve accommodating region 68 in the axial direction. It is positioned.

  Here, in the upper yoke 55 of the coil member 54 disposed in the partition member 30, the opening end portion of the tubular portion 86 of the valve fitting 84 in the axial direction (up and down in FIG. 1) that is the displacement direction of the valve fitting 84. A recess 89 is formed in a portion opposed to the. The recess 89 opens from the middle portion in the thickness direction of the upper yoke 55 toward the lower end surface and is connected to the valve storage region 68, so that the same non-resonance as the valve storage region 68 is formed inside the recess 89. A compressible fluid is enclosed. In this embodiment, the shape of the recess 89 is matched to the shape of the opening end of the cylindrical portion 86 that continuously extends in the circumferential direction with a rectangular cross section, and is a rectangular concave cross section that is slightly larger than the opening end. It extends continuously in the circumferential direction.

  Further, the height dimension of the valve fitting 84 is the same as or slightly smaller than the axial dimension between the valve seat 50 and the upper yoke 55 in the valve accommodating region 68. Accordingly, the valve fitting 84 is accommodated and disposed in the valve accommodating region 68 so as to be displaceable in the axial direction as much as the opening end portion of the tubular portion 86 of the valve fitting 84 enters the recess 89.

  In addition, the through hole 90 formed in the valve plate portion 88 of the valve fitting 84 and the communication hole 52 formed in the valve seat 50 are mutually connected in the axial direction under the arrangement state of the valve fitting 84 in the valve accommodating region 68. It is placed at a position where it is not projected.

  Here, the pressure receiving chamber 78 and the equilibrium chamber 80 are passed through the through hole 64 of the upper plate member 34, the inner hole 65 of the upper yoke 55, the valve accommodating region 68, the through hole 90 of the valve member 84, and the communication hole 52 of the valve seat 50. In the present embodiment, the second orifice passage 92 that communicates the pressure receiving chamber 78 and the equilibrium chamber 80 with each other includes the through hole 64, the inner hole 65, the valve accommodating region 68, and the through hole 90. And a communication hole 52.

  In particular, in the present embodiment, the resonance frequency of the fluid that flows through the first orifice passage 82 is effective for, for example, vibration in a low frequency region around 10 Hz corresponding to an engine shake or the like based on the resonance action of the fluid. It is tuned so as to exhibit a strong anti-vibration effect (high damping effect). On the other hand, the resonance frequency of the fluid that is caused to flow through the second orifice passage 92 is, for example, about 20 to 40 Hz corresponding to idling vibration or low-speed booming noise based on the resonance action of the fluid. It is tuned to obtain an effective anti-vibration effect against vibration. That is, the tuning frequency of the second orifice passage 92 is set to a higher frequency range than the tuning frequency of the first orifice passage 82. The tuning of the first orifice passage 82 and the second orifice passage 92 is necessary, for example, to change the rigidity of the wall springs of the pressure receiving chamber 78 and the equilibrium chamber 80, that is, to change the chambers 78 and 80 by a unit volume. This can be done by adjusting the passage length and passage cross-sectional area of each of the orifice passages 82 and 92 while taking into consideration the characteristic values based on the respective elastic deformation amounts of the main rubber elastic body 16 and the diaphragm 70 corresponding to the pressure change amount. In general, the frequency at which the phase of the pressure fluctuation transmitted through the orifice passages 82 and 92 changes to bring about a resonance state can be grasped as the tuning frequency of the orifice passages 82 and 92.

  A coil spring 94 as an urging means (biasing spring) is disposed between the upper plate member 34 and the valve member 84 in the valve accommodating region 68 in the axial direction. One end (lower side in FIG. 1) of the coil spring 94 is inserted into the valve fitting 84 and overlaps the cylindrical portion 86 in the direction perpendicular to the axis, and the valve plate of the valve fitting 84 in the axial direction. Overlaid on the portion 88. That is, the coil spring 94 is positioned in the direction perpendicular to the axis so as to be disposed on the same central axis as the valve fitting 84 by the tubular portion 86 of the valve fitting 84. Further, the other end (upper in FIG. 1) of the coil spring 94 is overlapped with the lower end around the inner hole 65 of the upper yoke 55. In this embodiment, the upper yoke 55 and the valve fitting 84 are connected to each other. It is arranged in a pre-compressed state.

  The valve fitting 84 is urged downward in the axial direction by the coil spring 94 and pressed against the valve seat 50 from above in the axial direction, whereby the displacement direction of the valve fitting 84 in the valve accommodating region 68 (this embodiment). Then, one of the displacement ends (downward in FIG. 1) is defined. Here, the through hole 90 formed in the communication hole 52 of the valve seat 50 and the valve fitting 84 is provided at a position where the projection is not projected in the axial direction, in other words, at a position different from each other in the radial direction. In a state in which the valve plate portion 88 of 84 is superposed on the valve seat 50, the communication hole 52 is closed by a central portion radially inward of the through hole 90 of the valve fitting 84, and the through hole 90 The seat 50 is closed by a radial intermediate portion or an outer peripheral portion radially outside the communication hole 52.

  Therefore, in the state where the valve plate portion 88 of the valve fitting 84 is superimposed on the valve seat 50 based on the biasing force of the coil spring 94 without energizing the coil 58, the communication between the through hole 90 of the valve fitting 84 and the valve seat 50 is established. As the hole 52 is closed, the valve accommodating region 68 and the equilibrium chamber 80 are fluid-tightly partitioned by the valve seat 50 and the valve plate portion 88, so that the second orifice passage 92 is shut off. . The shut-off state of the second orifice passage 92 refers to a state where the fluid flow action by the fluid flow path through the second orifice passage 92 between the pressure receiving chamber 78 and the equilibrium chamber 80 is not effectively generated.

  On the other hand, when the coil 58 is energized from the power supply device 62, the valve fitting 84 resists the urging force of the coil spring 94 due to the magnetic force generated between the coil member 54 and the valve fitting 84 formed of a ferromagnetic material. Thus, the suction displacement is made upward in the axial direction.

  Due to the suction displacement of the valve fitting 84, the valve plate portion 88 is separated from the valve seat 50 in the axial direction upward, so that the through hole 90 of the valve plate portion 88 and the communication hole 52 of the valve seat 50 are brought into a communication state. The valve storage area 68 and the equilibrium chamber 80 are communicated with each other. As a result, the second orifice passage 92 is brought into a communication state, and the fluid flow action by the fluid flow path through the second orifice passage 92 between the pressure receiving chamber 78 and the equilibrium chamber 80 is effectively generated. .

  In short, by controlling the power supply to the coil 58, the valve plate portion 88 of the valve fitting 84 can be displaced in the approaching direction and the separation direction with respect to the valve seat 50, and the second orifice passage 92 is blocked. It is possible to switch between the state and the communication state.

  Then, when the valve fitting 84 is sucked and displaced upward in the axial direction by energizing the coil 58, the opening end of the tubular portion 86 enters the recess 89 filled with the incompressible fluid. Since the recess 89 is slightly larger than the opening end of the cylindrical portion 86, the opening edge of the cylindrical portion 86 and the recess 89 with the cylindrical portion 86 entering the recess 89. A minute gap is formed between the portions. By causing fluid flow between the recess 89 and the valve accommodating region 68 through the minute gap, a damping effect is exhibited based on the fluid flow action of the fluid. That is, in the present embodiment, the projecting portion 95 that enters the recess 89 is formed by the opening end portion of the cylindrical portion 86, and includes the recess 89 and the projecting portion 95 in which the incompressible fluid is sealed. A damp-pot structure damping mechanism is configured.

  In particular, in the present embodiment, when the valve plate portion 88 is separated from the valve seat 50 by the action of a magnetic field generated by energization of the coil 58, the open end portion (projection portion 95) of the tubular portion 86 of the valve fitting 84 becomes the upper yoke. Thus, the power supply to the coil 58 is controlled so as to maintain the contact state. That is, the bottom of the recess 89 of the upper yoke 55 provided in the partition member 30 is configured as a stopper 96 (stopper mechanism), and the valve fitting 84 comes into contact with the stopper 96 of the partition member 30, thereby 84, the other displacement end in the displacement direction (upward in FIG. 1) of the valve accommodating region 68 is defined, and such a contact state is maintained, whereby the second orifice passage 92 is maintained in a communicating state. It is.

  Furthermore, in the present embodiment, the pressure in the pressure receiving chamber 78 is directed to the other in the displacement direction of the valve fitting 84 (upward in FIG. 1) through the through hole 64 of the upper plate fitting 34 and the inner hole 65 of the upper yoke 55. While being applied to the upper end surface (opening peripheral surface) of the cylindrical portion 86 and the other surface of the valve plate portion 88, the pressure in the equilibrium chamber 80 is applied to the valve fitting through the communication hole 52 of the partition member body 32. It is applied to one surface of the valve plate portion 88 directed to one of the 84 displacement directions (downward in FIG. 1). Then, without energizing the coil 58, the valve plate 88 is superimposed on the valve seat 50 on the basis of the urging force of the coil spring 94, and the second orifice passage 92 is shut off. When a large negative pressure is generated in the pressure receiving chamber 78 due to input or the like, and the relative pressure difference between the pressure receiving chamber 78 and the equilibrium chamber 80 increases, By applying an over-negative pressure action of the pressure receiving chamber 78 to the end face, the valve fitting 84 is separated from the valve seat 50 against the urging force of the coil spring 94 so that the second orifice passage 92 is in communication. It has become. In short, when the pressure receiving chamber 78 is in an overnegative pressure state when the coil 58 is not energized, the valve fitting 84 is displaced without causing the coil 58 to be energized, and the second orifice passage 92 is communicated. As a result, the pressure receiving chamber 78 and the equilibrium chamber 80 are short-circuited through the second orifice passage 92, and the overnegative pressure state of the pressure receiving chamber 78 shifts to a normal pressure state.

  In the automobile engine mount 10 having the above-described structure, when the automobile is running, the valve power supply 84 is attached to the valve seat by the urging force of the coil spring 94 by not energizing the coil 58 by the external power supply device 62. 50 is maintained so that the second orifice passage 92 is maintained in the shut-off state. As a result, when an engine shake that becomes a problem during driving of the automobile is input, pressure leakage through the second orifice passage 92 is prevented, and the first pressure based on the relative pressure difference between the pressure receiving chamber 78 and the equilibrium chamber 80 is prevented. The fluid flow through one orifice passage 82 is effectively generated, and the vibration isolation effect is advantageously exhibited based on the fluid action such as the resonance action of the fluid caused to flow between the pressure receiving chamber and the equilibrium chamber 90. .

  On the other hand, when the automobile is stopped, power is supplied from the outside to the coil 58 by the power supply device 62. When the coil 58 forms a magnetic field, the valve fitting 84 is attracted upward in the axial direction by the action of magnetic force. It is designed to be displaced. Then, the valve plate portion 88 of the valve fitting 84 is spaced apart from the valve seat 50 in the axial direction, and the protrusion 95 of the valve fitting 84 abuts against the stopper 96 of the partition member 30, thereby forming the valve seat 50. The communication holes 52 and the through-holes 90 formed in the valve plate portion 88 are all held in communication, and the communication state of the second orifice passage 92 is maintained. As a result, when idling vibration, which is a problem in a frequency range higher than the tuning frequency of the first orifice passage 82, is input when the automobile is stopped, the fluid flow action through the first orifice passage 82 is substantially reduced. On the other hand, a fluid action such as a resonance action by the fluid flow path through the second orifice passage 92 is effectively produced, and an excellent vibration isolation effect is obtained based on the fluid action.

  In particular, in the present embodiment, the solenoid actuator composed of the valve fitting 84 and the coil member 54 is provided in the partition member 30, so that it is not necessary to provide a new housing for housing and arranging the solenoid actuator. In addition to being able to advantageously reduce the cost based on the reduction in the number of points, the mount 10 can be advantageously made compact.

  In the present embodiment, the valve fitting 84 communicates the second orifice passage 92 from one displacement side that blocks the second orifice passage 92 against the urging force of the coil spring 94 by energization of the coil 58. By being displaced toward the other displacement side and coming into contact with the stopper 96, the other displacement end of the valve fitting 84 is defined. As a result, the shut-off state of the second orifice passage 92 is stably maintained. For example, the communication state of the second orifice passage is maintained only by separating the valve fitting from the valve seat without providing the stopper 96. Compared with the engine mount having the structure as described above, the minimum value of the electric power required to maintain the communication state can be easily set, and the use cost can be advantageously reduced.

  By the way, as described above, the solenoid-driven valve fitting 84 that is attracted and displaced in the axial direction by the action of the magnetic field generated by energization of the coil member 54 generally approaches the displacement side that is attracted and displaced from one side to the other. As the action of the magnetic field is increased, the displacement is increased. That is, in this embodiment, it is considered that the suction displacement force by the solenoid actuator increases as the valve fitting 84 moves away from the valve seat 50 and approaches the stopper 96.

  Accordingly, in the automotive engine mount 10 according to the present embodiment, the dash pot structure damping mechanism is provided on the other displacement side of the valve fitting 84, and the valve fitting 84 is positioned on the other displacement side. Based on the dampening effect of the dashpot structure dampening mechanism, the force that changes the suction force of the valve body from one side to the other can be suppressed by the solenoid actuator.

  Thus, when the valve fitting 84 comes into contact with the stopper 96, an excessive displacement force of the valve fitting 84 due to the characteristics of the solenoid actuator described above is suppressed, and the valve fitting 84 impacts or accelerates the stopper 96. A big hit is suppressed.

  In addition, since the damping mechanism is not provided on one displacement side opposite to the other displacement side on which the dashpot structure damping mechanism is provided in the displacement direction of the valve fitting 84, the valve fitting 84 has one side. The displacement is not suppressed by the damping action when positioned on the displacement side. That is, on one displacement side where the suction displacement force is smaller than the other displacement side, there is no risk of the displacement being suppressed by the dampening effect of the dashpot structure, so the valve fitting 84 is smooth from one to the other. Therefore, the transition between the communication state and the shut-off state in the second orifice passage 92 is smoothly realized.

  Therefore, in the fluid-filled engine mount 10 according to this embodiment, the accuracy of the shutoff state and the communication state of the second orifice passage accompanying the contact of the valve fitting 84 with the stopper 96 is improved, and the valve fitting 84 is Preventing the occurrence of hitting sound that becomes a problem when hitting the stopper 96 can be achieved at a high level.

  Further, in the present embodiment, by adopting the bottomed cylindrical valve fitting 84, a portion that contacts one displacement side (valve plate portion 88) and a portion that contacts the other displacement side (tubular portion) 86 and the projection 95), and the structure in which the coil spring 94 is inserted and supported can be realized compactly, the structure can be simplified, and the mount 10 can be advantageously made compact.

  In addition, in this embodiment, the urging force exerted on the valve fitting 84 by the coil spring 94 is appropriately adjusted, and when a large negative pressure is generated in the pressure receiving chamber 78 due to the input of large amplitude vibration, the coil spring 94. The valve fitting 84 that is in contact with the valve seat 50 based on the biasing force is separated from the valve seat 50 against the biasing force of the coil spring 94 by the action of negative pressure. Accordingly, the second orifice passage 92 is brought into a communication state without causing the valve fitting 84 to be sucked and displaced by energization of the coil 58, and the pressure of the pressure receiving chamber 78 and the equilibrium chamber are caused by the fluid flow through the second orifice passage 92. 80 pressure is quickly brought into equilibrium. Therefore, generation of abnormal noise and vibration due to cavitation, which is considered to be caused by an excessive negative pressure in the pressure receiving chamber 78, can be advantageously suppressed.

  Further, in the present embodiment, the height dimension of the valve fitting 84 provided with the projection 95 is higher than the height dimension of the valve accommodating region 68 with respect to the height dimension extending in the mount axis direction (up and down in FIG. 1). In a state in which the valve plate portion 88 of the valve fitting 84 abuts against the valve seat 50 and the valve fitting 84 is held at a communication position where the second orifice passage 92 communicates with the urging force of the coil spring 94. The protrusion 95 is spaced from the recess 89. Thereby, the dampening effect by the dashpot action accompanying the fitting of the protrusion 95 into the recess 89 is exhibited only when the valve fitting 84 is brought closer to the other displacement side by the solenoid actuator. As a result, the speed reduction of the switching operation of the valve fitting 84 due to the fitting of the protrusion 95 into the recess 89 is suppressed, and a quick switching operation can be realized.

  In this embodiment, the positional relationship between the protrusion 95 and the recess 89 is not limited to the above-described form. For example, the height dimension of the valve fitting 84 is stored in the valve housing with respect to the height dimension extending in the mount axis direction. The valve plate 84 of the valve fitting 84 abuts against the valve seat 50 so as to be larger than the height dimension of the region 68, and the valve fitting 84 communicates with the second orifice passage 92 by the biasing force of the coil spring 94. The protrusion 95 may enter the recess 89 while being held in position. Then, along with the drive displacement of the valve fitting 84 in the valve accommodating region 68, the protrusion 95 may be displaced along the wall portion of the recess 89 while remaining in the recess 89. As a result, interference with the peripheral wall portion of the valve housing region 68 of the valve fitting 84 and twisting displacement of the valve fitting 84 are prevented, and the operational stability of the valve fitting 84 is improved.

  As mentioned above, although one embodiment of the present invention has been described in detail, the present invention is not limited in any way by the specific description in the embodiment, and various changes, modifications, and modifications based on the knowledge of those skilled in the art. Needless to say, the present invention can be implemented in a mode with improvements and the like, and all such modes are included in the scope of the present invention without departing from the gist of the present invention.

  For example, the shape of the damping mechanism of the dashpot structure including the valve fitting 84, the partition member 30, the first orifice passage 82, the second orifice passage 92, the coil member 54, the coil spring 94, the recess 89, and the protrusion 95, etc. The form such as size, structure, number, arrangement, etc. is not limited to the illustrated form. Hereinafter, an automotive engine mount having a different form from the above-described embodiment may be described with reference to the drawings. However, members and parts having substantially the same structure as the above-described embodiment are illustrated in the drawing. By attaching the same reference numerals as those of the embodiment, detailed description thereof will be omitted.

  That is, in the above-described embodiment, the projecting portion 95 constituting a part of the damp-pot structure damping mechanism is configured by the opening end portion of the tubular portion 86 of the valve fitting 84. For example, FIG. As shown in the figure, it may be constituted by an outer flange-shaped portion 98 integrally formed at the opening end of the cylindrical portion 86, and the shape and size of the outer flange-shaped portion 98 and the recess 89 are appropriately set. By designing, the damping effect can be tuned. It is also possible to provide a dash pot structure damping mechanism on the bottom side of the valve fitting 84. Further, as described in JP-A-59-151537, when a solenoid actuator separate from the valve body is employed, a valve body such as a drive rod that exerts a driving force on the valve body. It is also possible to provide a damp-pot structure damping mechanism in a different part.

  Moreover, in the said embodiment, although the recess 89 and the protrusion 95 were all extended in the circumferential direction with the substantially constant cross section, according to the damping effect and formation space etc. which are requested | required, it is circumferential. Of course, it is possible to make the cross section different, or to partially form the damp-pot structure damping mechanism in a part or a plurality of parts on the circumference.

  Further, in the above-described embodiment, the protrusion 95 of the valve fitting 84 enters the recess 89 of the partition member 30 to exert a damping effect, and the valve fitting 84 is brought into contact with the bottom of the recess 89 while the protrusion 95 contacts the bottom of the recess 89. The displacement end on the suction displacement side by the actuator is defined, but the displacement end of the valve fitting 84 is defined by, for example, a portion of the valve fitting other than the protrusion contacting the partition member. Anyway.

  In the above-described embodiment, the communication hole 52 penetrates the valve seat 50 integrally formed with the partition member 30, the valve plate portion 88 abuts on the valve seat 50, and the communication hole 52 is formed by the valve plate portion 88. The second orifice passage 92 is brought into a communicating state by being directly covered, but, for example, one opening portion of a central hole penetrating the center of the partition member 30 in the axial direction is formed on the upper plate. The valve housing area 68 is formed by covering with the metal fitting 34 and the other opening with a flat plate-shaped valve seat metal fitting, and the radial direction of the valve metal fitting 84 on the valve seat metal fitting side in the valve housing area 68. The outwardly located gap penetrates the outer peripheral portion of the valve seat fitting and is connected to the equilibrium chamber 80, thereby forming one or more communication holes connecting the valve accommodating region 68 and the equilibrium chamber 80. The valve plate part 88 of the valve fitting 84 is in the center of the valve seat fitting. When it is contact, by which the communication hole is closed by the cylindrical portion 86 of the valve fitting 84, may be cut off state of the second orifice passage 92 is achieved.

  In the embodiment, the valve plate portion 88 of the valve fitting 84 abuts the valve seat 50 of the partition member 30 by the biasing force of the coil spring 94 and covers the communication hole 52 of the valve seat 50, thereby While the orifice passage 92 is cut off, the valve fitting 84 is attracted and displaced toward the stopper 96 against the urging force by energization of the coil 58, and comes into contact with the stopper 96. Although the state is maintained, for example, instead of providing the through hole 64 in the center of the upper plate bracket 34, the radial intermediate portion or the outer peripheral portion of the upper plate bracket 34 and the peripheral wall of the valve housing region 68 are provided. One or two or more through-holes extending continuously between the portions, and in a state in which the valve plate portion 88 is in contact with the valve seat fitting, the pressure-receiving chamber 78 of the through-hole and the valve accommodating region 68 are connected. By ensuring the second While the orifice passage 92 is brought into the communication state, the valve fitting 84 resists the urging force by being energized by the coil 58 and is sucked and displaced toward the stopper 96 to contact the stopper 96. The second orifice passage 92 can be blocked by being blocked by the cylindrical portion 86.

  Further, for example, as shown in the specification and drawings of Japanese Patent Application No. 2007-111253 filed earlier by the present applicant, it is elastic so as to cover the opening of the lower recess of the partition member. By arranging a movable rubber film that can be deformed and tuning the natural frequency of the movable rubber film to the middle to high frequency range, which is a problem for automobiles, as well as the tuning frequency of the second orifice passage, idling vibration The fluid flow through the second orifice passage may be advantageously realized by the resonant action of the movable rubber film at the time of input.

  In the above-described embodiment, the upper yoke 55 and the lower yoke 56 formed of a ferromagnetic material are disposed around the coil 58. However, the yoke is not always necessary, and is made of, for example, a nonmagnetic synthetic resin material. The coil 58 may be embedded in the partition member main body 32.

  In addition, the partition member 30 does not necessarily have a part of the outer peripheral surface exposed to the outside. For example, the partition member 30 is press-fitted into the inner peripheral side of the second mounting bracket having a cylindrical shape. It may be assembled to the mounting bracket.

  In the above embodiment, the coil member 54 and the coil spring 94 as the biasing means are provided in the partition member. However, a solenoid actuator is provided separately from the valve body that opens and closes the second orifice passage. The present invention can also be applied to a fluid-filled engine mount in which the output shaft is connected to a valve body and driven. Specifically, for example, as shown in Patent Document 1 (Japanese Patent Laid-Open No. 59-151537), a coil member (solenoid) is provided in a housing protruding from the outer peripheral surface of the second mounting member. The valve body is provided at one end of the valve shaft that is supported so as to be displaceable in the direction perpendicular to the axis with respect to the second mounting member, and the mover made of a ferromagnetic member is provided at the other end. The mover is arranged inside the coil member to constitute a solenoid actuator that operates the valve body by suction, while a coil spring that biases the valve body in a direction opposite to the suction direction by the solenoid actuator is provided, As the shaft is driven and displaced in the axial direction using the suction displacement force of the coil member and the biasing force of the coil spring, the valve element is displaced to the communication position and the blocking position of the second orifice passage. In Mel structure, it is also possible to employ a damping mechanism of the dashpot structure that operates with the displacement of the valve body in the fluid filled region.

  The opening / closing mechanism of the second orifice passage by the valve body is not limited. For example, a valve body mechanism for opening and closing an opening window extending in the radial direction as described in US Pat. No. 6,921,067 can also be employed in the present invention.

  In addition, in the above-described embodiments, specific examples of applying the present invention to an automobile engine mount have been described. However, the present invention is not limited to an automobile body mount, a differential mount, or the like, and is also used for vibration isolation of various vibrators other than an automobile. Any of them can be applied to the apparatus.

The longitudinal cross-sectional view of the engine mount for motor vehicles as one Embodiment of this invention. The longitudinal cross-sectional view of the engine mount for motor vehicles as another specific example of this invention.

Explanation of symbols

10: engine mount for automobiles, 12: first mounting bracket, 14: second mounting bracket, 16: rubber elastic body of main body, 30: partition member, 52: communication hole, 54: coil member, 58: coil, 64 : Through-hole, 65: inner hole, 68: valve accommodation area, 76: through-hole, 70: diaphragm, 78: pressure receiving chamber, 80: equilibrium chamber, 82: first orifice passage, 84: valve fitting, 89: concave 90: communication hole, 92: second orifice passage, 94: coil spring, 95: protrusion, 96: stopper

Claims (7)

A first attachment member attached to one of the power unit and the vehicle body, and a second attachment member attached to the other of the power unit and the vehicle body are connected by a rubber elastic body, and the second attachment member On both sides of the supported partition member, a pressure receiving chamber in which a part of the wall part is constituted by the main rubber elastic body and an equilibrium chamber in which a part of the wall part is constituted by a flexible film are formed, The pressure receiving chamber and the equilibrium chamber are filled with an incompressible fluid, and a first orifice passage and a second orifice passage for communicating the pressure receiving chamber and the equilibrium chamber are formed in the partition member, respectively. A valve body that tunes the second orifice passage to a higher frequency range than the first orifice passage, and is displaced to a communication position for communicating the second orifice passage and a blocking position for blocking, and the communication positions. A biasing means that biases the valve body toward one of the shut-off positions and holds the valve body in this position, and drives the valve body to the other of the communication position and the shut-off position against the biasing force of the biasing means In a fluid-filled engine mount provided with a solenoid actuator that holds in such a position,
A stopper mechanism is provided for defining the displacement end of the valve body driven by the solenoid actuator to the other side of the communication position and the shut-off position by contact, while the valve body is driven by the solenoid actuator. Opposing portions that are brought close to each other are provided in the sealed region of the incompressible fluid, and one of the facing portions opens into the facing surface to form a recess filled with the incompressible fluid, and A protrusion projecting on the opposite surface is formed on the other of the opposing portions, and the protrusion is in the recess on the other displacement side of the communicating position and the blocking position of the valve body driven by the solenoid actuator. A fluid-filled engine mount characterized by a dashpot-type damping mechanism that enters the inside.   The valve body is formed of a ferromagnetic material, and the valve body is displaceably disposed on a fluid flow path through the second orifice passage in the partition member, and a wall portion constituting the fluid flow path The urging means is disposed between the valve bodies to urge the valve body toward one of the communication position and the shut-off position, while the solenoid is arranged around the valve body in the partition member. The fluid-filled engine mount according to claim 1, wherein the solenoid actuator including the valve body, the solenoid, and the urging means is incorporated into the partition member.   The valve body has a bottomed cylindrical shape, and the protrusion is formed at the opening edge of the valve body, and the protrusion is driven by the solenoid actuator in the partition member. The fluid-filled engine mount according to claim 1, wherein the recess is provided at a position to be approached.   A coil spring is employed as the urging means, one end of the coil spring is accommodated and disposed inside the valve body, and the coil spring is positioned in a direction perpendicular to the axis by the peripheral wall portion of the valve body. The other end portion of the coil spring is supported by the partition member, and the valve body is urged toward the one of the communication position and the blocking position from the opening portion of the peripheral wall portion toward the bottom portion. 4. A fluid-filled engine mount according to 3.   The partition member is provided with a valve accommodating region in which the valve body is accommodated and disposed on the fluid flow path through the second orifice passage, and a fluid flow communication hole formed in the valve accommodating region is formed in the valve. The second orifice passage is blocked by being blocked by a body, and the valve body is separated from the wall portion of the valve accommodating region by energizing the solenoid to open the communication hole. The fluid-filled engine mount according to any one of claims 1 to 4, wherein the two orifice passages are in communication with each other.   In the valve housing region, a valve seat is provided on one displacement side of the communication position and the blocking position of the valve body, the communication hole is formed in the valve seat, and the valve body is overlapped with the valve seat. 6. In combination, the displacement end of one of the communication position and the blocking position of the valve body is defined, and the communication hole is closed by the valve body so that the second orifice passage is blocked. The fluid-filled engine mount described in 1.   In the valve housing region, the valve body is urged by the urging means from the pressure receiving chamber side of the second orifice passage toward the equilibrium chamber side, while on the urging direction side by the urging means. On the displacement side, the valve body abuts against the wall portion of the valve housing area to close the communication hole, and the pressure in the pressure receiving chamber and the equilibrium chamber is exerted on each surface in the displacement direction of the valve body. The valve body is displaced against the urging force of the urging means due to the negative pressure generated in the pressure receiving chamber when vibration is input, so that the communication hole is brought into a communication state. The fluid-filled engine mount according to claim 5 or 6.

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