JP2001041280A - Fluid-sealed type vibration control device and manufacture thereof - Google Patents

Abstract

PROBLEM TO BE SOLVED: To realize sealability of sealing fluid at a high degree through simple structure, in an insertion pole utilized as a hole for disposing the drive shaft of a rotary valve and a hole for an air passage for controlling an air pressure and formed in the cylindrical part of a second mounting member. SOLUTION: In the cylindrical part 24 of a second mounting member 14, a partition member 46 is situated in an inserted state with a seal rubber 43 located therebetween. In the partition member 46, by forming large protrusion parts on both sides in a radial direction where a through-hole 47 formed in the cylindrical part 24 is positioned, a nipping force exerted on the seal rubber 43 between the cylindrical part 24 and the partition member 46 is increased at the periphery of the through-hole.

Description

DETAILED DESCRIPTION OF THE INVENTION

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a fluid-filled type vibration damping device for obtaining a vibration damping effect by utilizing the flow action of an incompressible fluid flowing through an orifice passage, and a method of manufacturing the same. The present invention relates to a fluid-filled type vibration damping device whose vibration damping characteristics can be controlled from the outside and an advantageous manufacturing method thereof.

[0002]

2. Description of the Related Art Conventionally, a first mounting bracket and a second mounting bracket have been used as a type of a vibration isolating device such as a vibration isolating connection body and a vibration isolating support member interposed between members to be connected with vibration isolation. A fluid-filled type anti-shock device which is connected by a rubber elastic body and forms a plurality of fluid chambers mutually connected by an orifice passage so as to obtain an anti-vibration effect based on a flow action of an incompressible fluid through the orifice passage. Shaking devices are known. Also,
In order to achieve a higher vibration isolation effect, for example, Japanese Patent Application Laid-Open
JP-A-264958 and JP-A-11-22778 disclose a rotary valve for switching an orifice passage with respect to an orifice member which is inserted into a cylindrical portion of a second mounting member to form an orifice passage. A fluid-filled vibration damping device having a structure in which the vibration damping characteristics can be controlled from the outside by incorporating the same has been proposed.
In Japanese Patent Application Laid-Open No. 642 and Japanese Patent Application Laid-Open No. H10-184770, a working air chamber is formed in an orifice member which is inserted into a cylindrical portion of a second mounting member to form an orifice passage. A fluid-filled type vibration damping device having a structure in which the pressure is controlled to adjust and control the fluid flow through the orifice passage so that the vibration damping characteristics can be controlled from the outside has been proposed.

Meanwhile, in the vibration isolator incorporating the former rotary valve, it is necessary to form a hole for disposing a drive shaft that exerts a rotational driving force on the rotary valve.
Further, in the latter vibration isolator provided with a working air chamber,
It is necessary to form an air passage for applying air pressure to the working air chamber. As described in the above publication, these arrangement holes, air passages, and the like are generally provided with a control hole formed in the outer peripheral surface of the orifice member through a second mounting hole. It is constructed by opening and communicating with the outside through a through hole provided in the cylindrical part of the metal fitting.

However, in the fluid filled type vibration damping device having such a structure, the incompressible fluid sealed in the fluid chamber may leak through a through hole provided in the cylindrical portion of the second mounting member. Therefore, it is important to ensure a sufficiently stable sealing property of the sealed fluid in the insertion hole.

Therefore, for example, a thin seal rubber layer is formed on substantially the entire inner peripheral surface of the cylindrical portion of the second mounting member, and an orifice member is press-fitted into the cylindrical portion, and the cylindrical portion and the orifice are formed. It is conceivable that the sealing property of the insertion hole formed in the cylindrical portion is ensured by narrowing the pressure of the seal rubber layer between the members. However, in such a method, when a large narrow pressure is applied to the seal rubber layer between the cylindrical portion and the orifice member in order to obtain a sufficient sealing property, an extremely high part size system is required. This was not always an effective measure because, in addition to complicating the manufacturing process, the seal rubber layer was easily damaged during press-fitting, and the press-fitting of the orifice member was difficult due to the spring back of the seal rubber layer. .

It is conceivable to obtain a large narrow pressure on the seal rubber layer between the cylindrical portion and the orifice member by drawing the cylindrical portion after the insertion of the orifice member. In addition to the fact that diameter reduction such as octagonal drawing is troublesome, the shape of the second mounting bracket may be extremely effective because the diameter reduction of the cylindrical portion may be extremely difficult depending on the structure. It was not a strategy.

[0007]

The present invention has been made in view of the above-mentioned circumstances, and has as its object to solve the problems described above, including an arrangement hole for a drive shaft of a rotary valve and an air passage for air pressure control. A new fluid-filled type that can ensure sufficient and stable sealing performance of the filled fluid with a simple structure in the insertion hole of the cylindrical portion of the second mounting member used for a hole or the like. An object of the present invention is to provide a method of manufacturing a vibration isolator and a fluid-filled type vibration isolator.

[0008]

An embodiment of the present invention which has been made to solve such a problem will be described below. In addition, each aspect described below can be adopted in any combination. Further, aspects and technical features of the present invention are described in the entire specification and the drawings without being limited to those described below.
Alternatively, it should be understood that the present invention is recognized based on the inventive concept that can be grasped by those skilled in the art from the description thereof.

First, in a first aspect of the present invention relating to a fluid-filled type vibration damping device, a first mounting member is separated from a second mounting member having a cylindrical portion. The first mounting member and the second mounting member are connected by a main rubber elastic body, and an incompressible fluid is sealed therein so that the first mounting member and the second mounting member can be relatively connected at the time of vibration input. While forming a plurality of fluid chambers in which a large pressure difference is generated, an orifice member is inserted and arranged in the cylindrical portion of the second mounting member, and the outer peripheral surface of the orifice member is formed over the entire circumference of the cylindrical portion. The orifice member is closely fixed to the inner peripheral surface of the orifice member, and the orifice member forms an orifice passage communicating the plurality of fluid chambers with each other, and a control hole for externally controlling the vibration isolation characteristics of the orifice passage is formed in the orifice. Provided on the member, the second Through a through hole provided in the cylindrical portion of the mounting member, the control hole is opened to the outside. In the fluid filled type vibration damping device, between the orifice member and the cylindrical portion of the second mounting member. A seal rubber layer is provided, and the outer peripheral surface of the orifice member and the inner peripheral surface of the cylindrical portion are brought into close contact with each other all around the seal rubber layer, and the seal rubber layer is provided between the orifice member and the cylindrical portion. The present invention is characterized in that the applied compression ratio is changed in the circumferential direction to maximize the compression ratio in the radial direction where the through hole is located.

[0010] In the fluid filled type vibration damping device having the structure according to this aspect, the clamping force applied to the seal rubber layer between the orifice member and the cylindrical portion (second mounting member) is applied over the entire circumference. In the vicinity of the through hole of the cylindrical portion where fluid tightness is a problem, the compression rate of the seal rubber layer is maximized and a large clamping force is exerted. Therefore, the compressibility of the seal rubber layer is maximized in the vicinity of the through-hole of the cylindrical portion where the sealing performance of the fluid is a problem, and excellent sealing performance can be stably obtained.

In addition, by reducing the compression ratio with respect to the seal rubber layer in the portion of the cylindrical portion that is outside the through hole, even when the orifice member is press-fitted into the cylindrical portion and assembled, for example, the portion having a small compression ratio can be used. By securing a clearance space for the seal rubber layer, a large squeezing force is applied to the seal rubber layer near the through hole in the cylindrical portion while avoiding damage to the seal rubber layer and deterioration of the press-fitting operation due to springback. Thus, an effective sealing property can be obtained. Further, thereby, for example, even when it is extremely difficult to perform drawing on the cylindrical portion because the shape of the second mounting member is complicated or the like, the process is performed in the through hole of the cylindrical portion. It is possible to easily obtain an excellent sealing property without any problem.

In the first aspect, the compression rate exerted on the seal rubber layer is determined by the radial free length (free thickness) of the seal rubber layer before the orifice member is assembled to the cylindrical portion. It is the ratio of the dimension in the radial direction (the dimension in which the thickness changes) of the seal rubber layer compressed by the assembly of the orifice member to the dimension).
Further, as the specific configuration for changing the compression rate exerted on the seal rubber layer in the circumferential direction to maximize the compression rate in the radial direction where the through hole is located, various types can be adopted, but in particular, In this aspect, the second mounting member having a cylindrical portion whose inner diameter is not constant in the circumferential direction, a seal rubber layer whose inner diameter is not constant in the circumferential direction, and an orifice member whose outer diameter is not constant in the circumferential direction Advantageously, at least one of the above is adopted. That is, by employing at least one of the second mounting member, the seal rubber layer, and the orifice member, the through-hole can be formed by simply assembling the orifice member into the cylindrical portion of the second mounting member by press-fitting or the like. A configuration in which the compression ratio of the seal rubber layer is set to be the largest in the radial direction where it is located can be advantageously realized.

In the fluid filled type vibration damping device having the structure according to the first aspect, the seal rubber layer is formed by bonding to at least one of the outer peripheral surface of the orifice member and the inner peripheral surface of the cylindrical portion. This makes it possible to easily and stably arrange the seal rubber layer between the cylindrical portion and the press-contact portion of the orifice member.

[0014] In the second aspect of the present invention, particularly regarding a fluid-filled type vibration damping device, the sealing rubber layer is formed as follows.
The second mounting member is characterized in that it is bonded to the inner peripheral surface of the cylindrical portion. According to such an embodiment, the seal rubber layer can be formed more easily. For example, the seal rubber layer and the main rubber elastic body are integrally formed, and each of them is bonded and formed to the second mounting member. This also makes it possible to improve the manufacturability.

According to a third aspect of the present invention, there is provided a fluid filled type vibration damping device having a structure according to the first or second aspect, wherein the orifice member has an outer peripheral surface which penetrates the cylindrical portion. It is characterized in that a large-diameter projection projecting outward at least toward one side in the radial direction passing through the hole is formed.

According to a fourth aspect of the present invention, there is provided a fluid-filled type vibration damping device having a structure according to any one of the first to third aspects, wherein the inner peripheral surface of the cylindrical portion has The seal rubber layer is formed by bonding, and a small-diameter protrusion protruding radially inward on at least one side of both sides of the inner peripheral surface of the seal rubber layer that face each other in the radial direction passing through the through hole of the cylindrical portion. The feature is that a part is formed. In forming such a small-diameter protrusion, a cylindrical portion having an inner diameter substantially constant over the entire circumference is employed, and the thickness of the seal rubber layer provided on the inner peripheral surface is changed in the circumferential direction. Alternatively, it is also possible to make the thickness dimension of the seal rubber layer substantially constant over the entire circumference in the circumferential direction and change the inner diameter dimension of the cylindrical portion in the circumferential direction.

That is, according to the third or fourth aspect, it is advantageous that the compression rate exerted on the seal rubber layer is changed in the circumferential direction so that the compression rate is maximized in the radial direction where the through hole is located. It can be realized in.

In the third aspect, more preferably, a pair of large-diameter projections projecting outward on both sides in the radial direction passing through the through-hole of the cylindrical portion on the outer peripheral surface of the orifice member. It is formed. In the fourth aspect, more preferably, on the inner peripheral surface of the seal rubber layer provided on the cylindrical portion, a pair of inwardly projecting radially opposite sides where the through hole of the cylindrical portion is located. Is formed. This makes it possible to more stably apply a more effective clamping force to the seal rubber layer located near the through hole of the cylindrical portion. Further, when these large-diameter projections and inner-diameter projections are formed on the through-hole side of the cylindrical portion, they are formed over a larger area than the through-hole so as to cover the periphery of the through-hole. But
When formed on the side opposite to the through hole in the radial direction, it is not necessarily required to be larger than the through hole as long as an effective clamping force can be applied to the seal rubber layer around the through hole.

According to a fifth aspect of the present invention, there is provided a fluid filled type vibration damping device having a structure according to any one of the first to fourth aspects, wherein the orifice member and the cylindrical portion are arranged between the orifice member and the cylindrical portion. The maximum value of the compression ratio exerted on the seal rubber layer at the radially opposite side portions where the through holes are located is 35% to 65%.
%, And the minimum value on both sides in the radial direction perpendicular thereto is set to 4% to 10%. In such an embodiment, even better sealing properties around the through hole can be more stably secured, and even when the orifice member is press-fitted into the cylindrical portion, the The press-fitting operation can be easily performed. More preferably, the compression ratio of 35% to 65% is applied to the seal rubber layer over the entire area including the through hole and larger than the through hole in both radial portions where the through hole is located. , The compression ratio of 4% to 10% is applied to the seal rubber layer over the entire other region.

According to a sixth aspect of the present invention relating to a fluid filled type vibration damping device, in the fluid filled type vibration damping device having a structure according to any one of the first to fifth aspects, the orifice passage is opened and closed. And a drive shaft of the valve means is provided through the control hole of the orifice member and the through hole of the cylindrical portion. According to this aspect, a fluid-filled type vibration damping device capable of controlling the vibration damping characteristics by opening and closing or switching the orifice passage can be advantageously realized with excellent sealing properties of the sealed fluid. In addition, as the valve means, for example, a rotary valve that opens and closes an orifice passage by rotating around a central axis of a drive shaft provided in the control hole is preferably adopted. Also, in order to advantageously secure the assemblability of the orifice member to the cylindrical portion, it is desirable that the valve means is assembled so as not to protrude outward from the outer peripheral surface of the orifice member. For example, after assembling the orifice member to the cylindrical portion, the orifice member can be disposed by being inserted from the outside through a through hole of the cylindrical portion and connected to valve means. Furthermore, in this aspect, for example, one orifice passage is opened / closed by a valve means, the opening amount is adjusted, and the other orifices are formed across a plurality of fluid chambers and tuned differently from each other. A structure or the like in which one orifice passage and a second orifice passage are provided, and both of the orifice passages are selectively communicated by valve means,
It can be advantageously employed.

According to a seventh aspect of the present invention relating to a fluid-filled type vibration damping device, in the fluid-filled type vibration damping device having a structure according to any one of the first to sixth aspects, A first fluid chamber in which a part of the wall is configured,
A part of the wall portion is formed of a deformable elastic film and includes a second fluid chamber provided inside the orifice member;
While configuring the plurality of fluid chambers, the orifice passage includes a first orifice passage that interconnects the first fluid chamber and the second fluid chamber. A working air chamber is formed on the opposite side of the second fluid chamber, and the control hole of the orifice member allows
An air passage for controlling the air pressure of the working air chamber is configured. According to such an embodiment,
A semi-active type fluid that can control the vibration frequency by controlling the tuning frequency of the first orifice passage by controlling the air pressure of the working air chamber to emphasize the wall spring rigidity of the second fluid chamber. Active control of vibration damping characteristics by enclosing a vibration damping device or by directly controlling the internal pressure of the fluid chamber according to the vibration to be damped by actively applying air pressure fluctuation to the working air chamber An active-type fluid-filled type vibration damping device or the like can be advantageously realized with excellent sealing properties of the filled fluid. In order to advantageously secure the assemblability of the orifice member to the cylindrical portion, the control hole constituting the air passage is preferably formed without projecting from the outer peripheral surface of the orifice member. If
For example, after assembling the orifice member to the cylindrical part,
By connecting the separate air pipe to the control hole from the outside through the through hole of the cylindrical portion and fixing the same, the connection with the external air passage can be advantageously made.

According to an eighth aspect of the present invention, in a fluid-filled type vibration damping device having a structure according to any of the first to seventh aspects, the first mounting member is connected to the second mounting member. The first mounting member and the cylindrical portion are elastically connected with the main body rubber elastic body by being arranged opposite to one opening side of the cylindrical portion of the mounting member in the axial direction of the cylindrical portion. One of the openings in the axial direction of the cylindrical portion is closed in a fluid-tight manner, and the other opening in the axial direction of the cylindrical portion is closed in a fluid-tight manner by a lid member at least partially formed of a flexible film. On the other hand, the orifice member is formed in a substantially circular block shape, and a part of a wall portion is formed of the main rubber elastic body on both axial sides of the orifice member inserted and disposed in the cylindrical portion. Pressure receiving chamber where internal pressure fluctuations occur during input, and walls A plurality of fluid chambers including the pressure receiving chamber and the equilibrium chamber, and a plurality of the fluid chambers including the pressure receiving chamber and the equilibrium chamber. And a second orifice passage which communicates with the balance chamber. The orifice passage is configured to include the second orifice passage. In this embodiment, the orifice member also functions as a partition member that partitions the plurality of fluid chambers, and exhibits an effective vibration damping effect particularly against vibration input in the axial direction of the cylindrical portion. Get, eg FR
Advantageously, a fluid-filled type vibration damping device of a type suitably used for a type (front engine, rear drive type) automobile engine mount or the like is realized.

Still further, according to a ninth aspect of the present invention, in the fluid filled type vibration damping device having a structure according to any of the first to sixth aspects, the first mounting member has a substantially rod shape. At the same time, the entirety of the second mounting member is constituted by the cylindrical portion, and the second mounting member is disposed apart from the first mounting member outward in the direction perpendicular to the axis. While the main rubber elastic body is interposed between the first mounting member and the second mounting member in the direction perpendicular to the axis, the plurality of body rubber elastic bodies are interposed between the first mounting member and the second mounting member in the direction perpendicular to the axis. And the orifice member is formed in a substantially cylindrical shape, and the orifice member inserted and arranged in the second mounting member allows the orifice member to extend in the circumferential direction along the inner peripheral surface of the second mounting member. Extending the orifice passage Things, and features. In this embodiment, for example, an engine mount for an FF type (front engine, front drive type) automobile or the like, which can exhibit an effective vibration damping effect particularly against vibration input in the direction perpendicular to the axis of the cylindrical portion. The fluid-filled vibration isolator of the cylindrical type, which is preferably adopted, is advantageously realized. In the present embodiment, for example, a configuration in which a plurality of fluid chambers are disposed so as to be opposed to both sides of the first mounting member in a direction perpendicular to the axis is preferably adopted, whereby the plurality of fluid chambers are arranged. A fluid-filled cylindrical vibration damping device that can exhibit an effective vibration damping effect against vibrations that are input in the radial direction at positions facing each other is advantageously realized.

On the other hand, one aspect of the present invention relating to a method of manufacturing a fluid-filled type vibration damping device is to manufacture a fluid-filled type vibration damping device having a structure according to any of the first to ninth aspects. After the seal rubber layer is adhered to the inner peripheral surface of the cylindrical portion of the second mounting member, the orifice member is axially press-fitted and fixed to the cylindrical portion, whereby the orifice member is fixed. The compression ratio exerted on the sealing rubber layer between the cylindrical portion and the cylindrical portion is changed in the circumferential direction to maximize the compression ratio in the radial direction where the through hole is located.

According to the method of this aspect, the orifice member is simply press-fitted into the cylindrical portion of the second mounting member and assembled, without requiring special drawing or the like.
The compression rate exerted on the seal rubber layer can be set to be the largest in the radial direction where the through-hole is located, so that it is possible to easily and advantageously secure fluid tightness in the through-hole. It is.

The present invention according to each of the above-described embodiments is characterized in that one orifice passage is opened and closed and the opening degree is adjusted by rotating a rotary valve, and two or more orifice passages are selectively operated. The present invention can also be advantageously applied to a fluid-filled type vibration damping device in which opening and closing or opening degree is adjusted.
In addition to the orifice passage for which opening / closing and opening degree adjustment are performed by a rotary valve, an orifice passage which is always in communication can be formed so as to extend between the fluid chambers. By adopting such an orifice structure,
It is possible to obtain an effective vibration damping effect for a wider variety of input vibrations. In addition, as the orifice passage that is always in communication, a passage that is tuned to a lower frequency range than the orifice passage that is opened and closed by the rotary valve can be preferably used. In addition, the orifice passage that is always in communication and the orifice passage that is opened and closed by the rotary valve can be selectively operated without requiring any special switching means other than the rotary valve.

In the fluid filled type vibration damping device according to the present invention, it is possible to provide a plurality of control holes in the orifice member and a plurality of through holes in the cylindrical portion in the second mounting member. The plurality of control holes and the through holes are formed so as to open at substantially the same position on the circumference. Also,
Providing two control holes and through holes, for one of the control holes and through holes, according to the sixth embodiment,
It is also possible to arrange the drive shaft of the valve means and to form an air passage in the other control hole and the through hole according to the seventh aspect.

[0028]

DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENTS 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, FIGS. 1 to 4 show an FR-type automobile engine mount 10 as a first embodiment of the present invention. In the engine mount 10, a first mounting member 12 as a first mounting member and a second mounting member 14 as a second mounting member are arranged so as to be separated from each other and opposed to each other. It is elastically connected by the interposed main body rubber elastic body 16. The engine mount 10 is configured such that the power unit is fixedly mounted on the first mounting bracket 12 and the second mounting bracket 14, one of which is fixedly mounted on the power unit side and the other is fixedly mounted on the body side. On the other hand, it is designed to support vibration isolation. Further, under such a mounted state, the power unit weight is exerted on the engine mount 10 in a substantially vertical direction in FIG. 1 which is a substantially opposite direction of the first mounting bracket 12 and the second mounting bracket 14,
The main rubber elastic body 16 is elastically deformed in a direction in which the first mounting member 12 and the second mounting member 14 approach each other, and the first mounting member 12 and the second mounting member 1 are deformed.
4, the main vibration to be damped is input. In the following description, the vertical direction refers to the vertical direction in FIG. 1 in principle.

More specifically, the first mounting member 12 has a substantially disk shape, and has an outer peripheral edge portion which projects radially outward at one location on the circumference to form a second Mounting bracket 14
A stopper protruding portion 18 having a bent front end portion bent in a hook shape is integrally formed.
At the center of the lower surface of the first mounting member 12, a substantially cup-shaped support member 20 is overlapped and welded at the opening. Furthermore, a mounting bolt 22 protruding upward is fixed at the center of the first mounting bracket 12, and the first mounting bracket 12 is attached to a power unit (not shown) of the vehicle by the mounting bolt 22. It can be attached.

On the other hand, the second mounting member 14 is formed by a cylindrical metal member 24 as a cylindrical portion having a large-diameter substantially cylindrical shape, and a bottom metal member 26 having a large-diameter shallow-bottom substantially cylindrical shape with a bottom. I have. The cylindrical metal fitting 24 has a tapered portion 28 whose upper end in the axial direction increases in diameter upward, while a step portion 30 that expands radially outward is formed at the lower end in the axial direction. A large-diameter cylindrical caulking portion 32 extending axially downward from the outer peripheral edge of the step portion 30 is integrally formed. Further, an abutting projection 36 which is projected outward in the radial direction and reinforced by a reinforcing metal member 34 is integrally formed with the peripheral edge of the opening of the tapered portion 28 of the cylindrical metal member 24 at one location on the circumference. On the other hand, a flange-like portion 38 that extends radially outward is formed integrally with the opening periphery of the bottom fitting 26. Then, the bottom fitting 26 is superimposed on the lower opening of the tubular fitting 24, and the swaged portion 32 of the tubular fitting 24 is fixed to the flange-shaped portion 38 of the bottom fitting 26 by caulking.
The second mounting member 14 is formed to have a substantially deep, substantially bottomed cylindrical shape as a whole. At the center of the bottom of the bottom fitting 26, a mounting bolt 40 protruding downward is fixedly provided. With this mounting bolt 40, the second mounting fitting 14 is attached to an automobile body (not shown). It has become.

The second mounting member 14 is disposed so as to open upward in the axial direction, and is separated from the opening side of the second mounting member 14 so as to be separated from the first mounting member 14. The metal fitting 12 is disposed on substantially the same central axis as the second mounting metal 14. Thus, a main rubber elastic body 16 is provided between the first mounting metal 12 and the second mounting metal 14, and the first mounting metal 12 and the second Are elastically connected. The main rubber elastic body 16 has a substantially truncated conical shape as a whole, the first mounting bracket 12 is superimposed on the small diameter side end face, and the support metal fitting 20 is inserted in the axial direction from the small diameter side end face to be embedded. In the inserted state, the first mounting member 12 and the supporting member 20 are vulcanized and bonded to the main rubber elastic body 16. The outer peripheral surface of the large-diameter end portion of the main rubber elastic body 16 has a cylindrical metal fitting 2 that constitutes the second fitting 14.
4, the inner peripheral surfaces of the tapered portions 28 are overlapped and vulcanized and bonded. In short, in the present embodiment, as shown in FIGS. 5 and 6, the main rubber elastic body 16 includes the first mounting member 12, the supporting member 20, and the integrally vulcanized molded product 45 including the cylindrical member 24. The upper opening in the axial direction of the cylindrical metal fitting 24 is closed by the main rubber elastic body 16 in a fluid-tight manner.

In the integrally vulcanized molded article 45, the tapered outer peripheral surface of the support fitting 20 on the first mounting fitting 12 side and the cylindrical fitting 2 on the second mounting fitting 14 side.
The tapered portions 28 of the fourth member 4 are substantially parallel surfaces that are spaced apart from each other, and the body rubber elastic body 16 is interposed between the opposed surfaces so that a load such as the weight of the power unit is applied to the body rubber elastic body 16. On the other hand, it is made to act effectively as a compressive force. Further, in the integrally vulcanized molded article 45, the large-diameter side end face of the main rubber elastic body 16 has
A large-diameter recess 42 is formed and opened in the cylindrical metal fitting 24, and on the inner peripheral surface of the cylindrical metal fitting 24, a thin seal rubber layer 43 spreading over substantially the entire surface, An annular seal rubber projection 53 projecting in the axial direction is
Each is formed integrally with the main rubber elastic body 16. Furthermore, a cushioning rubber 44 is formed on the surface of the contact protrusion 36 of the second mounting member 14, and the stopper protrusion of the first mounting member 12 is covered so as to cover the contact protrusion 36. Section 18 is aligned. When the first mounting member 12 and the second mounting member 14 are relatively displaced by an input vibration load or the like, the stopper projection 18 is brought into contact with the contact projection 36 via the buffer rubber 44. Abut on the first mounting bracket 1
A stopper function for limiting the relative displacement amount of the second and second mounting members 14 and, consequently, the elastic deformation amount of the main rubber elastic body 16 is exerted.

Here, in particular, in such an integrally vulcanized molded product 45, the cylindrical metal fitting 24 has a substantially perfect circular shape with an axially middle portion, which occupies most of the portion, having an inner diameter: D1 (see FIG. 6). At the same time, the seal rubber layer 43, which is vulcanized and bonded to substantially the entire inner peripheral surface of the cylindrical metal fitting 24, has a substantially constant thickness throughout, so that the inner peripheral surface of the seal rubber layer 43 extends in the circumferential direction. A substantially constant inner diameter dimension over the entire circumference: D2
(See FIG. 6). Also, as described above, the inner diameter is substantially constant throughout.
In the axially intermediate portion of the cylindrical metal fitting 24, one circular through hole 47 is formed at the substantially center in the axial direction, penetrating through the cylindrical metal fitting 24 and the seal rubber layer 43 and opening to the inner and outer peripheral surfaces. ing.

Further, a partition member 46 and a diaphragm 48 as a flexible film which can be easily deformed are inserted and fitted into the integrally vulcanized molded article 45 from the axially lower opening of the cylindrical metal fitting 24 in order. , And the second mounting bracket 14. The partition member 46 as the orifice member has a substantially circular block shape having an outer peripheral surface slightly smaller in diameter than the tubular metal fitting 24. Also, the partition member 4
The outer peripheral edge of the lower end in the axial direction of 6 extends cylindrically downward in the axial direction, and the protruding tip portion is bent radially outward to integrally form a flange-shaped portion 50. . The partition member 46 is connected to the tube fitting 24.
, The outer peripheral surface is in close contact with the cylindrical metal fitting 24 via the seal rubber layer 43, and the flange-shaped portion 50 is
The bottom fitting 26 is superimposed on the step 30 of the tubular fitting 24.
By being caulked and fixed by the caulking part 32 together with the flange-shaped part 38 of the above, it is fixedly attached to the second mounting member 14. Further, the diaphragm 48 is formed of a thin rubber film that is easily deformed,
In addition to being slackened so as to be easily deformed, a substantially annular plate-shaped fixing bracket 52 is vulcanized and bonded to the outer peripheral edge. The diaphragm 48 is connected to the cylindrical fitting 24.
And the fixing bracket 52 is inserted into the stepped portion 3 of the tubular metal fitting 24.
The second mounting member 14 is attached in a state of covering the lower opening portion of the second mounting member 14 in a fluid-tight manner by being overlapped with the base member 26 and being caulked and fixed together with the flange portion 38 of the bottom metal member 26. In addition, between the fixing metal part 52 and the step part 30 of the second mounting metal part 14, the sealing rubber projection 53 is clamped to caulk and the fixing part is fluid-tightly sealed.

Thus, the openings on both sides of the cylindrical metal fitting 24 are
A fluid storage chamber 5 which is covered with a body rubber elastic body 16 and a diaphragm 48 in a fluid-tight manner and has an incompressible fluid sealed therein.
4 are formed. As the incompressible fluid to be enclosed, for example, water, alkylene glycol, polyalkylene glycol, silicone oil, or the like may be employed. A low-viscosity fluid of 0.1 Pa · s or less is suitably used. Further, the injection of the incompressible fluid can be performed simultaneously with the formation of the fluid storage chamber 54, for example, by assembling the partition member 46 and the diaphragm 48 to the integrally vulcanized molded product in the fluid. In the present embodiment, after assembling the partition member 46 and the diaphragm 48 to the integrally vulcanized molded product in the atmosphere, the vacuum is passed through the injection hole 56 formed in the fixing fitting 52 vulcanized and bonded to the diaphragm 48. The non-compressible fluid is filled by injecting the non-compressible fluid into the fluid accommodating chamber 54 by using a pull or the like as needed, and then sealing the injection hole 56 with a blind rivet 58. .

The fluid storage chamber 54 is provided in the cylindrical fitting 2.
4 is fluid-tightly divided by a partition member 46 disposed at an axially intermediate portion. Thus, on the upper side of the partition member 46, a part of the wall is formed of the main rubber elastic body 16 While a pressure receiving chamber 60 is formed as a fluid chamber, a part of the wall is
An equilibrium chamber 62 is formed as a second fluid chamber. The partition member 46 is formed of a hard material such as an aluminum alloy or a synthetic resin. That is, the pressure receiving chamber 60 includes the first mounting member 12 and the second mounting member 14.
At the time of vibration input during the period, vibration is input based on the elastic deformation of the main rubber elastic body 16 to cause a pressure change, while the volume change of the equilibrium chamber 62 is easily allowed by the deformation of the diaphragm 48. This absorbs and avoids pressure changes. An air chamber 64 is formed on the opposite side of the equilibrium chamber 62 with respect to the diaphragm 48 between the diaphragm 48 and the bottom fitting 26 to allow the deformation of the diaphragm 48.

Further, a partition member 46 for partitioning the pressure receiving chamber 60 and the equilibrium chamber 62 has a low frequency which allows the fluid flow between the two chambers 60 and 62 by allowing the pressure receiving chamber 60 and the equilibrium chamber 62 to communicate with each other. Orifice passage 66, medium frequency orifice passage 68 and high frequency orifice passage 70
They are formed substantially independently of each other. These orifice passages 66 and 6 are based on the pressure difference generated between the pressure receiving chamber 60 and the balance chamber 62 at the time of vibration input.
The generation of the fluid flow through the passages 8, 70 produces an anti-vibration effect based on the resonance action of the fluid against the input vibration in the frequency range according to the tuning of each of the orifice passages 66, 68, 70. It is supposed to be. In the present embodiment, these three orifice passages 66, 68, 70 are all formed in the pressure receiving chamber 60.
And an equilibrium chamber 62 are formed as a second orifice passage.

More specifically, first, the partition member 46 is provided with a concave groove 112 which is open on the upper surface and extends in the outer peripheral portion by a length of less than one circumference in the circumferential direction. In the figure, a thin disk-shaped lid fitting 78 is overlaid so as to cover the entire surface, and the concave groove 112 is covered with the lid fitting 78. Also, one end in the circumferential direction of the concave groove 112 is
The pressure receiving chamber 6 is formed through a communication hole 114 penetrating through the cover fitting 78.
The other end in the circumferential direction of the concave groove 112 is opened to the equilibrium chamber 62 through a connection hole 116 formed through the partition member 46 in the axial direction. As a result, including the concave groove 112, the communication hole 114, and the connection hole 116, the bridge extends between the pressure receiving chamber 60 and the equilibrium chamber 62,
A low frequency orifice passage 66 is formed to allow fluid flow between 0 and 62. In the present embodiment, the low-frequency orifice passage 66 is always formed in a communicating state.

In the present embodiment, the low frequency orifice passage 66 exerts an effective vibration damping effect (attenuation effect) against, for example, shake vibration based on the resonance action of the fluid caused to flow therein. It is tuned to be able to. Further, in the present embodiment, in particular, the low-frequency orifice passage 6 is also used for idling low-frequency vibration such as idling primary vibration whose frequency is close to the shake vibration and slightly higher in frequency range than the shake vibration.
The low-frequency orifice passage 66 is tuned in consideration of an effective vibration damping effect (low spring effect) based on the resonance action of the fluid that causes the fluid 6 to flow. In this tuning, for example, in consideration of the wall spring rigidity of the pressure receiving chamber 60 and the equilibrium chamber 62, the density of the sealed fluid, and the like, the cross-sectional area of the concave groove 112, the communication hole 114, and the connection hole 116 is A1 and the length. : L1 ratio: A1 / L1.

An upper recess 72 and a lower recess 74 are formed in the center of the upper surface and the lower surface of the partition member 46, and the lower recess 74 has a first flow restricting means as first flow restricting means. Rubber film 82 is provided. This first rubber film 8
Reference numeral 2 has a circular plate shape, and a substantially annular fixing plate metal member 84 is vulcanized and bonded to an outer peripheral edge portion thereof. The first rubber film 82 is fixed by the bolt 85,
The lower recess 7 is separated from the bottom surface of the lower recess 74 by a predetermined distance.
In a state where the opening 4 is fluid-tightly covered, the opening 4 is supported by a fixing plate metal fitting 84 and disposed in an extended state. In this arrangement state, the first rubber film 82 is allowed to be elastically deformed, and its lower surface is directly exposed to the equilibrium chamber 62.

On the other hand, the upper recess 72 is covered by a cover fitting 78, and the cover fitting 78 has opening windows 80, 80 for opening the upper recess 72 to the pressure receiving chamber 60.
Are formed. In the upper recess 72, a second rubber film 76 as a second flow rate restricting means is provided.
The second rubber film 76 has a circular plate shape thicker than the first rubber film 82, and an outer peripheral edge formed in a thick annular rib shape has an outer peripheral portion of the recess 72. In the recess 7
The center portion of the second rubber film 76 is elastically deformable in the upper recess 72 by being sandwiched between the bottom surface of the second member 2 and the cover fitting 78. Accordingly, the inside of the upper recess 72 is fluid-tightly divided into a bottom side and an opening side by the second rubber film 76, and the pressure receiving chamber is placed on the upper surface of the second rubber film 76. The internal pressure of the opening windows 80, 80
Is to be exerted through.

Here, in this embodiment, the central portion of the second rubber film 76 is thickened and substantially abuts against the bottom surface of the upper recess 72 of the partition member 46 and the lid fitting 78 to restrict displacement. In addition, the first rubber film 82 has a smaller thickness and a larger free length than the second rubber film 76. Accordingly, the first rubber film 82 has a smaller spring constant than the second rubber film 76, and elastic deformation is easily allowed. In addition, the first rubber film 82 and the second rubber film 76 are configured such that the displacement amount due to deformation is limited mainly by their own spring stiffness, and when the same pressure acts, A larger displacement is generated for the first rubber film 82 than for the second rubber film 76.

A radial hole 90 is formed in the partition member 46 as an internal passage extending straight through a middle portion in the axial direction in a diametric direction with a substantially rectangular cross section.
That is, the radial hole 90 is formed so that the inside of the partition member 46 is linearly formed in a direction substantially orthogonal to the direction in which the pressure receiving chamber 60 and the equilibrium chamber 62 face each other. It is covered with a metal fitting 24 in a fluid-tight manner. In addition, connection holes 92 and 94 are formed near both ends in the radial direction of the radial hole 90 so as to branch off from the radial hole 90 and extend in opposite axial directions. One end of the radial hole 90 is opened to the pressure receiving chamber 60 through a connection hole 92 from a window 96 formed in the cover fitting 78, and the other end of the radial hole 90 is connected to the other end of the radial hole 90. , Through the connection hole 94, the lower recess 74 is opened. Accordingly, the first rubber film 82 extends across the pressure receiving chamber 60 and the equilibrium chamber 62, including the radial hole 90, the connection holes 92 and 94, and the lower recess 74, based on the elastic deformation of the first rubber film 82. An orifice passage 68 for medium frequency is formed to allow fluid flow between the two chambers 60 and 62. In particular, in the present embodiment, the medium frequency orifice passage 68 exhibits an effective anti-vibration effect against idling high-order vibrations such as idling tertiary vibration based on the resonance action of the fluid caused to flow in the inside. Tuned to be able to. Note that, like the low frequency orifice passage 66, such tuning takes into consideration, for example, the wall spring rigidity of the pressure receiving chamber 60 and the equilibrium chamber 62, the spring rigidity of the first rubber film 82, the density of the sealed fluid, and the like.
This can be performed by adjusting the ratio of the cross-sectional area of the radial hole 90 and the connection holes 92 and 94: A2 to the length: L2: A2 / L2. Further, the amount of fluid flowing through the medium frequency orifice passage 68 is restricted by the elasticity of the first rubber film 82. Note that, in the present embodiment, A2 /
The value of L2 is set so that A1 / L1 <A2 / L2 with respect to the value of A1 / L1 in the low frequency orifice passage 66, whereby the tuning characteristics as described above are advantageously realized. Have been.

Further, the partition member 46 is formed with an axial hole 86 extending linearly with a substantially rectangular cross section on the central axis, and both sides of the axial hole 86 are formed with the upper concave portion 72 and the lower concave portion. The center of each of the locations 74 is opened. Accordingly, the first and second rubber films 82 and 76 extend over the pressure receiving chamber 60 and the equilibrium chamber 62, including the axial holes 86 and the upper and lower recesses 72 and 74. Thus, a high-frequency orifice passage 70 that allows fluid flow between the two chambers 60 and 62 is formed. In particular, in the present embodiment,
The high-frequency orifice passage 70 is tuned so as to exhibit an effective vibration-proofing effect against high-frequency vibrations such as running muffled sound based on the resonance effect of the fluid flowing through the orifice passage. The tuning is performed in the same manner as the low-frequency orifice passage 66, for example, the wall spring stiffness of the pressure receiving chamber 60 and the equilibrium chamber 62, the spring stiffness of the first and second rubber films 82 and 76, the density of the sealed fluid, and the like. In consideration of the above, the ratio of the sectional area of the axial hole 86: A3 and the length: L3:
This can be done by adjusting A3 / L3. The amount of fluid flowing through the high-frequency orifice passage 70 depends on the elasticity of the first and second rubber films 82 and 76.
In particular, the elasticity of the second rubber film 76 having a large spring constant is limited. In this embodiment, in the high frequency orifice passage 70, A3 /
The value of L3 is set such that A1 / L1 <A3 / L3 with respect to the value of A1 / L1 in the low frequency orifice passage 66, whereby the tuning characteristics as described above are advantageously realized. Have been.

In the partitioning member 46, the medium-frequency orifice passage 68 and the high-frequency orifice passage 70 intersect each other at a substantially central portion in the longitudinal direction of each passage. A valve mounting hole 100 is formed in the radial direction orthogonal to both the second and high frequency orifice passages 68 and 70 as a valve mounting hole that extends linearly through the partition member 46. A rotary valve 102 as a rotary valve is inserted into the valve mounting hole 100 and assembled. The rotary valve 102 is formed of a hard material such as a metal such as an aluminum alloy or a synthetic resin material, has a hollow bottomed cylindrical shape, and projects outward in the axial direction at the center of the bottom side. Drive shaft 10
5 are integrally formed. The valve mounting hole 10 as an assembly hole extending in the radial direction of the partition member 46 is provided.
0 and is assembled in an interpolated state. The valve mounting hole 100 has an inner diameter slightly larger than the outer diameter of the hollow cylindrical portion of the rotary valve 102, and has a smaller inner diameter at one end in the axial direction and a slightly larger inner diameter than the drive shaft 105. On the other hand, the other end in the axial direction is formed into a tapered shape to form a valve insertion portion 107. Then, the rotary valve 102 is inserted into the valve mounting hole 100 from the valve insertion portion 107 side.
Are inserted and assembled in the axial direction, and after the insertion, the valve holding plate 103 is press-fitted and fixed to the valve insertion portion 107, whereby the rotary valve 102 is inserted.
Are assembled in the valve mounting hole 100 so as not to come out in the axial direction and to be rotatable around the central axis. The drive shaft 105 of the rotary valve 102 includes:
An O-ring is externally fitted, and the O-ring seals a fluid-tight seal between the outer peripheral surface of the drive shaft 105 and the inner peripheral surface of the valve mounting hole 100.

In the cylindrical wall portion of the rotary valve 102, there are formed substantially rectangular communication holes 104, 104 penetrating inward and outward through portions facing each other in one radial direction. Depending on the position, these communication holes 104 are selectively aligned with either the opening of the radial hole 90 or the opening of the axial hole 86 in the inner peripheral surface of the valve mounting hole 100. It is made to be able to communicate.

Further, the valve mounting hole 10 of the partition member 46
The opening end of the rotary valve 102, into which the drive shaft 105 is incorporated, has a large diameter with a predetermined length in the axial direction, and is a recess 109 that opens to the outer peripheral surface of the partition member 46. The drive shaft 105 of the rotary valve 102
Are projected from the center of the bottom surface of the concave portion 109 into the concave portion 109. Further, the opening of the recess 109 is aligned with the through hole 47 of the second mounting member 14 (the cylindrical member 24), and the recess 109 is opened to the external space through the through hole 47. A stepping motor 106 is provided on the outer peripheral surface of the second mounting member 14 outside the opening side of the through hole 47. 14 (tube fitting 2
4). Then, the output shaft 110 of the stepping motor 106 is inserted into the recess 109 of the partition member 46 through the through hole 47 provided in the cylindrical metal fitting 24, and is coaxially connected to the drive shaft 105 of the rotary valve 102. ing. Thereby, the rotary valve 1
02 is rotated by the stepping motor 106 so as to communicate with the medium frequency orifice passage 68 and block the high frequency orifice passage 70, and a rotational position communicating with the high frequency orifice passage 70 and the medium frequency orifice passage. The rotation position is selectively set to a rotation position (the rotation position shown in FIGS. 1 and 2) in which the shutter 68 is shut off. The operation of the stepping motor 106 is controlled in accordance with the input state of the vibration to be damped, for example, based on a signal (for example, a speed signal or a shift position signal) corresponding to the running state of the automobile. Has become.

Therefore, in the engine mount 10 having the above-described structure, the mount anti-vibration characteristics can be changed by switching the rotation position of the rotary valve 102. As shown in the figure, the valve 102 is set at a rotational position where the pair of communication holes 104, 104 are opened on both axial sides of the partition member 46, and communicates with the high-frequency orifice passage 70, and While the orifice passage 68 is kept at the turning position to shut off, while the vehicle is stopped (idling), the rotary valve 102 is stopped.
Is rotated from the illustrated position by 90 degrees in any circumferential direction around the central axis, and is held at a rotational position where the medium-frequency orifice passage 68 is communicated and the high-frequency orifice passage 70 is shut off. .

Thus, under the running condition of the vehicle, a vibration-proof effect (vibration insulation effect) effective against high-frequency vibrations such as running muffled sound is obtained based on the resonance action of the fluid flowing through the high-frequency orifice passage 70. Based on the resonance effect of the fluid that is caused to flow through the low-frequency orifice passage 66 and is tuned to the low-frequency orifice passage 66, the vibration-proof effect (damping) that is effective against low-frequency vibrations such as shakes is produced. Effect) is exhibited. The low-frequency orifice passage 66 has a higher fluid flow resistance than the high-frequency orifice passage 70, but the second rubber film 76 restricts the fluid flow rate of the high-frequency orifice passage 70, thereby reducing the low-frequency orifice passage 70. The fluid flow through the orifice passage 66 can also advantageously be ensured.

On the other hand, when the vehicle is stopped, the pressure receiving chamber 6
Between 0 and the equilibrium chamber 62, fluid flow through the medium frequency orifice passage 68 is permitted. As a result, an effective vibration damping effect against idling vibration is exerted on the basis of the resonance action of the fluid that is caused to flow through the medium frequency orifice passage 68. In the present embodiment, the low-frequency orifice passage 66 is always in communication with the low-frequency orifice passage 68 and the amount of fluid flowing through the medium-frequency orifice passage 68 is restricted by the first rubber film 82. The fluid flow amount through the frequency orifice passage 66 is also advantageously ensured. In particular, in the present embodiment, an effective vibration damping effect against idling high-frequency vibration such as idling tertiary vibration is exhibited based on the resonance action of the fluid caused to flow through the medium frequency orifice passage 68, Based on the resonance action of the fluid flowing through the low frequency orifice passage 66, an effective vibration damping effect against idling low frequency vibration such as idling primary vibration is exerted.

The engine mount 10 of the present embodiment is
In this case, the first rubber film 82
Is provided, and the second rubber film 76 is provided on the upper surface side of the partition member 46. Therefore, the thickness and area (free length) of the first and second rubber films 82 and 76 are provided. And the like can be advantageously ensured without enlarging the partition member 46, etc., and the compatibility between the tuning freedom of the medium frequency and high frequency orifice passages 68, 70 and the compactness can be advantageously achieved. .

The low-frequency orifice passage 66 is always in communication, but is tuned to a lower frequency range than the frequency range in which the second and high-frequency orifice passages 68 and 70 exhibit an anti-vibration effect. Since the flow resistance of the low-frequency orifice passage 66 significantly increases when vibrations in the tuning frequency range of the medium-frequency and high-frequency orifice passages 68 and 70 are input, the vibration isolation effect based on the medium-frequency and high-frequency orifice passages 68 and 70 is increased. Can be exhibited effectively. Further, since the amount of fluid flowing through the medium frequency orifice passage 68 is restricted by the upper and lower rubber films 82 and 76, the amount of fluid flowing through the low frequency orifice passage 66 during traveling is sufficiently ensured, and An anti-vibration effect based on the frequency orifice passage 66 can also be effectively exhibited.

By the way, in the engine mount 10 having such a structure, it is necessary to stably secure a sufficient fluid tightness in order to stably obtain the desired vibration damping effect based on the fluid flow action. Is important. In this embodiment, in the present embodiment, the through hole 47 is formed in the cylindrical metal fitting 24 in order to exert a rotational driving force on the rotary valve 102, so that the fluid tightness due to a fluid leak or the like through the through hole 47 is obtained. Degradation tends to be a problem. In particular, in the present embodiment, a tapered portion 28, a stepped portion 30, a caulked portion 32, and the like are formed in the cylindrical metal fitting 24, and a mounting fitting 111 for mounting the bracket fitting 108 is provided on the outer peripheral surface thereof. Since it is difficult to improve the sealing performance by drawing the cylindrical fitting 24 after press-fitting the member 46, it is feared that it is difficult to secure the sealing performance between the outer peripheral surface of the partition member 46 and the inner peripheral surface of the cylindrical fitting 24. It is.

Therefore, the engine mount 1 of this embodiment is
In the case of No. 0, the following sealing structure is specially adopted in order to sufficiently secure the fluid tightness near the through hole 47.

That is, as shown in FIG. 7 and FIG. 8, the partition member 46 has a cylindrical outer peripheral surface having an outer diameter dimension: D3.
A pair of large-diameter protrusions 120, 12 protruding radially outward on the outer peripheral surface pressed against via
0 is integrally formed. Such a pair of large diameter projections 12
Reference numerals 0 and 120 are opposed to each other in a radial direction of the partition member 46 which is a rotation center axis of the rotary valve 102.
The partition member 46 has a circumferential width larger than an opening width of the concave portion 109 provided in the partition member 46 and is formed over the entire axial length of the partition member 46. Thereby, the concave portion 1 of the partition member 46 is formed.
09 is formed as a large-diameter projection 120 throughout, and the outer diameter of the partition member 46 is set to be equal to that of the rotary valve 10.
It is set to be the largest in the radial direction that is the rotation center axis of No. 2.

In short, in the present embodiment, the partition member 46
In the above, the outer diameter dimension in the radial direction which is the rotation center axis of the rotary valve 102: D4 is the outer diameter dimension in the other radial direction:
It is set to be larger than D3, and is set so as to satisfy the following expression with respect to the inner diameter dimension of the cylindrical fitting 24 in the second mounting bracket 14: D1 and the inner diameter dimension of the seal rubber layer 43: D2. It is. D2 ≦ D3 <D4 <D1

Then, the partition member 46 having such a structure is press-fitted from below in the axial direction into a separately formed integrally vulcanized molded product 45 as shown in FIGS. It is assembled by In this case, as shown in FIGS. 1 to 4, the pair of large-diameter protrusions 120, 120 are formed on the outer peripheral surface of the partition member 46, so that the partition member 46 and the tubular metal fitting 24 are separated from each other. The clamping pressure applied to the seal rubber layer 43 is made different in the circumferential direction of the seal rubber layer 43. Specifically, the compression ratio of the seal rubber layer 43 is such that the large diameter protrusion 12
0,120 is the largest at the formed portion,
In the region where the large-diameter protrusions 120 and 120 are formed in the partition member 46, a larger clamping force is applied to the seal rubber layer 43 than in the region where they are not formed.

Accordingly, in the engine mount 10 having the above-described structure, a pair of large-diameter protrusions 120 are formed at specific positions corresponding to the through holes 47 of the cylindrical member 24 in the partition member 46, and the cylindrical member 24 is formed. Since the compression ratio with respect to the seal rubber layer 43 is reduced in a portion of the metal fitting 24 that is deviated from the through hole 47 in the circumferential direction, the through hole 47 is particularly reduced.
, A large clamping pressure can be applied to the seal rubber layer 43 in a stable manner, and the stabilization of the sealing performance and the improvement of the reliability can be advantageously achieved.

Furthermore, the compression rate of the seal rubber layer 43 is reduced in the portion of the cylindrical metal fitting 24 which is circumferentially deviated from the through hole 47, so that even when the partition member 46 is press-fitted into the cylindrical metal fitting 24 and assembled. In a portion where the radial protrusion 120 is not formed and the compression ratio with respect to the seal rubber layer 43 is reduced, an escape space for the seal rubber layer 43 can be advantageously secured. Therefore, the partition member 46 is pressed into the cylindrical metal fitting 24. When assembling, seal rubber layer 4
3 can be advantageously avoided, and the partitioning member 46 can be easily and reliably press-fitted and set at the target assembling position. With a simple operation of simply press-fitting the member 46 into the cylindrical metal fitting 24, a large clamping force is effectively and stably applied to the seal rubber layer 43 around the through hole 47 provided in the cylindrical metal fitting 24. Accordingly, it is possible to stably obtain an extremely effective sealing property in the vicinity of the through-hole 47, and in the fluid storage chamber 54.

Particularly, in the present embodiment, in the region where the large-diameter protrusions 120, 120 are formed in the partition member 46, the value of the compression ratio Pa in the seal rubber layer 43 (see the following formula).
Are set so as to satisfy the following conditional expression (a), and the large-diameter protrusions 120, 120 in the partition member 46 are set.
In the region out of the range, the value of the compression ratio: Pb (see the following expression) in the seal rubber layer 43 is set so as to satisfy the following conditional expression (b). Pa = (((φD1-φD2) / 2) − ((φD1-φ
D4) / 2)) / ((φD1-φD2) / 2) Pb = (((φD1-φD2) / 2) − ((φD1-φ
D3) / 2)) / ((φD1−φD2) / 2) 35% ≦ Pa ≦ 65% ... Conditional expression (a) 4% ≤ Pb ≤ 10% ... Conditional expression (b)

That is, by satisfying such a conditional expression, the sealing rubber layer 43 is firmly sandwiched around the through hole 47 while the assembling workability by press-fitting the partition member 46 into the cylindrical fitting 24 is advantageously ensured. By pressurizing, it is possible to easily and stably obtain more excellent fluid tightness. In particular, in the present embodiment, the large-diameter protrusion 12 larger than the through hole 47 is formed with respect to the partition member 46.
By providing 0, the compression ratio that satisfies the above-mentioned conditional expression (a) could be set in the seal rubber layer 43 in a sufficiently large range around the through-hole 47, whereby a more excellent fluid You can get dense.

In manufacturing the engine mount 10 having the above-described structure, for example, the following manufacturing method is suitably adopted.

That is, under the condition that the first mounting member 12 and the second mounting member 14 are set in the molding die of the rubber elastic body 16, the molding material is filled with a rubber material and vulcanized. Thereby, the first and second mounting brackets 12,
Vulcanized molded article 45 of the main rubber elastic body 16 having
To manufacture. Separately, the rotary valve 102, the first and second rubber films 82 and 76, and the like are attached to the separately manufactured partition member 46, and the cover fitting 78 is provided.
Are mounted on each other to obtain an assembly of partition members.

Subsequently, as described above, the assembly of the partition member 46 is press-fitted into the cylindrical fitting 24 of the integrally vulcanized molded product 45 from below in the axial direction and integrally assembled. In addition,
At this time, the cylindrical member 24 and the partition member 46 are circumferentially aligned with each other so that the concave portion 109 of the partition member 46 opens through the through hole 47 of the cylindrical member 24. The axially press-fitting position of the partition member 46 into the cylindrical metal fitting 24 is such that the outer peripheral edge of the upper surface of the partition member 46 is in contact with the lower end surface of the rubber elastic body 16 and the flange member is formed integrally with the partition member 46. The portion 50 is set by abutting on the step portion 30 of the tubular metal fitting 24.

Further, after the fixing fitting 52 is press-fitted into the caulking portion 32 of the cylindrical fitting 24 and the diaphragm 48 is assembled,
An incompressible fluid is injected and filled through the injection hole 56 of the fixing bracket 52, and then the blind rivet 58 is inserted into the injection hole 56.
Seal with.

Then, the bottom fitting 26 is attached to the outside of the diaphragm 48, and the flange 38 of the bottom fitting 26 is joined to the partition member 46 by the caulking section 32 of the tubular fitting 24.
By caulking and fixing together with the flange-shaped portion 50 and the fixing bracket 52, the intended engine mount 10 can be obtained. Further, a stepping motor 106 is fixed to the second mounting bracket 14 via a bracket 108 and mounted on the engine mount 10 prior to mounting on the vehicle, and an output shaft of the stepping motor 106 is mounted. 110 is inserted inward through the through hole 47 of the cylindrical fitting 24, and in the concave portion 109 of the partition member 46, the output shaft 110 is connected to the drive shaft 105 of the rotary valve 102 protruding from the bottom of the concave portion 109. Are connected.

The filling of the non-compressible fluid into the fluid accommodating chamber 54 is performed by means of the injection hole 56 as described above. 24 is pressed into the caulking portion 32 and the fixing metal 52 is pressed against the step 30 of the cylindrical metal fitting 24 with the sealing rubber projection 53 interposed therebetween, thereby forming a sealed fluid sealing area and filling the incompressible fluid at the same time. It is also possible to enclose.

In the first embodiment, the large-diameter projections 120, 120 are formed on the outer peripheral surface of the partition member 46, so that the space between the partition member 46 and the tube fitting 24 (second mounting member 14) is increased. The compression ratio for the seal rubber layer 43 in the circumferential direction is changed in the circumferential direction. In addition, by adopting a specific configuration in the cylindrical metal fitting 24 or the seal rubber layer 43, the compression ratio for the seal rubber layer 43 in the circumferential direction is changed. It can be changed. Specific examples of the structure are sectional views corresponding to FIG.
1, respectively.

That is, in another first specific example shown in FIG. 9, the cylindrical fitting 24 has a true cylindrical shape whose inner diameter is constant over the entire circumference, as in the first embodiment. The inner diameter of the inner surface is D:
The thickness dimension of the seal rubber layer 43 formed in Step 2 is changed in the circumferential direction, so that the portion where the through hole 47 is formed and the portion opposed in the radial direction have a larger circumferential width than the through hole 47 and extend over the entire length in the axial direction. A pair of extending small-diameter protrusions 122 are formed, so that the inner diameter dimension D5 in the radial direction where the through hole 47 is located in the seal rubber layer 43 is smaller than the inner diameter dimension D2 in the other radial directions. Have been.

In the second specific example shown in FIG. 10, the inner peripheral surface of the sealing rubber layer 43 is formed in a true cylindrical shape whose inner diameter is constant in the circumferential direction. 24 has a deformed shape in the circumferential direction, and a pair of small-diameter protrusions 124, 124 extending in the axial direction with a circumferential width larger than the through-hole 47, respectively, at a portion where the through-hole 47 is formed and a radially opposite portion thereof. Has been formed,
The inner diameter dimension D6 in the radial direction where the through hole 47 is located is smaller than the inner diameter dimension D1 in the other radial directions.

Further, in the third specific example shown in FIG. 11, a pair of small-diameter protrusions 124, 124 are formed in
7 is smaller than the inner diameter dimension in the other radial direction: D1, and the seal rubber layer 43 is substantially entirely formed on the inner peripheral surface of the cylindrical fitting 24. It is formed with a constant thickness dimension.

That is, by adopting the cylindrical metal fitting 24 and the seal rubber layer 43 shown in any of the first to third embodiments, the partition member 46 is press-fitted in the axial direction to form the through hole 47. The compression ratio with respect to the seal rubber layer 43 can be set higher in the radial position than in the other radial directions, whereby the same effect as in the first embodiment can be effectively obtained. Thus, it is possible to stably secure excellent sealing performance in the through hole 47. Note that the configuration shown in these first to third specific examples includes a pair of large-diameter projections 120, 120 as shown in the first embodiment.
It is also possible to adopt in combination with the partition member 46 provided with, but it is also possible to adopt a partition member having a perfect cylindrical outer peripheral surface without the large-diameter protrusion 120, and adopts such a partition member. Even in this case, as described above, by adopting a specific configuration in the tubular metal fitting 24 and the seal rubber layer 43, the compression ratio with respect to the seal rubber layer 43 is changed in the circumferential direction, so that the effective sealing property in the portion where the through hole 47 is formed. Can be obtained.

Next, FIGS. 12 and 13 show a cylindrical mount 208 used as an engine mount for an FF type vehicle as a second embodiment of the present invention.

In these figures, 210 and 212
Are an inner cylinder fitting and an outer cylinder fitting as a first attachment member and a second attachment member, respectively, are arranged eccentrically by a predetermined amount, and serve as a main body rubber elastic body interposed therebetween. Are connected to each other by a rubber elastic body 214.

In such an engine mount, the inner cylinder fitting 210 and the outer cylinder fitting 212 are attached to one of the vehicle body side and the power unit side including the engine, and are interposed therebetween. The power unit is supported on the vehicle body for vibration isolation. In such an engine mount, the weight of the power unit is exerted between the inner and outer cylindrical fittings 210 and 212 in such a mounted state, and the rubber elastic body 214 is deformed, so that the two fittings 210 and 212 are attached.
Are positioned on substantially the same axis, and the vibration to be damped is mainly caused by the inner and outer cylindrical metal fittings 21.
0, 212 are input in a substantially eccentric direction (vertical direction in the figure).

More specifically, the inner cylindrical member 210 is formed in a hollow rod shape or a thick cylindrical shape, and a metal sleeve 216 having a substantially thin cylindrical shape is formed radially outward. It is disposed eccentrically by a predetermined distance.
A rubber elastic body 214 is interposed between the inner cylindrical fitting 210 and the metal sleeve 216, and the rubber elastic body 214 is provided between the outer peripheral surface of the inner cylindrical fitting 210 and the inner peripheral surface of the metal sleeve 216. Are formed as integral vulcanized molded articles which are respectively vulcanized and bonded.

The rubber elastic body 214 has a hollow portion 218 penetrating in the axial direction at a portion where the radial separation distance between the inner cylindrical metal fitting 210 and the metal sleeve 216 is small.
Are formed over substantially half a circumference in the circumferential direction. Thus, the tensile stress induced in the rubber elastic body 214 is reduced by the power unit weight exerted in the mounted state as described above.

Further, a first pocket portion 220 that opens radially outward is formed at a portion of the rubber elastic body 214 where the radial separation distance between the inner cylinder fitting 210 and the metal sleeve 216 is large. It is opened through a first window 222 provided in the metal sleeve 216.

On the other hand, the first pocket portion 220 is radially opposed to the first pocket portion 220 with the inner cylindrical fitting 210 interposed therebetween.
A second pocket portion 224 that opens radially outward is formed at a portion where the radial distance between the inner cylinder fitting 210 and the metal sleeve 216 is small, and a second pocket portion 224 provided on the metal sleeve 216 is formed. It is opened through a window 226. In the second pocket portion 224, the bottom wall portion 228 is thinned by the lightening portion 218 to form a flexible film that is easily elastically deformed.

Further, the metal sleeve 216 has a small diameter portion at the axial center portion and a circumferential groove 230 extending in the circumferential direction at the axial center portion. Then, the first pocket portion 220 is formed by the circumferential groove 230.
The first window 222 as an opening of the second pocket portion 2
Twenty-four second windows 226, which are openings, are connected to each other between the peripheral side edges.

Then, in the integrally vulcanized molded product having such a structure, if necessary, the metal sleeve 216 is subjected to a diameter reduction process, and the rubber elastic body 214 is preliminarily compressed. The first and second orifice halves 232 and 234, each having a substantially semi-cylindrical shape, are assembled from both sides of the first and second pocket portions 220 and 224 in the facing direction, so that the overall thickness is substantially equal. An orifice member 236 having a meat cylindrical shape is formed, and is fitted into the circumferential groove 230 of the metal sleeve 216.

The orifice member 236 has the structure shown in FIG.
As shown in FIGS. 17 to 17, the first concave groove 238 is bent on the outer peripheral surface and extends in the circumferential direction for a length of about two and a half circles.
And a second groove 244 extending in a circumferential direction with a length of substantially half a circumference with a larger cross-sectional area than the first groove 238 is formed independently of each other. And the orifice member 2
36, both ends of the first concave groove 238 are provided in the through-hole 2 provided through the bottom wall portion.
40 and 242, the first pocket portion 220 and the second pocket portion 224 are opened.
Both ends of the second concave groove 244 are connected to the first pocket portion 2 through through holes 246 and 248 provided through the bottom wall portion.
20 and the second pocket portion 224.

Further, the first orifice half body 232 provided on the side of the first pocket part 220 has a thicker center portion in the circumferential direction.
The first groove 238 and the second groove 244 have a tunnel structure extending through the first orifice half 232 in the circumferential direction.

The first orifice half body 23
A flat mounting seat 252 is formed on the outer peripheral surface of the second thick portion 250, and a central concave portion of the mounting seat 252 extends inward to form a first recess having a tunnel structure. A circular valve assembly hole 254 communicating with the groove 238 is formed.

Then, such an orifice member 236
12 and 13, the metal vulcanized molded product is press-fitted and fixed to the outer cylinder fitting 212, as shown in FIGS. The outer tube fitting 21 is fixed to the orifice member 236.
2 is externally fitted and fixed.
12 is reduced in diameter and is more firmly fitted and fixed.
Here, in the present embodiment, the second mounting member is constituted by the outer cylindrical metal fitting 212 itself having the cylindrical shape. In other words, the entire second mounting member is formed as a cylindrical portion. Of the outer cylinder 212. It should be noted that the outer cylinder fitting 212 is provided with a thin seal rubber layer 256 over substantially the entire inner peripheral surface thereof.
The space between the fitting surfaces of the outer tube fittings 6 and the outer tube fitting 212 and the space between the orifice member 236 and the outer tube fitting 212 are fluid-tightly sealed.

That is, due to the external fitting of the outer cylinder fitting 212, the openings of the first pocket portion 220 and the second pocket portion 224, the first concave groove 238 provided in the orifice member 236, and the second concave portion 238 are formed. Each of the concave grooves 244 is covered.

Then, by the first pocket portion 220,
A predetermined incompressible fluid is sealed and the inner and outer cylinder fittings 210 and 2
A pressure receiving chamber 258 in which an internal pressure fluctuation is generated based on the elastic deformation of the rubber elastic body 214 at the time of vibration input to the space 12 is formed, while a predetermined incompressible fluid is sealed by the second pocket portion 224. Thus, an equilibrium chamber 260 in which a change in volume is allowed based on the deformation of the bottom wall portion 228 is formed.
Furthermore, the pressure receiving chamber 25 is formed by the first concave groove 238.
8 and the equilibrium chamber 260 are formed with a low-frequency orifice passage 262 which communicates with each other.
4, the pressure receiving chamber 258 and the balancing chamber 26 have a larger cross-sectional area / length ratio than the low-frequency orifice passage 262.
A high-frequency orifice passage 264 communicating with zero is formed. In the present embodiment, these two orifice passages 262 and 264 are both formed as second orifice passages that connect the pressure receiving chamber and the equilibrium chamber.

The pressure receiving chamber 258 and the equilibrium chamber 26
Water, alkylene glycol, polyalkylene glycol, silicone oil, and the like are generally used as the incompressible fluid sealed in 0 as in the sealed fluid in the first embodiment. Also, the encapsulation of such a fluid can be advantageously performed, for example, by assembling the mount in the fluid.

Further, an opening window 266 as a through hole is formed in the outer cylinder fitting 212 at a position where the mounting seat 252 of the first orifice half body 232 is located. The valve assembly 268 is fixed to the mounting seat 252.

The valve assembly 268 includes a housing 274 integrally formed of a metal material or a resin material by die casting, injection molding, or the like. The housing 274 has a valve mounting hole 2 having a circular cross section at the center.
It has a substantially cylindrical shape with a bottom provided with 76, and a mounting portion 278 is integrally provided on the opening side. In addition, a pair of communication holes 282 and 282 are formed on the peripheral wall portion of the housing 274 at portions opposed to each other in the direction perpendicular to the axis.
Are formed.

The rotary valve 284 is inserted and arranged in the valve mounting hole 276 of the housing 274. The rotary valve 284 has a circular short column-shaped head 288 having a valve hole 286 penetrating in a direction perpendicular to the axis, and a rod-shaped leg 290 protruding from one side of the head 288 in the axial direction. It is composed of
Then, it is fitted into the valve mounting hole 276 of the housing 274 from the head 288 side, and is held by a holding ring 292 so as to be rotatable around the axis. That is, by rotating the rotary valve 284 in the housing 274, the communication holes 282 and 282 formed in the housing 274 are connected to each other through the valve hole 286 or blocked. . Note that the sliding surface between the outer peripheral surface of the rotary valve 284 and the inner peripheral surface (sliding contact surface) of the valve mounting hole 276 is so close as to prevent the flow of fluid therethrough.

Further, the mounting portion 278 of the housing 274
, A drive motor 300 is fixedly mounted, and an output shaft 302 of the drive motor 300 is fixed to a leg 290 of a rotary valve 284 protruded outward through an opening window 266 provided in the outer cylinder fitting 212. Have been combined. The drive motor 300 drives the rotary valve 284 to rotate around one axis which is the central axis.

Then, the valve assembly 268 as described above is used.
Is the orifice member 236 (first orifice half body 2)
32) is inserted into the valve assembly hole 254 provided in
The communication holes 282 and 282 are connected to the high frequency orifice passage 264.
Are fixed with bolts 306 and assembled.

In the engine mount 208 having the structure described above, the high frequency orifice passage 264 is controlled to open and close by rotating the rotary valve 284 about one axis. 12 and 13 show a state where the high-frequency orifice passage 264 is shut off by the rotary valve 284.

Then, the medium frequency orifice passage 264
Is closed, the pressure receiving chamber 258 and the equilibrium chamber 26
The flow of the fluid between 0 and 0 is generated exclusively through the low-frequency orifice passage 262. As a result, a vibration-proof effect (high-damping effect) against low-frequency vibrations such as shake and bounce is exhibited based on the resonance action of the fluid. Is done.

On the other hand, the high-frequency orifice passage 264
Is open, the pressure receiving chamber 258 and the equilibrium chamber 26
The flow of the fluid between 0 and 0 is mainly generated through the high-frequency orifice passage 264 having a smaller flow resistance than the low-frequency orifice passage 262, so that medium or high-frequency vibrations such as muffled sounds are generated based on the resonance action of the fluid. A vibration damping effect (low dynamic spring effect) is exhibited.

By the way, in the engine mount 208 having such a structure, it is necessary to stably secure sufficient fluid tightness in order to stably obtain an intended vibration damping effect based on the fluid flow action. Is important. Where
In the present embodiment, since the opening window 266 is formed in the outer cylinder fitting 212 in order to apply a rotational driving force to the rotary valve 284, a decrease in fluid tightness due to a fluid leak or the like through the opening window 266 is prevented. Prone to problems.

Therefore, the engine mount 2 of this embodiment is
In 08, in order to ensure sufficient fluid tightness near the opening window 266, the following sealing structure is specially adopted.

That is, as shown in FIGS. 14 to 17, the orifice member 236 has a cylindrical outer peripheral surface having an outer diameter dimension: D10. A pair of large-diameter projections 310, 310 protruding outward in the radial direction, respectively, are integrally formed on the outer peripheral surface that is pressed into contact with the intermediate member. The pair of large-diameter projections 310, 310
The orifice member 236, which is the center axis of rotation of the orifice 84, is opposed to the orifice member 236 in one radial direction.
36 has a larger circumferential width than the opening width of the valve assembly hole 254 provided in the orifice member 2.
The orifice member 236 is formed over the entire axial length of the orifice member 236 with a circumferential width larger than the mounting seat 252 provided on the orifice 36. As a result, the periphery of the valve assembly hole 254 and the mounting seat 252 of the orifice member 236 is formed as a large-diameter projection 310 over the entire circumference. The largest value is set in the radial direction.

In short, in the present embodiment, in the orifice member 236, the outer diameter dimension D11 in the radial direction serving as the rotation center axis of the rotary valve 284 is set to be larger than the outer diameter dimension D10 in the other radial directions. And the inner diameter dimension of the outer sleeve 212: D12 and the inner diameter dimension of the seal rubber layer 256 when no load is applied: D1
3 is set so as to satisfy the following expression. D13 ≦ D10 <D11 <D12 Also in this embodiment, similarly to the first embodiment, the values D10 to D13 are set so as to satisfy the compression ratio according to the following conditional expression. Is more desirable. Pa = (((φD12−φD13) / 2) − ((φD1
2-φD11) / 2)) / ((φD12-φD13) /
2) Pb = (((φD12−φD13) / 2) − ((φD1
2-φD10) / 2)) / ((φD12-φD13) /
2) 35% ≤ Pa ≤ 65% 4% ≤ Pb ≤ 10%

The orifice member 236 having such a structure is assembled by being axially press-fitted into the outer cylinder fitting 212 having the inner peripheral surface covered with the seal rubber layer 256. There, a pair of large-diameter projections 310, 310 is provided on the outer peripheral surface of the orifice member 236.
Is formed, the pinching force applied to the seal rubber layer 256 between the outer cylindrical members 212 of the orifice member 236 is made different in the circumferential direction of the seal rubber layer 256. Specifically, the compression ratio in the seal rubber layer 256 is such that the large-diameter projections 310 and 31
In the area where the large-diameter protrusions 310 and 310 are formed in the orifice member 236, the area is larger than the area where they are not formed. Nipping pressure is exerted.

Therefore, in the engine mount 208 having the above-described structure, a pair of large-diameter projections 310 are formed at specific positions corresponding to the opening windows 266 of the outer metal fitting 212 in the orifice member 236. By reducing the compression ratio with respect to the seal rubber layer 256 in a portion of the outer cylinder fitting 212 that is circumferentially deviated from the opening window 266, the seal rubber layer 2 is particularly formed near the opening window 266.
Since a large clamping force can be applied to the 56 stably, stabilization of sealing performance and improvement of reliability can be advantageously achieved similarly to the engine mount 10 in the first embodiment. It is.

In addition, at the portion of the outer cylinder fitting 212 which is circumferentially deviated from the opening window 266, the seal rubber layer 256 is formed.
Of the orifice member 23
Even in the case where the seal rubber layer 256 is press-fitted into the outer cylinder fitting 212 and assembled, the relief space of the seal rubber layer 256 can be advantageously secured in a portion where the large rubber projection 310 is not formed and the compression ratio of the seal rubber layer 256 is reduced. Therefore, when the orifice member 236 is press-fitted into the outer tube fitting 212 and assembled, damage to the seal rubber layer 256 and deterioration of the press-fitting operation due to springback are advantageously avoided, and the orifice member 236 is assembled for the purpose. The orifice member 236 can be easily press-fitted and set to the position with high accuracy. In addition, the orifice member 236 is provided on the outer cylinder fitting 212 by a simple operation of press-fitting the outer cylinder fitting 212. Around the opening window 266, the sealing rubber layer 2
A large pinching pressure can be effectively and stably applied to the valve 56, so that the extremely effective fluid tightness can be stably maintained near the opening window 266, and thus in the pressure receiving chamber 258 and the equilibrium chamber 260 as the fluid chamber. It is possible to get it.

Note that such an engine mount 208
In the above, after the integrally vulcanized molded product of the rubber elastic body 214 to which the orifice member 236 is assembled is press-fitted into the outer cylinder fitting 212, the outer cylinder fitting 21 is further subjected to an eight-way drawing process or the like.
By reducing the diameter of 2, it is possible to further improve the fluid tightness. Also, after the integrally vulcanized molded product of the rubber elastic body 214 and the orifice member 236 are inserted into the outer cylinder fitting 212, Outer cylinder fitting 212 by eight-way drawing
Of the orifice member 236 and the metal sleeve 21
6 by fitting the outer tube fitting 212 to
The seal rubber layer 256 can be pressed between the orifice member 236 or the metal sleeve 216 and the outer cylinder 212 in the radial direction.

Next, FIG. 19 shows an engine mount 318 for an FR type automobile as a third embodiment of the present invention. In the present embodiment, members and parts having the same structure as that of the first embodiment are denoted by the same reference numerals as those of the first embodiment in the drawings, so that detailed descriptions thereof will be given. Omitted.

That is, in the engine mount of the present embodiment, the partition member 320 does not include valve means for selectively communicating the plurality of orifice passages.
Instead, inside the partition member 320, a part of the wall portion is formed of the rubber elastic plate 322, and the sub liquid chamber 324,
A working air chamber 326 is provided on the opposite side of the auxiliary liquid chamber 324 with the rubber elastic plate 322 interposed therebetween. The working air chamber 326 is subjected to air pressure fluctuation through an air communication passage 328. As a result, the anti-vibration characteristics of the mount are controlled.

More specifically, the partition member 320 includes a thick disk-shaped partition member main body 330 formed of a metal such as an aluminum alloy or a rigid material such as a synthetic resin material. This partition member main body 330 is, like the partition member 46 in the first embodiment, a swaged portion 32 of the tubular metal fitting 24 at a flange-shaped portion 332 integrally formed on the outer peripheral edge at the lower end in the axial direction.
By being swaged and fixed, it is fixedly attached to the second fitting 14. An annular locking protrusion 334 having an outer dimension smaller than the outer dimension of the partition member main body 330 is provided on the upper end surface in the axial direction of the partition member 320. On the surface, a locking groove 336 extending continuously in the circumferential direction is formed. Further, a cylindrical vertical wall portion 3 protruding upward in the axial direction is provided on the inner peripheral edge
38 are integrally formed.

Further, the inner cover 340 and the outer cover 342 are integrally assembled to the partition member body 330 by being sequentially superposed from above in the axial direction. The inner lid fitting 340 has an inverted bottomed cylindrical shape that opens downward, and a locking portion 344 that is bent inward in the radial direction is integrally formed at the periphery of the opening. At the same time, an annular step portion 348 connected in the circumferential direction is provided at an axially intermediate portion of the cylindrical wall portion 346. The large-diameter cylindrical portion 350 has an opening on the side of the step 348, and the upper bottom has The small-diameter projection 352 is formed. The inner cover 340 is overlapped with the partition member main body 330 from above in the axial direction, and the locking portion 344 is attached to the partition member main body 3.
It is fixedly assembled by entering and locking the locking grooves 336 of the thirty. Also, the inner lid fitting 3
The step portion 348 of the vertical wall portion 3 of the partition member main body 330
38, a lower annular passage 354 extending circumferentially around the outer peripheral portion is formed between the partition member main body 330 and the inner cover fitting 340, and a central portion is formed at the central portion. , A large central space 356 is formed. Furthermore, the outer lid fitting 342 is
It has an inverted bottomed cylindrical shape with a diameter slightly larger than 0. The peripheral wall portion 358 of the outer lid metal member 342 is press-fitted against the large-diameter cylindrical portion 350 of the inner lid metal member 340 and fixed to the outside. As a result, the outer cover fitting 342 is
0 and thus the partition member main body 330 is integrally assembled. Further, in the assembled state, the bottom wall portion of the inner lid fitting 340 and the bottom wall portion of the outer lid fitting 342 are closely overlapped. Thereby, the inner lid fitting 3
An upper annular passage 360 is formed between the outer cover 40 and the outer lid 342 so as to extend continuously in the circumferential direction at the outer peripheral portion.
A lower annular passage 354 formed between the partition member main body 330 and the inner cover 340, and an upper annular passage 360 formed between the inner cover 340 and the outer cover 342.
Are communicated with each other at one location on the periphery, the upper annular passage 360 is communicated with the pressure receiving chamber 60 at another portion on the periphery, and the lower annular passage 354 is communicated with another portion on the periphery. In the above, the partition member main body 330 is communicated with the equilibrium chamber 62 via a connection hole 355 that passes through the inside of the partition member body 330 in the axial direction. The lower and upper annular passages 354, 36
0 forms a low-frequency orifice passage 362 as a second orifice passage that connects the pressure receiving chamber 60 and the equilibrium chamber 62 to each other.

On the other hand, the rubber elastic plate 322 as an elastic film is accommodated in a central space 356 formed between the partition member main body 330 and the inner cover fitting 340.
The rubber elastic plate 322 has a disk shape formed of a rubber elastic body, and a small-diameter inverted cup-shaped connecting metal member 364 is vulcanized and bonded to a central portion thereof, and an outer peripheral edge thereof is provided. An attachment metal fitting 366 having an annular shape with an L-shaped cross section is vulcanized and bonded to the portion. The fitting metal member 366 is press-fitted and fixed to the vertical wall portion 338 of the partition member main body 330, so that the fitting member 366 is accommodated and arranged in the central space 356 so as to expand in a direction perpendicular to the axis of the mount. The rubber elastic plate 322 is formed of a material having a thickness and a material that exerts an elastic force capable of restoring an initial shape in an expanded state against external force.

Then, the rubber elastic plate 322 allows
The central space 356 is fluid-tightly divided into two, and a sub liquid chamber 324 filled with an incompressible fluid is formed between the rubber elastic plate 322 and the inner lid 340. On the other hand, between the rubber elastic plate 322 and the partition member main body 330,
A working air chamber 326 is formed opposite to the auxiliary liquid chamber 324 with the rubber elastic plate 322 interposed therebetween. Further, a leaf spring 368 is provided in the sub liquid chamber 324,
It is accommodated and arranged above the upper part 22 so as to be separated by a predetermined distance and spread in the direction perpendicular to the axis. The outer peripheral edge of this leaf spring 368 is the stepped portion 3 between the fitting metal fitting and the 366 inner lid metal fitting 340.
48, the pressure is fixedly narrowly supported. On the other hand, an upper bottom portion of a connection fitting 364 vulcanized and bonded to the rubber elastic plate 322 is fixed by caulking to a central portion of the leaf spring 368. That is, the restoring force of the rubber elastic plate 322 to the initial state is assisted by the elastic force of the leaf spring 368. The leaf spring 368 is appropriately formed with an appropriately shaped lightening hole or the like in order to adjust the spring coefficient. Sub-liquid chambers 324 are formed substantially on both upper and lower sides of the leaf spring through the lightening holes.

The auxiliary liquid chamber 324 communicates with the pressure receiving chamber 60 through the upper annular passage 360. That is, in the present embodiment, the upper annular passage 360 forms a high-frequency orifice passage 372 as a first orifice passage that connects the pressure receiving chamber 60 and the auxiliary liquid chamber 324 to each other. Further, in the partition member main body 330, the air communication passage 32 extending radially inward from the outer peripheral surface and having an inner end portion that is in open communication with the working air chamber 326 is provided.
8 are formed. The opening of the air communication passage 328 in the partition member main body 330 is
7 and is opened to the outer peripheral surface of the cylindrical fitting 24 through the through hole 47. The air communication passage 328 has a through hole 4 formed in the cylindrical metal fitting 24.
7, a connection pipe 374 press-fitted from the outside is fixed, and the external air pipe 3 is connected via the connection pipe 374.
76 is connected.

Further, the external air pipe 376 connected to the connection pipe 374 is selectively switched between the atmosphere and the negative pressure source by a switching valve 378 and connected. In accordance with the switching operation of the valve 378, the atmospheric pressure and the negative pressure are selectively applied to the working air chamber 326. That is, in the engine mount 318 having such a structure, for example, by switching the switching valve 378 in response to the vibration to be damped, air pressure fluctuation is exerted on the working air chamber 326, and the rubber elasticity is changed. By vibrating the plate 322, a positive fluid pressure difference is generated between the auxiliary liquid chamber 324 and the pressure receiving chamber 60, and the high frequency orifice passage 37 is formed.
The active vibration damping effect can be obtained by utilizing the resonance action of the fluid which is caused to flow through 2. Alternatively, the switching valve 378 is switched according to the vibration to be damped, and the air pressure applied to the working air chamber 326 is selectively switched between the atmospheric pressure and the negative pressure, so that the wall spring rigidity of the sub liquid chamber 324 is reduced. The tuning frequency range of the high-frequency orifice passage 372 can be adjusted according to the vibration by changing it.

In the engine mount 318 according to this embodiment having the above-described structure, similarly to the first embodiment, the partition member main body 330 has radially opposite sides where the opening of the air communication passage 328 is located. The large-diameter projection 38
0 are respectively formed. Thus, an effective compressive force is applied to the seal rubber layer 43 on both radial sides where the opening of the air communication passage 328 is located. Accordingly, in the engine mount 318 according to the present embodiment, similarly to the first embodiment,
A large narrow pressure can be stably applied to the seal rubber layer 43 in the vicinity of the through hole 47, whereby leakage of the sealed fluid through the through hole 47 is effectively prevented, and the sealing property is improved. Stabilization and improved reliability can be advantageously achieved.

Further, the engine mount 31 of this embodiment
8 can also be manufactured according to the same process as in the first embodiment, so that the partition member 320 can be easily assembled by press-fitting the cylindrical member 24, and at the time of assembly, the sealing rubber layer 43 is formed. Damage and assembly failure due to springback can also be advantageously avoided, thus ensuring excellent manufacturability and stable quality,
This makes it possible to advantageously manufacture the engine mount 318, which has an excellent sealing property in the fluid-filled area.

The embodiments of the present invention have been described in detail above, but these are merely examples.
By the specific description in such an embodiment,
It is not to be construed as limiting.

For example, the number and the structure of the orifice passages interconnecting the plurality of fluid chambers are appropriately determined according to the required vibration isolation characteristics and the like, and are not limited at all. . For example, one or four or more orifice passages can be formed, and only one orifice passage can be opened / closed by a rotary valve, or three or more orifice passages can be selectively communicated / blocked,
Alternatively, it is also possible to control the opening amounts of the orifice passages. For example, by providing a plurality of valve holes in one rotary valve, a plurality of orifice passages can be simultaneously opened and closed.

In the above-described embodiment, two fluid chambers are constituted by the pressure receiving chambers 60 and 258 in which pressure changes occur at the time of vibration input and the balance chambers 62 and 260 having variable volumes. The specific configuration and number are not limited. For example, as the plurality of fluid chambers, a pair of pressure receiving chambers in which a substantially opposite pressure change (a pressure change whose phase is shifted by 180 degrees) is generated at the time of vibration input may be employed, or one or a plurality of pressure receiving chambers may be used. It is also possible to configure a fluid chamber by a plurality of equilibrium chambers.

Further, in the above embodiment, the partition member 4
6, 320 and the orifice member 236, the through-hole 47 of the cylindrical metal part 24 or the outer cylindrical metal part 212 as a cylindrical part.
A pair of large-diameter projections 120, 120, 310, 310 and 380, 380 are formed on both sides in the radial direction where the opening window 266 is located.
The protrusion 80 may be provided on only one radial side of the partition member 46 or the orifice member 236.

Further, in the cylindrical engine mount 208 according to the second embodiment, similarly to the engine mount 10 according to the first embodiment, the orifice member 236 is provided.
In addition to providing the large-diameter projection 310 on the orifice member 236, or instead of providing the large-diameter projection 310 on the orifice member 236, the small-diameter projection 1 is formed according to the configuration shown in FIGS.
It is also possible to employ a seal rubber layer 256 provided with the outer tube 22 and an outer tube fitting 212 provided with the small-diameter protrusion 124.

Further, in addition to the large-diameter projection on the orifice member, the cylindrical projection and the small-diameter projection on the seal rubber layer are:
It is not necessary to be formed integrally with each of these members, but it is also possible to form them by fixing other members.

In addition, in the above-described embodiment, a specific example in which the present invention is applied to an engine mount for an automobile is shown. However, the present invention is also applicable to a differential mount, a body mount, and the like for an automobile, or other than an automobile. It goes without saying that the present invention can be similarly applied to various vibration isolating devices and the like.

In addition, although not enumerated one by one, the present invention
Based on the knowledge of those skilled in the art, various changes, modifications, improvements, and the like can be made, and unless such embodiments depart from the spirit of the present invention.
Both are included in the scope of the present invention,
Needless to say.

[0124]

As is apparent from the above description, in the fluid filled type vibration damping device having the structure according to the present invention, the fluid tightness is improved by the through hole formed in the cylindrical portion of the second mounting member. The reduction is effectively prevented with a simple structure, whereby the sealing performance of the sealed fluid can be extremely advantageously and stably ensured, and the intended vibration damping effect has excellent durability. It is exhibited in.

Further, according to the method of the present invention, even when the above-mentioned through-hole is formed in the cylindrical portion of the second mounting member, it is easy to press-fit the orifice member or partition member into the cylindrical portion. By such an assembling operation, it is possible to advantageously and easily secure fluid tightness in the through hole.

[Brief description of the drawings]

FIG. 1 is a longitudinal sectional view showing an engine mount for a vehicle as a first embodiment of the present invention, and is a sectional view taken along a line I in FIG.
It is a figure corresponding to -I cross section.

FIG. 2 is a longitudinal sectional view of the engine mount shown in FIG. 1, and is a view corresponding to a II-II section in FIG.

FIG. 3 is a sectional view taken along the line III-III in FIG. 2;

FIG. 4 is a sectional view taken along line IV-IV in FIG. 2;

FIG. 5 is a longitudinal sectional view showing an integrally vulcanized molded product constituting the engine mount shown in FIG. 1;

6 is a sectional view taken along line VI-VI in FIG.

FIG. 7 is a plan view showing a partition member constituting the engine mount shown in FIG. 1;

8 is a view taken in the direction of arrows VIII-VIII in FIG. 7;

FIG. 9 is a cross-sectional view corresponding to FIG. 6, showing another specific example of the tube fitting that can be employed in the engine mount shown in FIG. 1;

FIG. 10 is a cross-sectional view corresponding to FIG. 6, showing still another specific example of the cylindrical metal fitting that can be employed in the engine mount shown in FIG. 1;

FIG. 11 is a cross-sectional view corresponding to FIG. 6, showing still another specific example of the tubular metal fitting that can be employed in the engine mount shown in FIG. 1;

FIG. 12 is a cross-sectional view showing a cylindrical engine mount for an automobile according to a second embodiment of the present invention.

FIG. 13 is a longitudinal sectional view of the engine mount shown in FIG.

FIG. 14 is a transverse cross-sectional view showing an orifice member used in the engine mount shown in FIG. 12;

FIG. 15 is a transverse cross-sectional view showing an outer cylinder fitting and a seal rubber layer used in the engine mount shown in FIG. 12;

FIG. 16 is a bottom view of FIG.

FIG. 17 is a left side view of FIG.

FIG. 18 is a right side view in FIG.

FIG. 19 is a longitudinal sectional view showing an automobile engine mount as a third embodiment of the present invention.

20 is a sectional view taken along the line XX-XX in FIG.

[Explanation of symbols]

 REFERENCE SIGNS LIST 10 engine mount 12 first mounting fitting 14 second mounting fitting 16 main rubber elastic body 24 cylindrical fitting 43 sealing rubber layer 45 integrally vulcanized molded product 46 partition member 47 through hole 60 pressure receiving chamber 62 equilibrium chamber 66 low frequency orifice passage 68 Medium-frequency orifice passage 70 High-frequency orifice passage 105 Drive shaft 110 Output shaft 106 Stepping motor 120 Large-diameter projection 122 Small-diameter projection 210 Inner tube fitting 212 Outer tube fitting 214 Rubber elastic body 236 Orifice member 254 Valve assembly hole 258 Pressure receiving chamber 260 Equilibrium chamber 262 Low frequency orifice passage 264 Medium frequency orifice passage 266 Opening window 268 Valve assembly 274 Housing 276 Valve mounting hole 284 Rotary valve 318 Engine mount 320 Partition member 324 Secondary liquid chamber 328 Air Communication passage 362 Low frequency orifice passage 372 High frequency orifice passage 380 Large diameter projection

Claims (10)

[Claims] 1. A first mounting member is spaced apart from a second mounting member having a cylindrical portion, and the first mounting member and the second mounting member are connected by a rubber elastic body. While forming a plurality of fluid chambers in which an incompressible fluid is sealed and a relative pressure difference is generated when vibration is input between the first mounting member and the second mounting member. An orifice member is inserted and arranged in the cylindrical portion of the second mounting member, and the outer peripheral surface of the orifice member is closely fixed to the inner peripheral surface of the cylindrical portion over the entire circumference, and the plurality of fluids are fixed by the orifice member. An orifice passage communicating the chambers with each other is formed, and a control hole for externally controlling the vibration isolation characteristics of the orifice passage is provided in the orifice member, and is provided in the cylindrical portion of the second mounting member. Through the through hole In the fluid filled type vibration damping device having a hole opened to the outside, a seal rubber layer is arranged between the orifice member and the cylindrical portion of the second mounting member, and the outer peripheral surface of the orifice member and the cylindrical portion are formed. The inner peripheral surface of the orifice member and the cylindrical portion are made to closely contact each other over the entire circumference with the sealing rubber layer interposed therebetween, and the compression rate exerted on the sealing rubber layer is changed in the circumferential direction, so that the insertion hole is A fluid filled type vibration damping device characterized by having the highest compression ratio in the radial direction where it is located. 2. The fluid filled type vibration damping device according to claim 1, wherein the seal rubber layer is formed by bonding to an inner peripheral surface of a cylindrical portion of the second mounting member. 3. An outer peripheral surface of the orifice member,
The fluid filled type vibration damping device according to claim 1 or 2, wherein a large-diameter projection projecting outward toward at least one side in a radial direction passing through the through hole of the cylindrical portion is formed. 4. The sealing rubber layer is bonded and formed on the inner peripheral surface of the cylindrical portion, and both sides of the inner peripheral surface of the sealing rubber layer which are opposed to each other in the radial direction passing through the through hole of the cylindrical portion. The fluid filled type vibration damping device according to any one of claims 1 to 3, wherein a small-diameter protrusion protruding radially inward is formed on at least one side. 5. A maximum compression ratio between the orifice member and the cylindrical portion applied to the seal rubber layer is 35% to 65% at both radial sides where the insertion hole is located.
The fluid-filled type vibration damping device according to any one of claims 1 to 4, wherein a minimum value at both sides in a radial direction orthogonal to the above is set to 4% to 10%. 6. A valve means for opening and closing the orifice passage is incorporated in the orifice member, and a drive shaft of the valve means is provided through the control hole of the orifice member and the through hole of the cylindrical portion. Claims 1 to 5
The fluid filled type vibration damping device according to any one of the above. 7. A pressure receiving chamber in which a part of a wall portion is formed by the main rubber elastic body, and a sub-liquid provided in the orifice member, wherein a part of the wall portion is formed by a deformable elastic film. A plurality of fluid chambers, and a first orifice passage that interconnects the pressure receiving chamber and the sub-liquid chamber to form the orifice passage. The working air chamber is formed on the side opposite to the auxiliary liquid chamber, and an air passage for controlling the air pressure of the working air chamber is formed by the control hole of the orifice member. Fluid-filled anti-vibration device. 8. The first mounting member is disposed so as to face one opening side of the cylindrical portion of the second mounting member in the axial direction, and the first mounting member and the cylindrical portion are connected to each other. By elastically connecting with the main rubber elastic body, one axial side of the cylindrical portion is closed fluid-tightly,
While the other opening side of the cylindrical portion in the axial direction is closed in a fluid-tight manner by a lid member at least partially formed of a flexible film, the orifice member has a substantially circular block shape, and A pressure-receiving chamber in which a part of a wall is formed of the main rubber elastic body and an internal pressure fluctuation is generated at the time of vibration input, on both sides in the axial direction with the orifice member interposed therebetween, and a part of the wall Forming a plurality of fluid chambers including the pressure receiving chamber and the equilibrium chamber, the pressure chambers and the equilibrium chamber being formed by the orifice member. The fluid-filled type vibration damping device according to any one of claims 1 to 7, wherein a second orifice passage is formed so as to communicate with each other, and the orifice passage is configured to include the second orifice passage. 9. The method according to claim 9, wherein the first mounting member has a substantially rod shape, and the second mounting member is entirely formed of the cylindrical portion. The second mounting member is disposed at a distance, and the main rubber elastic body is interposed between opposing surfaces of the first mounting member and the second mounting member in the direction perpendicular to the axis. And the plurality of fluid chambers are formed between opposed surfaces of the second mounting member in the direction perpendicular to the axis, and the orifice member is formed in a substantially cylindrical shape, and the orifice member is inserted and arranged in the second mounting member. 7. The fluid filled type vibration damping device according to claim 1, wherein the orifice passage is formed so as to extend in a circumferential direction along an inner peripheral surface of the second mounting member. 10. A manufacturing method of the fluid filled type vibration damping device according to claim 1, wherein the seal rubber layer is bonded to an inner peripheral surface of the cylindrical portion of the second mounting member. And then press-fixing the orifice member in the axial direction with respect to the cylindrical portion.