CN110030323B - Vibration-proof device - Google Patents

Vibration-proof device Download PDF

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Publication number
CN110030323B
CN110030323B CN201811532431.7A CN201811532431A CN110030323B CN 110030323 B CN110030323 B CN 110030323B CN 201811532431 A CN201811532431 A CN 201811532431A CN 110030323 B CN110030323 B CN 110030323B
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CN
China
Prior art keywords
cylindrical outer
rubber
mass
mass member
outer member
Prior art date
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Active
Application number
CN201811532431.7A
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Chinese (zh)
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CN110030323A (en
Inventor
安田恭宣
渡边佳典
古町直基
畑中桂史
市川浩幸
松原裕二
森健太郎
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Sumitomo Riko Co Ltd
Original Assignee
Sumitomo Riko Co Ltd
Toyota Motor Corp
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Publication date
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Publication of CN110030323A publication Critical patent/CN110030323A/en
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    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B60—VEHICLES IN GENERAL
    • B60K—ARRANGEMENT OR MOUNTING OF PROPULSION UNITS OR OF TRANSMISSIONS IN VEHICLES; ARRANGEMENT OR MOUNTING OF PLURAL DIVERSE PRIME-MOVERS IN VEHICLES; AUXILIARY DRIVES FOR VEHICLES; INSTRUMENTATION OR DASHBOARDS FOR VEHICLES; ARRANGEMENTS IN CONNECTION WITH COOLING, AIR INTAKE, GAS EXHAUST OR FUEL SUPPLY OF PROPULSION UNITS IN VEHICLES
    • B60K5/00—Arrangement or mounting of internal-combustion or jet-propulsion units
    • B60K5/12—Arrangement of engine supports
    • B60K5/1208—Resilient supports
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16F—SPRINGS; SHOCK-ABSORBERS; MEANS FOR DAMPING VIBRATION
    • F16F13/00—Units comprising springs of the non-fluid type as well as vibration-dampers, shock-absorbers, or fluid springs
    • F16F13/04—Units comprising springs of the non-fluid type as well as vibration-dampers, shock-absorbers, or fluid springs comprising both a plastics spring and a damper, e.g. a friction damper
    • F16F13/06—Units comprising springs of the non-fluid type as well as vibration-dampers, shock-absorbers, or fluid springs comprising both a plastics spring and a damper, e.g. a friction damper the damper being a fluid damper, e.g. the plastics spring not forming a part of the wall of the fluid chamber of the damper
    • F16F13/08—Units comprising springs of the non-fluid type as well as vibration-dampers, shock-absorbers, or fluid springs comprising both a plastics spring and a damper, e.g. a friction damper the damper being a fluid damper, e.g. the plastics spring not forming a part of the wall of the fluid chamber of the damper the plastics spring forming at least a part of the wall of the fluid chamber of the damper
    • F16F13/14—Units of the bushing type, i.e. loaded predominantly radially
    • F16F13/1481—Units of the bushing type, i.e. loaded predominantly radially characterised by features of plastic springs, e.g. presence of cavities or stiffeners; characterised by features of flexible walls of equilibration chambers, i.e. membranes
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16F—SPRINGS; SHOCK-ABSORBERS; MEANS FOR DAMPING VIBRATION
    • F16F13/00—Units comprising springs of the non-fluid type as well as vibration-dampers, shock-absorbers, or fluid springs
    • F16F13/04—Units comprising springs of the non-fluid type as well as vibration-dampers, shock-absorbers, or fluid springs comprising both a plastics spring and a damper, e.g. a friction damper
    • F16F13/06—Units comprising springs of the non-fluid type as well as vibration-dampers, shock-absorbers, or fluid springs comprising both a plastics spring and a damper, e.g. a friction damper the damper being a fluid damper, e.g. the plastics spring not forming a part of the wall of the fluid chamber of the damper
    • F16F13/08—Units comprising springs of the non-fluid type as well as vibration-dampers, shock-absorbers, or fluid springs comprising both a plastics spring and a damper, e.g. a friction damper the damper being a fluid damper, e.g. the plastics spring not forming a part of the wall of the fluid chamber of the damper the plastics spring forming at least a part of the wall of the fluid chamber of the damper
    • F16F13/14—Units of the bushing type, i.e. loaded predominantly radially
    • F16F13/16—Units of the bushing type, i.e. loaded predominantly radially specially adapted for receiving axial loads
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16F—SPRINGS; SHOCK-ABSORBERS; MEANS FOR DAMPING VIBRATION
    • F16F15/00—Suppression of vibrations in systems; Means or arrangements for avoiding or reducing out-of-balance forces, e.g. due to motion
    • F16F15/02—Suppression of vibrations of non-rotating, e.g. reciprocating systems; Suppression of vibrations of rotating systems by use of members not moving with the rotating systems
    • F16F15/022—Suppression of vibrations of non-rotating, e.g. reciprocating systems; Suppression of vibrations of rotating systems by use of members not moving with the rotating systems using dampers and springs in combination
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16F—SPRINGS; SHOCK-ABSORBERS; MEANS FOR DAMPING VIBRATION
    • F16F15/00—Suppression of vibrations in systems; Means or arrangements for avoiding or reducing out-of-balance forces, e.g. due to motion
    • F16F15/02—Suppression of vibrations of non-rotating, e.g. reciprocating systems; Suppression of vibrations of rotating systems by use of members not moving with the rotating systems
    • F16F15/023—Suppression of vibrations of non-rotating, e.g. reciprocating systems; Suppression of vibrations of rotating systems by use of members not moving with the rotating systems using fluid means
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16F—SPRINGS; SHOCK-ABSORBERS; MEANS FOR DAMPING VIBRATION
    • F16F15/00—Suppression of vibrations in systems; Means or arrangements for avoiding or reducing out-of-balance forces, e.g. due to motion
    • F16F15/02—Suppression of vibrations of non-rotating, e.g. reciprocating systems; Suppression of vibrations of rotating systems by use of members not moving with the rotating systems
    • F16F15/04—Suppression of vibrations of non-rotating, e.g. reciprocating systems; Suppression of vibrations of rotating systems by use of members not moving with the rotating systems using elastic means
    • F16F15/08—Suppression of vibrations of non-rotating, e.g. reciprocating systems; Suppression of vibrations of rotating systems by use of members not moving with the rotating systems using elastic means with rubber springs ; with springs made of rubber and metal
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16F—SPRINGS; SHOCK-ABSORBERS; MEANS FOR DAMPING VIBRATION
    • F16F2222/00—Special physical effects, e.g. nature of damping effects
    • F16F2222/08—Inertia
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16F—SPRINGS; SHOCK-ABSORBERS; MEANS FOR DAMPING VIBRATION
    • F16F2228/00—Functional characteristics, e.g. variability, frequency-dependence
    • F16F2228/06—Stiffness

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Physics & Mathematics (AREA)
  • Acoustics & Sound (AREA)
  • Aviation & Aerospace Engineering (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Transportation (AREA)
  • Combined Devices Of Dampers And Springs (AREA)
  • Arrangement Or Mounting Of Propulsion Units For Vehicles (AREA)
  • Vibration Prevention Devices (AREA)
  • Springs (AREA)

Abstract

Provided is a vibration damping device of a novel structure, which can reduce the deformation rigidity required for a cylindrical outer member mounted on a second mounting member in a dynamic damper, and can improve the deformation rigidity of the cylindrical outer member without thickening. A vibration damping device (10) has a structure in which a first mounting member (18) and a second mounting member (20) are elastically coupled to each other by a main rubber elastic body (22), a bracket (14) is mounted on the second mounting member, a mounting portion (52) to be mounted to any one of members constituting a vibration transmission system is provided on the bracket, a cylindrical outer member (60) press-fitted and fixed to the second mounting member is provided, a mass member (58) is disposed on the inner periphery of the cylindrical outer member, and the cylindrical outer member and the mass member are elastically coupled to each other by a support rubber (62) fixed to the outer periphery of the mass member to constitute a dynamic damper (16).

Description

Vibration-proof device
Cross Reference to Related Applications
The present application claims priority from japanese patent application 2017-246569, filed on 22/12/2017, and from japanese patent application 2018-098880, filed on 23/5/2018, the entire contents of which are incorporated herein by reference.
Technical Field
The present invention relates to a vibration isolator suitable for an engine mount or the like of an automobile, and more particularly to a vibration isolator provided with a dynamic damper.
Background
Conventionally, a vibration isolator suitable for an engine mount of an automobile or the like is known. The vibration damping device has a structure in which a first mounting member and a second mounting member mounted to one member constituting a vibration transmission system are elastically coupled to each other by a main rubber elastic body.
Further, for example, japanese patent laying-open No. 6-94068 (patent document 1) proposes the following: by adding a dynamic damper to the engine mount, an improvement in vibration damping performance is achieved. That is, patent document 1 discloses the following structure: the engine mount includes a cup-shaped housing, and a dynamic damper is configured by housing a mass member in an air chamber formed by the housing and elastically supporting the mass member with rubber.
However, as shown in fig. 1 and 2 of patent document 1, when the mass member of the dynamic damper is elastically supported in a cantilever state by rubber, the rubber is easily elastically deformed in a wobbling state at the time of vibration input, and therefore there is a possibility that the vibration damping effect by displacement of the mass member is reduced.
On the other hand, as shown in fig. 3 of patent document 1, if a structure is adopted in which rubber is disposed on the outer periphery of the mass member of the dynamic damper and the mass member is elastically supported in the radial direction, the displacement mode of the mass member can be stabilized. However, in the structure shown in fig. 3 of patent document 1, since the bolts as the mounting structure to the engine or the vehicle body are directly provided to the case, the case is required to have a large deformation rigidity, and there is a possibility that the material for forming the case is limited, the weight is increased because the case is thick, and the like.
Documents of the prior art
Patent document
Patent document 1: japanese laid-open patent publication No. 6-94068
Disclosure of Invention
Problems to be solved by the invention
The present invention has been made in view of the above circumstances, and an object of the present invention is to provide a vibration damping device having a novel structure, which can reduce the deformation rigidity required for a cylindrical outer member attached to a second attachment member in a dynamic damper, and can improve the deformation rigidity of the cylindrical outer member without increasing the thickness of the cylindrical outer member.
Means for solving the problems
Embodiments of the present invention made to solve such problems are described below. The components used in the respective embodiments described below may be used in any combination as possible.
That is, a first aspect of the present invention relates to a vibration isolator having a structure in which a first mounting member and a second mounting member mounted to one of members constituting a vibration transmission system are elastically coupled to each other through a main rubber elastic body, wherein a bracket is mounted to the second mounting member, and a mounting portion to be mounted to one of the members constituting the vibration transmission system is provided on the bracket, while a cylindrical outer member press-fitted and fixed to the second mounting member is provided, a mass member is disposed on an inner periphery of the cylindrical outer member, and the cylindrical outer member and the mass member are elastically coupled to each other by a support rubber fixed to an outer periphery of the mass member to constitute a dynamic damper.
According to the vibration damping device having the structure according to the first aspect, the vibration damping effect due to the internal friction and the like caused by the elastic deformation of the main rubber elastic body and the vibration damping effect due to the dynamic damper can be obtained at the same time, and the vibration damping performance can be improved.
Further, since the cylindrical outer member is reinforced by the second mounting member by press-fitting and fixing the cylindrical outer member to the second mounting member, the deformation rigidity of the cylindrical outer member alone can be set relatively small, and a large deformation rigidity of the cylindrical outer member can be obtained in an assembled state of being assembled to the second mounting member. Therefore, for example, the cylindrical outer member can be made thin to reduce the weight, and the deformation of the cylindrical outer member can be prevented.
Further, since the dynamic damper has a structure in which the mass member is disposed on the inner periphery of the cylindrical outer member and the outer peripheral portion thereof is elastically supported by the support rubber, torsional displacement of the mass member is less likely to occur with respect to vibration input in the axial direction, and a vibration damping effect against input vibration can be effectively obtained. In particular, even when the mass of the mass member is increased to favorably obtain the vibration damping effect by the dynamic damper, the intended vibration damping effect can be effectively obtained by stably supporting the mass member at the outer peripheral portion, and the deformation of the cylindrical outer member supporting the mass member of large mass via the support rubber is prevented by the reinforcing effect by press-fitting.
A second aspect of the present invention is the vibration damping device according to the first aspect, wherein the cylindrical outer member is open on both sides in the axial direction, one open end portion in the axial direction of the cylindrical outer member is press-fitted and fixed to the second mounting member, and the mass member is exposed to the outside from the cylindrical outer member through the other opening in the axial direction of the cylindrical outer member.
According to the second aspect, it is easier to set the axial dimension of the mass member to be larger in the limited installation space of the vibration damping device, as compared with the case where the mass member is housed in the cylindrical outer member having a cylindrical shape with a bottom. As a result, a large mass of the mass member can be easily obtained, and the vibration damping effect by the dynamic damper can be advantageously obtained.
A third aspect of the present invention is the vibration damping device according to the second aspect, wherein the vibration damping device includes a reinforcing portion in which the other axial opening end portion of the cylindrical outer member is bent toward the inner circumferential side.
According to the third aspect, the one axial end portion of the cylindrical outer member is reinforced by press-fitting and fixing the cylindrical outer member to the second mounting member, and the other axial end portion of the cylindrical outer member is reinforced by the reinforcing portion, so that a large deformation rigidity of the cylindrical outer member is ensured. In particular, by providing the reinforcing portion at the other axial opening end portion away from the press-fit fixing portion press-fitted and fixed to the second mounting member, the deformation rigidity of the cylindrical outer member can be effectively improved.
A fourth aspect of the present invention is the vibration damping device according to the third aspect, wherein the supporting rubber is fixed to the reinforcing portion of the cylindrical exterior member.
According to the fourth aspect, a large compressive elastic component of the support rubber can be easily obtained with respect to the input in the axial direction, and a large tuning degree of freedom of the elasticity in the axial direction in the support rubber can be obtained.
A fifth aspect of the present invention is the vibration damping device according to any one of the first to fourth aspects, wherein a stepped portion is provided at an axially intermediate portion of the cylindrical outer member.
According to the fifth aspect, the step portion functions as a reinforcing structure, thereby improving the deformation rigidity of the cylindrical exterior member.
A sixth aspect of the present invention is the vibration isolator according to any one of the first to fifth aspects, wherein the cylindrical outer member is open at a lower side, and a retaining projection projecting toward an inner periphery is provided at a lower opening of the cylindrical outer member, and the retaining projection constitutes a fail safe (fail safe) for preventing the mass member from coming off the cylindrical outer member downward.
According to the sixth aspect, in the event of breakage of the supporting rubber, the mass member can be prevented from coming off the cylindrical outer member downward by the fail-safe, and safety can be improved. Further, by a simple structure in which the anti-slip projection is provided in the opening portion on the lower side of the cylindrical exterior member, effective fail-safe can be realized.
A seventh aspect of the present invention is the vibration damping device according to any one of the first to sixth aspects, wherein the second mounting member is formed in a tubular shape, one axial opening of the second mounting member is closed by the main rubber elastic body, the other axial opening of the second mounting member is closed by a flexible film, a pressure receiving chamber having a wall portion a part of which is formed by the main rubber elastic body and a balance chamber having a wall portion a part of which is formed by the flexible film are formed between the main rubber elastic body and the flexible film, the tubular outer member press-fitted and fixed to the second mounting member is extended outward in the axial direction, the mass member is disposed outward in the axial direction with respect to the flexible film, the tubular outer member and the mass member are elastically coupled by the support rubber, and a communication hole for opening a space formed between the flexible film and the mass member in the axial direction to the atmosphere is formed in the tubular outer member, At least one of the mass member and the supporting rubber.
According to the seventh aspect, by providing the vibration isolation device in a fluid-filled type, an excellent vibration isolation effect based on the flow action of the fluid can be obtained. Further, by providing a dynamic damper in a fluid filled vibration damping device that exhibits an excellent vibration damping effect against vibrations of a predetermined frequency, it is possible to achieve, for example, effective vibration damping performance against a plurality of vibrations of different frequencies and more excellent vibration damping performance against vibrations of a specific frequency.
Further, by providing the communication hole, the space formed between the flexible membrane and the mass member is prevented from being closed, the deformation of the flexible membrane can be prevented from being hindered by the air elasticity of the space, and the pressure difference between the pressure receiving chamber and the equilibrium chamber is largely exhibited at the time of vibration input, so that the vibration-proof effect by the flow action of the fluid or the like can be effectively obtained.
An eighth aspect of the present invention is the vibration damping device according to the seventh aspect, wherein the mass member is disposed below the flexible film, and a covering rubber covering an upper surface of the mass member is integrally formed with the support rubber.
According to the eighth aspect, even when the flexible film abuts on the upper surface of the mass member at the time of vibration input, the generation of abnormal noise can be suppressed by the cushioning effect of the covering rubber. Further, by fixing the covering rubber integrally formed with the supporting rubber to the mass member, the fixing strength and durability of the supporting rubber to the mass member can be improved. Further, since the upper surface of the mass member is covered with the covering rubber, even if water or the like intrudes between the flexible film and the mass member, corrosion such as rust in the mass member can be prevented. Further, since the surface of the mass member is widely covered with the covering rubber, for example, even when the mass member becomes high in temperature due to heat from the outside, the covering rubber can reduce the radiant heat from the mass member to the flexible film, and can expect an effect of suppressing the temperature rise of the flexible film, the equilibrium chamber sealing liquid, and the like, and an effect of suppressing vibration and abnormal noise due to resonance and the like of the mass member, the cylindrical exterior member, and the like.
A ninth aspect of the present invention is the vibration damping device according to the eighth aspect, wherein a material injection portion for molding the support rubber and the cover rubber is provided in the cover rubber.
According to the ninth aspect, since the material injection portion at the time of rubber molding in which the projection is generated and it is difficult to uniformize the shape and the characteristics with other portions is provided at a position distant from the support rubber constituting the dynamic damper, the characteristics intended for the support rubber and thus the dynamic damper can be obtained more stably.
A tenth aspect of the present invention is the vibration damping device according to the ninth aspect, wherein a material guide portion is formed from the material injection portion to the supporting rubber by providing the material injection portion in a state of protruding from a center of an upper surface of the mass member toward an outer peripheral end, and by locally increasing a thickness dimension of the covering rubber.
According to the tenth aspect, it is possible to avoid an unnecessary thickness of the covering rubber at the central portion of the upper surface of the mass body, and to ensure good fluidity of the rubber material from the material injection portion to the supporting rubber when the material is injected into the rubber molding cavity in the molding die by the material guide portion. Further, since the material injection portion is provided on the outer peripheral side of the upper surface of the mass member so as to avoid the opposing position opposing the central portion of the flexible membrane that is likely to be largely deformed at the time of vibration input, even when the material injection portion has a protrusion, it is possible to reduce or avoid a decrease in the durability of the flexible membrane due to the collision of the flexible membrane with the protrusion.
An eleventh aspect of the present invention is the vibration isolator according to any one of the seventh to tenth aspects, wherein the mass member is disposed below the flexible film, the communication hole is formed so as to open to an upper surface of the mass member, and the upper surface of the mass member has a tapered surface that is inclined downward toward the opening of the communication hole.
According to the eleventh aspect, the space between the flexible film and the mass member is opened to the atmosphere through the communication hole formed in the mass member. Further, even if water enters the upper side of the mass member, for example, the entered water is guided toward the opening of the communication hole by the tapered surface provided on the upper surface of the mass member, passes through the communication hole, and is rapidly discharged to the outside. This prevents water from being accumulated on the upper surface of the mass member for a long period of time, thereby avoiding problems such as rusting of the mass member.
A twelfth aspect of the present invention is the vibration damping device according to any one of the seventh to eleventh aspects, wherein the mass member is disposed below the flexible film, and the communication hole is formed so as to open to an upper surface of the supporting rubber.
According to the twelfth aspect, the space between the flexible film and the mass member is opened to the atmosphere by the communication hole formed in the supporting rubber. Further, even if water enters the upper side of the supporting rubber, for example, water is rapidly discharged to the outside through the communication hole, and therefore, water can be prevented from being accumulated on the upper surface of the supporting rubber for a long period of time, and a problem such as deterioration of the supporting rubber can be avoided. In addition, the communication hole in the supporting rubber may be used together with the communication hole in the mass member according to the eleventh aspect.
Further, the elastic characteristics of the supporting rubber can be adjusted by the shape, size, arrangement, number of the communicating holes, and the like, and the elastic characteristics of the supporting rubber can be obtained as a target.
A thirteenth aspect of the present invention provides the vibration damping device according to any one of the first to twelfth aspects, wherein the bracket includes a fitting tube portion press-fitted and fixed to the second mounting member.
According to the thirteenth aspect, the bracket is press-fitted into the second mounting member, whereby a further reinforcing effect can be achieved for the cylindrical exterior member by the bracket due to the reinforcing effect of the second mounting member. In the present invention, the cylindrical exterior member and the bracket may be press-fitted into the second mounting member or press-fitted into the second mounting member.
Effects of the invention
According to the present invention, by press-fitting and fixing the cylindrical outer member of the dynamic damper to the second mounting member and reinforcing the cylindrical outer member by the second mounting member, the deformation rigidity of the cylindrical outer member alone can be set relatively small, and a large deformation rigidity of the cylindrical outer member can be obtained in an assembled state of being assembled to the second mounting member. Therefore, for example, the cylindrical outer member can be made thin to reduce the weight, and the deformation of the cylindrical outer member can be prevented. Further, since the dynamic damper has a structure in which the mass member is disposed on the inner periphery of the cylindrical outer member and the outer peripheral portion of the mass member is elastically supported by the supporting rubber, torsional displacement of the mass member is less likely to occur with respect to vibration input in the axial direction, and a damping action against input vibration can be effectively obtained.
Drawings
Fig. 1 is a sectional view showing an engine mount according to an embodiment of the present invention.
Fig. 2 is a plan view of a dynamic damper constituting the engine mount shown in fig. 1.
Fig. 3 is a bottom view of the dynamic vibration absorber shown in fig. 2.
Fig. 4 is a sectional view IV-IV of fig. 2.
Fig. 5 is a perspective view of the dynamic vibration absorber shown in fig. 2.
Fig. 6 is a perspective view of the dynamic vibration absorber shown in fig. 2 at another angle.
Fig. 7 is a sectional view showing an engine mount according to another embodiment of the present invention.
Fig. 8 is a sectional view VIII-VIII of fig. 9 showing an engine mount as another embodiment of the present invention. And is a sectional view showing an engine mount as an embodiment.
Fig. 9 is a cross-sectional view IX-IX of fig. 8.
Description of the reference numerals
10. 90, 100: an engine mount (vibration isolator); 14: a bracket; 16: a dynamic vibration absorber; 18: a first mounting member; 20: a second mounting member; 22: a main rubber elastic body; 32: a flexible film; 46: a pressure receiving chamber; 48: a balancing chamber; 50: assembling the barrel part; 52: an installation part; 58: a mass member; 60: a cylindrical outer member; 62: a supporting rubber; 66: a mass body communication hole (communication hole); 68: a conical surface; 72: a reinforcing portion; 74: an anti-drop projection; 76: a step portion; 78: a rubber communication hole (communication hole); 80: a space; 82: fail safe; 102: an upper surface; 104: a material injection part; 106: a material guide.
Detailed Description
Hereinafter, embodiments of the present invention will be described with reference to the drawings.
Fig. 1 shows an engine mount 10 for an automobile as an embodiment of a vibration damping device formed in a structure according to the present invention. The engine mount 10 has a configuration in which a bracket 14 and a dynamic vibration reducer 16 are mounted on a mount main body 12. In the following description, the vertical direction refers to an axial direction and to a vertical direction in fig. 1 that is substantially vertical in a vehicle mounted state described later.
More specifically, the mount body 12 is a fluid-filled vibration damping device, and has a structure in which the first mounting member 18 and the second mounting member 20 are elastically coupled to each other by the body rubber elastic body 22.
The first mounting member 18 is a highly rigid member formed of metal or the like, has an approximately cylindrical shape extending in the axial direction as a whole, and an axially intermediate portion is provided to be locally enlarged in diameter. Further, a screw hole 24 that opens at the upper surface and extends vertically is formed in the first mounting member 18.
The second mounting member 20 is a highly rigid member formed of metal or the like, and includes a thin, large-diameter cylindrical portion 25 having a substantially cylindrical shape, and an intermediate step portion 26 is formed at an axially intermediate portion of the cylindrical portion 25, and the cylindrical portion 25 is formed in a stepped cylindrical shape, wherein an upper portion above the intermediate step portion 26 is larger in diameter than a lower portion. The second mounting member 20 of the present embodiment is formed by press working (drawing), and the lower end portion of the cylindrical portion 25 is bent toward the inner peripheral side to include the annular reinforcing rib 27, so that the deformation rigidity of the second mounting member 20 is improved.
Then, the first mounting member 18 and the second mounting member 20 are vertically arranged on substantially the same central axis, and the first mounting member 18 and the second mounting member 20 are elastically coupled to each other by the main rubber elastic body 22. The main rubber elastic body 22 has a substantially truncated cone shape, and a radially central portion thereof is vulcanization bonded to the first mounting member 18, and an outer peripheral surface of a radially larger lower end portion thereof is vulcanization bonded to an inner peripheral surface of the second mounting member 20. In this way, the main rubber elastic body 22 of the present embodiment is formed as an integrally vulcanization molded product including the first mounting member 18 and the second mounting member 20. Further, it is desirable to reduce the tensile stress caused by shrinkage after molding of the main rubber elastic body 22 by subjecting the second mounting member 20 to diameter reduction processing such as 360-degree radial compression after vulcanization molding of the main rubber elastic body 22.
Further, a recess 28 opened on the lower surface is formed in the main rubber elastic body 22. The recess 28 is gradually increased in diameter toward the opening, and opens on the inner periphery of the small diameter portion of the cylindrical portion 25 in the second mounting member 20. Further, the inner peripheral surface of the small diameter portion of the cylindrical portion 25 of the second mounting member 20 is covered with the seal rubber layer 30. The seal rubber layer 30 is formed integrally with the main rubber elastic body 22, is formed in a thin tubular shape, and extends from the outer circumferential lower side of the recess 28.
In addition, a flexible film 32 is attached to the lower end portion of the second attachment member 20. The flexible film 32 is, for example, a thin rubber film, has a slack in the vertical direction, and has an annular fixing member 34 fixed to the outer peripheral end portion. The fixing member 34 is inserted into the inner periphery of the cylindrical portion 25 of the second mounting member 20 and is fitted into the small diameter portion of the cylindrical portion 25 covered with the seal rubber layer 30, whereby the flexible film 32 is mounted to the lower end portion of the second mounting member 20.
Thereby, the upper opening of the cylindrical portion 25 of the second mounting member 20 is closed to be fluid-tight by the main rubber elastic body 22, and the lower opening of the cylindrical portion 25 of the second mounting member 20 is closed to be fluid-tight by the flexible film 32. A fluid chamber 36 in which a non-compressible fluid is sealed is formed between the main rubber elastic body 22 and the flexible membrane 32 in the axial direction on the inner periphery of the cylindrical portion 25 of the second mounting member 20. The incompressible fluid sealed in the fluid chamber 36 is not particularly limited, but is preferably a low-viscosity liquid of 0.1Pa · s or less, and for example, water, ethylene glycol, alkylene glycol, polyalkylene glycol, silicone oil, or a mixture thereof may be used.
In addition, a partition member 38 is disposed in the fluid chamber 36. The partition member 38 includes a substantially circular plate-shaped body portion 40, and a substantially cylindrical fitting portion 42 extending downward is integrally formed at an outer peripheral end portion of the body portion 40. Further, a throttle passage 44 penetrating vertically is formed in a radially central portion of the body 40. The tuning frequency, which is the resonance frequency of the fluid flowing through the orifice passage 44, is adjusted based on the ratio of the passage cross-sectional area to the passage length, and is set to a medium to high frequency corresponding to, for example, idle vibration, running sound, and the like. Of course, the specific structure and tuning frequency of the throttle passage may be changed, and for example, the tuning frequency of the throttle passage may be set to a low frequency corresponding to engine shake by forming the throttle passage extending in the circumferential direction in the outer peripheral portion of the partition member to secure a long passage length of the throttle passage.
The partition member 38 is disposed in the fluid chamber 36, and includes a small diameter portion where the outer peripheral end portion of the fitting portion 42 is fitted to the cylindrical portion 25 of the second mounting member 20 via the seal rubber layer 30. Thus, the fluid chamber 36 is divided into two parts by the partition member 38 along the upper and lower sides, and a pressure receiving chamber 46 having a wall part constituted by the main rubber elastic body 22 is formed at a position above the partition member 38, and a balance chamber 48 having a wall part constituted by the flexible film 32 is formed at a position below the partition member 38. The pressure receiving chamber 46 and the equilibrium chamber 48 are filled with a non-compressible fluid and communicate with each other through the orifice passage 44.
The bracket main body 12 configured in this way mounts the bracket 14 as a separate component on the second mounting member 20. The bracket 14 is a highly rigid member formed of metal or the like, and has a structure in which a plurality of attachment portions 52 are fixedly provided at the lower end portion of an attachment tube portion 50 having a substantially cylindrical shape. The fitting cylinder portion 50 is integrally formed with an annular plate-shaped stopper receiving portion 54 protruding toward the inner periphery at the upper end portion, and the lower portion of the fitting cylinder portion 50 having a larger diameter than the upper portion is press-fitted and fixed to the second mounting member 20 in an externally fitted state. The mounting portion 52 has a cross-sectional shape bent in a substantially L-shape, an upper end portion thereof is fixed by welding or the like so as to overlap an outer peripheral surface of a lower end portion of the mounting tube portion 50, and a mounting bolt 56 projecting downward is fixed to a lower end portion thereof in a penetrating state.
Further, a dynamic damper 16 is attached to the holder main body 12. As shown in fig. 2 to 6, the dynamic damper 16 has a structure in which the mass member 58 and the cylindrical outer member 60 are elastically coupled by the support rubber 62.
More specifically, the mass member 58 is formed of a material having a relatively large specific gravity such as iron, and has an approximately cylindrical shape as a whole. Further, a stepped surface 64 is provided on the outer peripheral surface of the mass member 58, and a portion below the stepped surface 64 is set to have a smaller diameter than the upper side. Further, a mass communication hole 66 as a communication hole penetrating vertically is formed in a radially central portion of the mass member 58. The mass communication hole 66 opens at the upper surface of the mass member 58, and a tapered surface 68 that is inclined downward toward the upper opening of the mass communication hole 66 is formed at the upper surface of the mass member 58. The tapered surface 68 is provided at a radially intermediate portion in the upper surface of the mass member 58 over the entire circumference, and is inclined downward toward the inner circumference.
The cylindrical outer member 60 is formed of metal or the like as a member independent of the second mounting member 20 and the bracket 14, has a substantially cylindrical shape with a thin wall and a large diameter, and is open on both axial sides, in other words, both vertical sides. Further, the flange portion 70 protruding outward is continuously formed over the entire circumference of the upper end portion of the cylindrical outer member 60, the lower end portion of the cylindrical outer member 60 is curved inward, and the inward flange-shaped reinforcing portion 72 protruding inward is continuously formed over the entire circumference of the lower end portion of the cylindrical outer member 60. Further, at the lower end portion of the cylindrical outer member 60, retaining projections 74 extending to a position closer to the inner periphery than the reinforcing portion 72 are provided at a plurality of positions (four positions in the present embodiment) in the circumferential direction. The tubular outer member 60 of the present embodiment is formed by press working (drawing) a metal blank plate.
Further, the lower portion of the cylindrical outer member 60 is set to have a smaller diameter than the upper portion, and a stepped portion 76 is formed at an axially intermediate portion. The stepped portion 76 of the present embodiment is formed continuously over the entire circumference in a substantially constant tapered shape that slopes downward toward the inner circumference, and the small diameter portion of the cylindrical outer member 60 on the lower side of the stepped portion 76 is shorter in axial length than the large diameter portion on the upper side of the stepped portion 76.
The cylindrical outer member 60 is formed to have a substantially constant thickness, and is formed to have a wall thickness smaller than the fitting tube portion 50 of the bracket 14, and to have a wall thickness smaller than the second mounting member 20 or substantially the same thickness as the second mounting member 20.
The mass member 58 is disposed on the inner periphery of the cylindrical outer member 60, and a support rubber 62 is disposed between the mass member 58 and the cylindrical outer member 60. The support rubber 62 is an annular rubber elastic body, and in the present embodiment, includes a plurality of rubber communication holes 78 serving as communication holes. The rubber communication hole 78 is formed to vertically penetrate in a predetermined cross-sectional shape extending in the circumferential direction, an upper opening is opened in the upper surface of the supporting rubber 62 between the mass member 58 and the cylindrical outer member 60 in the radial direction, and a lower opening is opened in the inner peripheral surface of the supporting rubber 62 between the mass member 58 and the reinforcing portion 72 of the cylindrical outer member 60. In the present embodiment, the four rubber communication holes 78, 78 are arranged substantially equally spaced from each other in the circumferential direction.
The outer peripheral surface of the supporting rubber 62 is vulcanization-bonded to the inner peripheral surface of the cylindrical outer member 60, and the lower surface is vulcanization-bonded to the upper surfaces of the reinforcement portion 72 and the retaining projection 74 in the cylindrical outer member 60, while the inner peripheral surface is vulcanization-bonded to the outer peripheral portion of the mass member 58, that is, the step surface 64 and the large diameter portion on the upper side of the step surface 64. Thereby, the mass body member 58 and the cylindrical outer member 60 are elastically coupled to each other by the supporting rubber 62.
Further, in a state where the mass member 58 and the cylindrical outer member 60 are elastically coupled by the supporting rubber 62, the mass member 58 is exposed to the outside through the lower opening of the cylindrical outer member 60, and in the present embodiment, the lower portion of the mass member 58, which is made small in diameter, partially protrudes downward from the lower opening of the cylindrical outer member 60. Thus, for example, even when another member of the vehicle is disposed below the cylindrical outer member 60, the mass member 58 can be disposed toward the inner periphery of the other member of the vehicle, and a mass member 58 having a large mass can be obtained. The stepped surface 64 of the mass member 58 is located above the reinforcing portion 72 and the retaining projection 74 that constitute the lower end portion of the tubular outer member 60, and the large-diameter portion of the mass member 58 located above the stepped surface 64 is disposed on the inner periphery of the tubular outer member 60 over the entire range.
In addition, the distance between the elastic center extending in the radial direction of the support rubber 62 and the center of gravity of the mass member 58 is preferably short, and the elastic center is preferably set to pass through the center of gravity of the mass member 58. This reduces torsional displacement of the mass member 58 with respect to vertical vibration input described later. Further, the support rubber 62 is fixed to a small diameter portion of the tubular outer member 60 below the stepped portion 76.
Further, after vulcanization molding of the support rubber 62, the cylindrical outer member 60 is subjected to diameter reduction processing, whereby the tensile stress caused by shrinkage after molding of the support rubber 62 is reduced, and the inner peripheral portion of the retaining protrusion 74 of the cylindrical outer member 60 is disposed at a position overlapping the stepped surface 64 of the mass member 58 in axial projection. The supporting rubber 62 is disposed below the stepped portion 76 of the tubular outer member 60.
In the dynamic damper 16 configured as described above, the cylindrical outer member 60 is press-fitted and fixed to the second mounting member 20, whereby the dynamic damper 16 is mounted to the holder main body 12. That is, the upper portion of the cylindrical outer member 60 is fixed to the second mounting member 20 and the cylindrical outer member 60 is extended to the lower side of the second mounting member 20 by press-fitting the large diameter portion of the cylindrical outer member 60 on the upper side of the stepped portion 76 into the small diameter portion of the cylindrical portion 25 of the second mounting member 20 on the lower side of the intermediate stepped portion 26. Thus, the mass member 58 and the support rubber 62 are disposed below the holder main body 12, and the dynamic damper 16 is actually configured below the holder main body 12. Further, a space 80 is formed between the flexible film 32 of the holder main body 12 and the upper and lower portions of the mass member 58 and the support rubber 62 of the dynamic damper 16. The space 80 is opened to the atmosphere through the mass communication hole 66 and the rubber communication hole 78, and thereby the internal pressure is maintained at approximately atmospheric pressure.
Since the cylindrical outer member 60 is reinforced by the second mounting member 20 by press-fitting and fixing the upper portion of the cylindrical outer member 60 to the lower portion of the second mounting member 20 in this manner, it is possible to prevent deformation of the cylindrical outer member 60 without setting the deformation rigidity of the cylindrical outer member 60 itself to be particularly large. In particular, in the present embodiment, the second mounting member 20 is press-fitted and fixed to the fitting tube portion 50 of the thick bracket 14, and the reinforcing rib 27 is provided at the lower end portion of the second mounting member 20, whereby the deformation rigidity of the second mounting member 20 is improved, and therefore the reinforcing effect of the cylindrical outer member 60 by press-fitting toward the second mounting member 20 is more favorably exhibited. In other words, the deformation rigidity of the second mounting member 20 is increased by press-fitting the bracket 14 into the second mounting member 20 in the externally fitted state, whereby the reinforcing effect of the bracket 14 can act on the cylindrical outer member 60 via the second mounting member 20, as compared with the cylindrical outer member 60 into which the second mounting member 20 is press-fitted in the externally fitted state.
Further, since the lower end portion of the tubular outer member 60 of the present embodiment, which is away from the press-fit fixing portion toward the second mounting member 20, is bent toward the inner periphery to be the reinforcing portion 72, the deformation rigidity of the tubular outer member 60 is effectively ensured.
In addition, in the tubular outer member 60, an annular stepped portion 76 having a tapered shape is formed in a portion protruding toward the lower side in the axial direction from a portion press-fitted and fixed to the second mounting member 20. The stepped portion 76 is also apart from the fixed portion of the supporting rubber 62 in the cylindrical outer member 60, and is provided between the portion of the cylindrical outer member 60 that is press-fitted and fixed to the second mounting member 20 and the portion to which the supporting rubber 62 is fixed in the axial direction. In this way, by providing the step portion 76 at the axially intermediate portion of the cylindrical outer member 60 and at a position away from the press-fit fixing portion of the cylindrical outer member 60 toward the second mounting member 20 and the fixing portion of the supporting rubber 62, the deformation rigidity of the cylindrical outer member 60 is further improved.
Since the tubular outer member 60 is provided as a separate member from the bracket 14 directly fixed to the vehicle body described later, a large deformation rigidity required for fixing to the vehicle body is not required. Therefore, in the tubular outer member 60, while weight reduction and the like due to thinning are achieved, the necessary deformation rigidity is ensured by press-fitting and fixing to the second mounting member 20 and formation of the reinforcing portion 72 and the stepped portion 76, and stable mounting to the vehicle is achieved by setting a sufficient deformation rigidity in the bracket 14.
Further, the relative position of the cylindrical outer member 60 in the axial direction with respect to the second mounting member 20 is regulated by causing the flange portion 70 provided at the upper end of the cylindrical outer member 60 to abut against the intermediate step portion 26 of the second mounting member 20 in the axial direction. Thus, the mass member 58 is disposed below the lower end of the second mounting member 20 and is disposed so as to be separated downward from the flexible film 32, and in particular, the initial separation distance of the mass member 58 from the flexible film 32 is set so that the flexible film 32 does not come into contact with the mass member 58 when the flexible film 32 is deformed or the mass member 58 is displaced upward and downward. Further, since the flange portion 70 is overlapped in a state of contact with the intermediate step portion 26 of the second mounting member 20, the flange portion 70 is reinforced by the intermediate step portion 26 which increases the deformation rigidity by fitting into the fitting cylindrical portion 50 of the bracket 14, and the deformation rigidity of the cylindrical outer member 60 is further improved.
In the engine mount 10 configured as described above, for example, the first mounting member 18 is mounted on the power unit side, not shown, and the second mounting member 20 is mounted on the vehicle body side, not shown, via the bracket 14. Thereby, the power unit and the vehicle body are coupled to each other in a vibration-proof manner via the engine mount 10. Further, since the bracket 14 is attached to the vehicle body at the attachment portion 52 provided with the attachment bolt 56, the lower surface of the attachment portion 52 is set as the attachment surface of the bracket 14 facing the vehicle body. Further, the lower end of the mass member 58 is set to be located at least above the extended surface of the lower surface of the mounting portion 52 located at the lowermost end.
In the assembled state of the vehicle, when vibration in the vertical direction is input, relative pressure fluctuation occurs between the pressure receiving chamber 46 and the equilibrium chamber 48, and a fluid flow passing through the orifice passage 44 is generated between the pressure receiving chamber 46 and the equilibrium chamber 48. This exerts the vibration-proof effect based on the flow action such as the resonance action of the fluid, and the vibration-proof effect is exerted as a target. In particular, in the present embodiment, since the orifice passage 44 is tuned to the medium to high frequencies such as idling vibration and running booming noise, the vibration insulating function by the low dynamic elasticity is exhibited when the medium to high frequency vibration is input.
Further, when vibration in the vertical direction is input, the dynamic damper 16 has an effect of reducing the input vibration by displacing the mass member 58 vertically with respect to the cylindrical outer member 60 so as to cancel out the vibration. This can also exhibit the vibration-proof effect of the dynamic damper 16. The outer diameter of the large diameter portion of the mass member 58 on the upper side of the stepped surface 64 is set to be smaller than the inner diameter of the reinforcing rib 27 of the second mounting member 20 and smaller than the inner diameter of the fixing member 34 of the flexible film 32, and the outer peripheral edge of the upper end of the mass member 58 is positioned on the inner periphery of the reinforcing rib 27 and the fixing member 34. This prevents the rigid mass member 58 from coming into contact with the rigid reinforcing ribs 27 and the fixing member 34 due to vertical displacement, and allows a large vertical displacement stroke of the mass member 58 while suppressing the axial dimension of the engine mount 10.
Further, by adjusting the resonance frequency of the mass-elastic system composed of the mass member 58 and the support rubber 62 in the dynamic damper 16, the frequency of the vibration to be damped by the dynamic damper 16 can be set as necessary. Specifically, for example, by making the resonant frequency of the dynamic damper 16 substantially equal to the tuning frequency of the orifice passage 44 in the carrier body 12, it is possible to achieve more excellent vibration damping performance against vibrations of a specific frequency, while making the tuning frequency of the orifice passage 44 and the resonant frequency of the dynamic damper 16 different from each other, it is possible to achieve effective vibration damping performance against a plurality of input vibrations of different frequencies. In the present embodiment, a plurality of rubber communication holes 78 are formed in the support rubber 62, and the elasticity of the support rubber 62 is adjusted by the shape, the hole cross-sectional area, the number of formations, and the like of the rubber communication holes 78. Further, in the present embodiment, the elasticity in the axial direction of the supporting rubber 62 is adjusted by disposing the supporting rubber 62 not only between the outer peripheral surface of the mass body member 58 and the inner peripheral surface of the cylindrical outer member 60 in the radial direction but also between the stepped surface 64 of the mass body member 58 and the reinforcing portion 72 and the retaining projection 74 of the cylindrical outer member 60 in the axial direction.
The dynamic damper 16 of the present embodiment has a structure in which the outer periphery of the mass member 58 is elastically supported by the annular support rubber 62, and therefore the mass member 58 is less likely to be displaced in the torsional direction or the like, and the vibration damping effect by the vertical displacement of the mass member 58 can be effectively obtained.
Further, by forming the mass communication hole 66 in the mass member 58 and forming the rubber communication hole 78 in the support rubber 62, the space 80 formed between the flexible film 32 and the mass member 58 and between the upper and lower sides of the support rubber 62 communicates with the external space through the mass communication hole 66 and the rubber communication hole 78. Accordingly, the space 80 is opened to the atmosphere, and deformation of the flexible membrane 32 is prevented from being hindered by the air elasticity of the space 80, so that when axial vibration is input, a large variation in relative pressure between the pressure receiving chamber 46 and the equilibrium chamber 48 is caused in the holder main body 12, and a vibration damping effect by the flow action of the fluid can be effectively obtained.
For example, even if water enters the space 80 through the mass communication hole 66 and the rubber communication hole 78, the water on the mass member 58 can be discharged to the outside through the mass communication hole 66, and the water on the support rubber 62 can be discharged to the outside through the rubber communication hole 78. In particular, a tapered surface 68 that is inclined downward toward the upper opening of the mass communication hole 66 is provided on the upper surface of the mass member 58 having a large area, and water on the mass member 58 is guided to the mass communication hole 66 and quickly discharged. This can prevent water from accumulating on the upper surfaces of the mass member 58 and the supporting rubber 62 over a long period of time, thereby preventing rusting, deterioration, and the like of the mass member 58 and the supporting rubber 62.
Further, since the retaining projection 74 of the tubular outer member 60 overlaps the stepped surface 64 of the mass member 58 in the vertical projection, even if the supporting rubber 62 is broken, the mass member 58 does not come off downward from the tubular outer member 60, and safety is ensured by the fail-safe 82 including the retaining projection 74. In the present embodiment, considering the case where the mass member 58 tilts when the supporting rubber 62 breaks, the mass member 58 is engaged with the retaining projection 74 of the tubular outer member 60 regardless of the orientation of the mass member 58, and functions as the fail-safe 82, so that the mass member 58 does not fall off the tubular outer member 60 downward, for example, by making the upper portion of the mass member 58 above the stepped surface 64 have a sufficient length in the axial direction. It is also obvious that the fail-safe 82 prevents the mass member 58 from falling off downward, and the falling-off preventing projection 74 constituting the fail-safe 82 is disposed on the lower side in the gravitational force acting direction with respect to the mass member 58 in the assembled state in which the engine bracket 10 is assembled to the vehicle.
The embodiments of the present invention have been described above in detail, but the present invention is not limited to the specific description. For example, in the above-described embodiment, the holder main body 12 as the fluid-filled vibration damping device is exemplified, but a solid-type holder main body in which no fluid is filled may be employed. That is, the engine mount 90 as the vibration damping device shown in fig. 7 has a structure in which the bracket 14 and the dynamic damper 16 are mounted on the mount main body 92, and is configured such that the mount main body 92 is elastically connected to the first mounting member 18 and the second mounting member 20 by the main rubber elastic body 22, and the pressure receiving chamber and the equilibrium chamber in which the incompressible fluid is sealed are not formed as in the above-described embodiment. In the engine mount 90 of fig. 7, vibration damping effects due to internal friction and the like caused by elastic deformation of the main rubber elastic body 22 and vibration damping effects caused by the dynamic damper 16 can be effectively obtained even when vibration is input in the vertical direction. In the engine mount 90 shown in fig. 7, the same members and portions as those of the above-described embodiment are denoted by the same reference numerals, and the description thereof is omitted.
Further, in the above embodiment, the support rubber 62 is fixed to the outer peripheral surface of the mass member 58, but the shape of the support rubber 62, the fixing position to the mass member 58 and the cylindrical exterior member 60, and the like are not limited. In the above embodiment, the surface of the mass member 58 is exposed except for the fixing region of the supporting rubber 62, but a part or the whole of the surface of the mass member 58 or the inner circumferential surface including the mass communication hole 66 may be covered with a covering rubber or the like.
Specifically, for example, as shown in fig. 8 to 9, an inner space may be defined between the facing surfaces of the mass member 58 and the flexible film 32 by surrounding the space with the cylindrical outer member 60, and the surface of the mass member 58 exposed to the inner space may be covered with the covering rubber 98.
That is, in the engine mount 100 shown in fig. 8 to 9, the upper surface 102 of the mass member 58 constituting the dynamic damper 16 is formed into a flat surface shape which spreads in the direction perpendicular to the axis perpendicular to the mount center axis and which is substantially horizontal in the mount-mounted state. The mass member 58 of the present embodiment is a solid block structure, and the mass communication hole (66) of the above embodiment is not formed.
Further, a covering rubber 98 covering the surface is formed on the mass member 58 and is fixed to the outer peripheral surface by vulcanization adhesion or the like. The cover rubber 98 is formed integrally with the support rubber 62 constituting the dynamic vibration reducer 16. The covering rubber 98 may cover the entire surface of the mass member 58, and in this embodiment, the upper outer circumferential surface and the upper surface 102 of the mass member 58 located above the fixed portion of the supporting rubber 62 are covered over substantially the entire range. Thus, in the assembled state in which the dynamic damper 16 is assembled to the mount main body 12, the surface of the mass member 58 facing the internal space 80 surrounded by the cylindrical outer member 60 and defined between the facing surfaces of the flexible film 32 and the mass member 58 is substantially covered over the entire range by the covering rubber 98.
The thickness of the covering rubber 98 is not limited as long as it is a thickness necessary to stably form a rubber material over the surface of the mass member 58 and prevent damage such as peeling due to handling during manufacturing and use after assembly. Of course, in this embodiment, since the injection portion 104 of the rubber material into the molding cavity of the molding die is formed in the cover rubber 98 at the time of molding the cover rubber 98 and the support rubber 62 which are integrally formed, the thickness dimension of the cover rubber 98 is set in consideration of the flowability of the rubber material toward the support rubber 62.
Specifically, in the present embodiment, the material injection portion 104 is provided so as to be positioned on the upper surface 102 of the mass member 58 in consideration of mold release in the direction of the holder center axis (vertical direction in the drawing). A material injection portion 104 is provided on the upper surface 102 of the mass member 58 at a position separated from the center toward the outer periphery by a predetermined distance and closer to the outer peripheral end than the center. In addition, a plurality of (four in the drawing) material injection portions 104 are provided at positions at substantially equal intervals in the circumferential direction of the mass member 58, and in this embodiment, all the material injection portions 104 are provided at positions separated by substantially the same distance radially inward from the outer peripheral end of the upper surface 102.
Each material injection portion 104 is formed in a convex shape protruding upward corresponding to a gate set at an injection port of the molding die, and the thickness dimension of the covering rubber 98 covering the upper surface 102 is increased in the material injection portion 104. Further, the covering rubber 98 is provided with a material guide portion 106 having a thick route from the material injection portion 104 to the support rubber 62. By forming the material guide portion 106 by locally thickening the covering rubber 98, a large flow path cross-sectional area can be ensured without unnecessarily thickening the covering rubber 98 covering the central portion of the upper surface 102 or the like, so that the rubber material injected into the molding cavity from the material injection portion 104 at the time of rubber molding can be quickly introduced into the supporting rubber 62.
The material guide portion 106 can be formed by an arbitrary route from the material injection portion 104 to the support rubber 62, and particularly, the material guide portion 106 of the present embodiment extends radially outward from the material injection portion 104 set in the vicinity of the outer peripheral end in the upper surface 102 of the mass member 58, further extends in the axial direction along the outer peripheral surface downward from the outer peripheral end of the upper surface 102 to reach the support rubber 62, and connects each material injection portion 104 and the support rubber 62 by the shortest route.
According to the engine mount 100 of the present embodiment, since the upper surface 102 of the mass member 58 is covered with the covering rubber 98, even if water or the like enters and stays in the internal space 80, rust or the like of the mass member 58 can be prevented. Further, by fixing the covering rubber 98 integrally molded with the supporting rubber 62 to the mass member 58, the strength and durability of the fixing of the supporting rubber 62 to the mass member 58 can be improved. Further, even if the flexible film 32 deformed at the time of vibration input abuts against the mass member 58, the generation of abnormal noise can be suppressed by the cushioning effect of the covering rubber 98. Further, since the surface of the mass member 58 is covered with the covering rubber 98, even when the mass member 58 becomes high in temperature due to, for example, heat from the outside, the covering rubber 98 can reduce the radiant heat from the mass member 58 to the flexible film 32, and an effect of suppressing a temperature rise of the enclosed liquid or the like in the flexible film 32 and the fluid chamber 36 can be expected, and an effect of suppressing vibration or abnormal noise due to resonance or the like of each member such as the mass member 58 and the cylindrical outer member 60 can also be expected.
In particular, since the material injection portion 104 of the support rubber 62 is provided in the cover rubber 98, even when the material injection portion 104 has a partially convex shape or the like, it is possible to avoid adverse effects on the characteristics or the like of the support rubber 62 constituting the dynamic damper 16. Further, since the material injection portion 104 is set in the vicinity of the outer peripheral end of the upper surface 102 of the mass member 58, even when the material injection portion 104 is convex, the flexible membrane 32 deformed at the time of vibration input can be prevented from colliding strongly with the material injection portion 104, and the deformation of the flexible membrane 32 can be prevented from being hindered, and adverse effects on durability and the like can be avoided.
In the engine mount 100 shown in fig. 8 to 9, the bracket 14 can be press-fitted and fixed to the second mounting member 20 in an externally fitted state, similarly to the engine mount 10 of the above embodiment. Except for this point, since the basic structure of the engine mount 100 of the present embodiment is the same as that of the engine mount 10 of the above embodiment, for the sake of easy understanding, the same reference numerals are given to the members and portions substantially the same as those of the above embodiment.
The specific shape, size, and the like of the mass member are merely examples, and may be appropriately changed depending on the vibration damping performance required of the dynamic damper, the allowable installation space of the engine mount in the vehicle, and the like.
The specific structure of the bracket is appropriately changed depending on the structure of the vehicle body side and the like. Further, the bracket is not necessarily limited to be press-fitted and fixed to the second mounting member, and may be fixed by means other than press-fitting, such as bolting.
In the above embodiment, the mass communication hole 66 penetrating the mass member 58 and the rubber communication hole 78 penetrating the support rubber 62 are illustrated as communication holes, but the communication hole may be either the mass communication hole 66 or the rubber communication hole 78. Further, the communication hole may be formed to open the space 80 to the atmosphere, and may be formed to penetrate the peripheral wall of the cylindrical outer member 60, for example. Further, the communication hole is not essential, and particularly in the solid type engine mount 90 shown in fig. 7, since there is no concern that the air elasticity hinders the deformation of the flexible film, the communication hole can be omitted.
In the above embodiment, the structure in which the dynamic vibration reducer 16 is disposed on the lower side of the holder main body 12 has been described, but the dynamic vibration reducer may be disposed on the upper side of the holder main body, for example.
In the above embodiment, the cylindrical exterior member 60 and the bracket 14 are press-fitted and fixed to the second mounting member 20 in an externally fitted state, but at least one of the cylindrical exterior member and the bracket may be press-fitted and fixed in an internally fitted state by being inserted into the inner periphery of the second mounting member, for example.
Further, in addition to the structure in which both ends in the axial direction are open as in the above-described embodiment, the cylindrical outer member may be a bottomed cylinder or the like in which only one end in the axial direction is open. In this case, the axial end of the cylindrical outer member is press-fitted and fixed to the second mounting member for reinforcement, and the mass member and the support rubber can be protected by the bottom wall portion of the cylindrical outer member.
The present invention is not limited to the engine mount, and can be applied to various known vibration isolators. Further, the present invention is applicable not only to an anti-vibration device for an automobile but also to an anti-vibration device for use other than an automobile.

Claims (11)

1. A vibration isolation device (10, 90, 100) having a structure in which a first mounting member (18) and a second mounting member (20) mounted to one of members constituting a vibration transmission system are elastically coupled to each other via a main rubber elastic body (22), the vibration isolation device (10, 90, 100) being characterized in that,
a bracket (14) is attached to the second attachment member (20), and an attachment portion (52) to be attached to any one of the members constituting the vibration transmission system is provided on the bracket (14),
the vibration isolation device (10, 90, 100) is provided with a cylindrical outer member (60) which is press-fitted and fixed to the second mounting member (20), a mass member (58) is arranged on the inner periphery of the cylindrical outer member (60), the cylindrical outer member (60) and the mass member (58) are elastically coupled by a support rubber (62) which is fixed to the outer peripheral portion of the mass member (58) to constitute a dynamic damper (16),
the cylindrical outer member (60) is open on both sides in the axial direction, one open end portion in the axial direction of the cylindrical outer member (60) is press-fitted and fixed to the second mounting member (20), and the mass member (58) is exposed from the cylindrical outer member (60) to the outside through the other opening in the axial direction of the cylindrical outer member (60),
the vibration isolation device (10, 90, 100) is provided with a reinforcing part (72) formed by bending the other opening end part of the cylindrical outer member (60) in the axial direction towards the inner circumferential side,
the support rubber (62) is disposed radially between the mass member (58) and the cylindrical outer member (60), and is also disposed axially between the mass member (58) and the reinforcing portion (72).
2. The anti-vibration device (10, 90, 100) according to claim 1,
the supporting rubber (62) is fixed to the reinforcing portion (72) of the cylindrical exterior member (60).
3. Anti-vibration device (10, 90, 100) according to claim 1 or 2,
a stepped portion (76) is provided at an axially intermediate portion of the cylindrical outer member (60).
4. Anti-vibration device (10, 90, 100) according to claim 1 or 2,
the cylindrical outer member (60) is open at the lower side, and a retaining protrusion (74) protruding inward is provided at an opening portion on the lower side of the cylindrical outer member (60), and the retaining protrusion (74) constitutes a fail-safe (82) that prevents the mass member (58) from coming out downward from the cylindrical outer member (60).
5. Anti-vibration device (10, 100) according to claim 1 or 2,
the second mounting member (20) is formed in a tubular shape, one opening in the axial direction of the second mounting member (20) is closed by the main rubber elastic body (22), the other opening in the axial direction of the second mounting member (20) is closed by a flexible film (32), a pressure receiving chamber (46) having a wall portion in which a part of the pressure receiving chamber is formed by the main rubber elastic body (22) and a balance chamber (48) having a wall portion in which a part of the balance chamber is formed by the flexible film (32) are formed between the main rubber elastic body (22) and the flexible film (32),
the cylindrical outer member (60) press-fitted and fixed to the second mounting member (20) extends outward in the axial direction, the mass member (58) is disposed outward in the axial direction with respect to the flexible film (32), the cylindrical outer member (60) and the mass member (58) are elastically coupled by the support rubber (62), and communication holes (66, 78) that open a space formed between the flexible film (32) and the mass member (58) in the axial direction to the atmosphere are formed in at least one of the cylindrical outer member (60), the mass member (58), and the support rubber (62).
6. The anti-vibration device (100) according to claim 5,
the mass member (58) is disposed on the lower side with respect to the flexible film (32), and a covering rubber (98) that covers the upper surface (102) of the mass member (58) is formed integrally with the support rubber (62).
7. The anti-vibration device (100) according to claim 6,
a material injection portion (104) for molding the support rubber (62) and the covering rubber (98) is provided in the covering rubber (98).
8. The vibration isolator (100) according to claim 7,
a material guide portion (106) is formed from the material injection portion (104) to the supporting rubber (62) by providing the material injection portion (104) in a state of protruding at a position closer to the outer peripheral end than the center in the upper surface (102) of the mass member (58) and locally increasing the wall thickness dimension of the covering rubber (98).
9. The vibration isolator (10) according to claim 5,
the mass member (58) is disposed on the lower side with respect to the flexible film (32), the communication hole (66) is formed so as to open on the upper surface of the mass member (58), and the upper surface of the mass member (58) is provided with a tapered surface (68) that is inclined downward toward the opening of the communication hole (66).
10. Anti-vibration device (10, 100) according to claim 5,
the mass member (58) is disposed on the lower side with respect to the flexible film (32), and the communication hole (78) is formed so as to open on the upper surface of the supporting rubber (62).
11. Anti-vibration device (10, 90, 100) according to claim 1 or 2,
the bracket (14) has a fitting cylinder portion (50) that is press-fitted and fixed to the second mounting member (20).
CN201811532431.7A 2017-12-22 2018-12-14 Vibration-proof device Active CN110030323B (en)

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EP0426938B1 (en) * 1989-11-09 1994-04-06 Firma Carl Freudenberg Rubber mounting with hydraulic damping
JP3362575B2 (en) * 1995-09-29 2003-01-07 東海ゴム工業株式会社 Mounting device and method of manufacturing the same
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JP5883312B2 (en) * 2011-03-25 2016-03-15 住友理工株式会社 Fluid-filled vibration isolator and manufacturing method thereof
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