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GB2239507A - Damping device - Google Patents

Damping device Download PDF

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Publication number
GB2239507A
GB2239507A GB9026007A GB9026007A GB2239507A GB 2239507 A GB2239507 A GB 2239507A GB 9026007 A GB9026007 A GB 9026007A GB 9026007 A GB9026007 A GB 9026007A GB 2239507 A GB2239507 A GB 2239507A
Authority
GB
United Kingdom
Prior art keywords
working chamber
compensation
chamber
passageway
damping device
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Withdrawn
Application number
GB9026007A
Other versions
GB9026007D0 (en
Inventor
Hajime Takeguchi
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.)
Nissan Motor Co Ltd
Original Assignee
Nissan Motor Co Ltd
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Nissan Motor Co Ltd filed Critical Nissan Motor Co Ltd
Publication of GB9026007D0 publication Critical patent/GB9026007D0/en
Publication of GB2239507A publication Critical patent/GB2239507A/en
Withdrawn legal-status Critical Current

Links

Classifications

    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16FSPRINGS; SHOCK-ABSORBERS; MEANS FOR DAMPING VIBRATION
    • F16F13/00Units comprising springs of the non-fluid type as well as vibration-dampers, shock-absorbers, or fluid springs
    • F16F13/04Units 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
    • F16F13/06Units 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
    • F16F13/08Units 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
    • F16F13/14Units of the bushing type, i.e. loaded predominantly radially

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Combined Devices Of Dampers And Springs (AREA)
  • Arrangement Or Mounting Of Propulsion Units For Vehicles (AREA)

Abstract

A damping device, eg for vehicle engine mountings, comprises a resilient member 16 mounted between rigid inner and outer sleeves 12, 14, a longer passageway 32 providing communication between a working chamber 22 containing fluid and a first compensation chamber 30, and a shorter passageway 36 providing communication between the working chamber 22 and a second compensation chamber (34 - Fig. 6). The resilient member 16 has openings therein defining diaphragms of different resilience eg 26, 42 bounding the working chamber 22 and the first and second compensation chambers. The longer passageway 32 and the diaphragms bounding the working chamber 22 and the first compensation chamber 30 are designed to damp lower frequency vibrations, eg due to engine running, while the shorter passageway 36 and the diaphragms bounding the working chamber and the second compensation chamber are designed to damp higher frequency vibrations, eg due to engine idling. A radial opening 28 divides part of the member 16 into portions 16a, 16b in which the first and second compensation chambers are respectively located. Reinforcing rings 46, 48 are embedded in the member 16. <IMAGE>

Description

1 FLUID FILLED ELASTOMERIC DA14PING DEVICE
BACKGROUND OF THE INVENTION 1. FIELD OF THE INVENTION
The present invention relates to a fluid f illed elastomeric damping device which is used as a power unit mounting to a vehicle body or the like.
2. DESCRIPTION OF THE PRIOR ART
Generally, a vehicular power unit consisting of an engine and transmission is mounted on a vehicle body by way of an elastomeric mounting so that vibrations of the power unit are not transmitted to the vehicle body.
An example of such a mounting is disclosed in Japanese Patent Provisional Publication No. 61-65935 and provided with a working chamber and compensation chamber intercommunicated through a single restrictive fluid passageway formed in an inner sleeve.
A disadvantage of the prior art mounting is that it cannot effect a desired damping action on both engine idling vibration (i.e., engine vibration at idling) and engine shake (i.e., engine vibration at vehicle running, which is lower in frequency and larger in amplitude than the engine idling vibration).
-I 2 Another disadvantage is that it has a difficulty in being designed so as to ef fect a desired damping action on low frequency vibration as engine shake (about 10 Hz), etc. since the single fluid passageway, which is formed in the inner sleeve and theref ore short, tends to cause the damping device to resonate at a high frequency, i.e., tends to cause an oscillatory system of a high resonant frequency, the mass of which oscillatory system is constituted by the fluid within the restrictive fluid passageway and the spring of which oscillatory system is constituted by the resilient walls defining the working and compensating chambers, i.e., the resilience in expansion and contraction of the working and compensation chambers.
A further disadvantage is that it cannot be durable for a long period of usage since the resilient walls defining the working and compensating chambers are needed to make the working and compensating chambers variable in volume largely.
SUMMARY OF THE INVENTION
It is accordingly an object of the present invention to provide a fluid filled elastomeric damping device which can provide desired damping actions in response to different vibration phenomena, e.g. engine idling vibration and engine shake.
z 3 In accordance with a preferred embodiment of the present invention as described hereinafter, there is provided a fluid filled elastomeric damping device which comprises rigid inner and outer sleeves having a space therebetween, a resilient member precompressed axially and radially thereof disposed within the space to connect the inner and outer sleeves together and thereby subdividing the space into two regions, a working chamber in one of the regions enclosed between the resilient member and the outer sleeve, the working chamber containing a fluid, first and second compensation chambers in the other of the regions and containing a fluid, and first and second restrictive fluid passageways of different lengths between the outer sleeve and the resilient member, the first restrictive fluid passageway being located at an axial end of the outer sleeve to extend circumferentially thereof for providing communication between the working chamber and the first compensation chamber, the second restrictive fluid passageway being located at the other axial end of the outer sleeve to extend circumferentially thereof for providing communication between the working chamber and the second compensation chamber.
As will become apparent from the following, the above structure is effective for solving the above 4 noted problems inherent in the prior art device. More particularly, the proposed structure can readily attain a restrictive fluid passageway of a sufficient length,' has improved durability, can be attained with a minimum number of constituent parts and is economical to manufacture and assemble.
The above and other features of the present invention are set forth with particularity in the appended claims and, together with advantages thereof, will best be understood from the following detailed description of an exemplary embodiment which is given with reference to the accompanying drawings.
BRIEF DESCRIPTION OF THE DRAWINGS
Fig. 1 is a perspective view of a f luid filled elastomeric damping device according to an embodiment of the present invention, with an outer sleeve thereof being omitted; Fig. 2 is a longitudinal sectional view of the damping device of Fig. 1; 20 Fig. 3 is a view similar to Fig. 2 but shows a process of fitting the resilient deformable member in the outer sleeve; Fig. 4 is a sectional view taken along the line W-W of Fig. 2; 25 Fig. 5 shows how a longer restrictive fluid passageway is developed within the damping device; 1.
r Fig. 6 is a sectional view taken along the line VI-VI of Fig. 2; and Fig. 7 shows how a shorter restrictive fluid passageway is developed within the damping device.
DESCRIPTION OF THE PREFERRED EMBODIMENT
Referring to Figs. 1 to 7 inclusive, a fluid filled elastomeric damping device according to an embodiment of the present invention is generally indicated by 10 and includes concentric rigid inner and outer sleeves 12, 14 and an elastomeric or resilient deformable member 16 interposed between the inner and outer sleeves 12, 14 to interconnect the same.
In use of the damping device 10. the inner sleeve 12 may be attached to a power unit 18 with a bolt (not shown) passing therethrough while the outer sleeve 14 is attached to a vehicle body 20 so that the power unit 18 is supported by way of the resilient deformable member 16 on the vehicle body 20.
Alternatively, the inner and outer sleeves 12, 14 may be attached to the power unit 18 and the vehicle body 20 respectively to produce the same effect.
The resilient deformable member 16 bounds or defines on one side thereof, i.e., on the lower side thereof in the drawings a working chamber 22 filled with hydraulic fluid "L" and has a narrow axial 1 6 opening 24 extending along the working chamber 22 so that a diaphragm 26 is defined between the working chamber 22 and the opening 24.
The resilient deformable member 16 has, on the other side thereof, i.e., on the upper side in the drawings and at an axially central portion thereof. a narrow radial opening 28 which axially separates the upper side portion thereof into two sections 16a. 16b, one 16a of which sections is f ormed with a f irst compensating chamber 30 filled with hydraulic fluid "L" and communicated through a longer restrictive fluid passageway 32 with the working chamber 22, and the other 16b is formed with a second compensating chamber 34 filled with hydraulic fluid "L" and communicated through a shorter restrictive fluid passageway 36 with the working chamber 22. In this embodiment, the first and second compensation chambers 30, 34, when viewed in a plane of projection perpendicular to the axis of the resilient member 16.
are formed into sector-like shapes arranged symmetrically on opposite sides of a diametrical line.
The resilient deformable member 16 further has narrow axial openings 38, 40 extending along the first and second compensating chambers 30r 34 so that diaphragms 42, 44 are defined between the openings 38, and compensation chambers 30, 34, respectively.
z 1 7 The resilient deformable member 16 is reduced in diameter at its opposite axial ends so as to provide stepped end portions 16c, 16d. Two axially aligned reinforcement rings 46, 48 of generally L-like section are embedded in the stepped end portions 16c,, 16d of the resilient deformable member 16 at locations adjacent to the peripheries thereof. The reinforcement rings 46, 48 have hollow part cylindrical portions 46a, 48a embedded in the axially separated sections 16a, 16b of the resilient deformable member 16 at locations adjacent to the outer peripheries thereof.
The resilient deformable member 16 is made of rubber or the like and bonded at the inner periphery thereof to the inner sleeve 12 by sulfurization and precompressed to fit at the outer periphery thereof in the outer sleeve 14. In this connection, the resilient deformable member 16 is firmly fitted in the outer sleeve 14 by the effect of the reinforcement rings 46, 48. This fitting is attained, as shown in Fig. 3, by precompressing the resilient deformable member 16 radially thereof and pushing the same axially into the outer sleeve 14 until the axially separated sections 16a. 16b of the resilient deformable member 16 are in contact with each other as shown in Fig. 2.
8 The longer and shorter restrictive fluid passageways 32, 36 are defined between the stepped end portions 16c, 16d of the resilient def ormable member 16 and the outer sleeve 14 when the resilient deformable member 16 and the outer sleeve 14 are assembled together. In this connection, the outer sleeve 14 has an inward flange 54 at a first end opposite to a second end through which the resilient deformable member 16 is pushed into the outer sleeve 14. After insertion of the resilient deformable member 16 into the outer sleeve 14, the second end is bent as shown by the dotted line in Fig. 3 and thus formed into an inward flange 56 so that two arcuate spaces are defined between the inward flanges 54. 56 and the stepped end portions 16c, 16d of the resilient member 16 to serve as the shorter restrictive fluid passageway 36 and the longer restrictive fluid passageway 32, respectively, as shown in Figs. 5 and 7. 20 The outer sleeve 14 is sealed by caulking at the inward flanges 54. 56 to the stepped end portions 16c, 16d of the resilient deformable member 16. The stepped end portion 16c of the resilient deformable member 16, which defines the above described longer restrictive fluid passageway 32, is formed with notches or cuts 32a, 32b through which the is 9 restrictive f luid passageway 32 communicates at the opposite longitudinal ends thereof with the working chamber 22 and the first compensation chamber 30. on the other hand, the stepped end. portion 16d of the resilient def ormable member 16, which def ines the shorter restrictive fluid passageway 36, is formed with notches or cuts 36a, 36b through which the restrictive fluid passageway 36 communicates at the opposite longitudinal ends thereof with the working chamber 22 and the second compensation chamber 34.
In operation, vibrations of the power unit 18 cause the inner and outer sleeves 12, 14 to move relative to each other. The relative movements of the inner and outer sleeves 12, 14 cause deformations of the resilient deformable member 16 and therefore variations of volume of the working chamber 22. The variations of volume of the working chamber 22 cause fluid flow between the working chamber 22 and the first compensation chamber 30 and/or the second compensation chamber 34.
In this instance, it is to be noted that the fluid filled elastomeric damping device 10 of this invention is provided with two restrictive fluid passageways through which fluid can flow between the working chamber 22 and the first and second compensation chambers 30, 34, i.e. fluid can flow between the working chamber 22 and the first compensation chamber 30 through the longer restrictive fluid passageway 32 and between the working chamber 22 and the second compensation chamber 34 through the shorter restrictive fluid passageway 36.
in this embodiment, the fluid flow through the longer restrictive fluid passageway 32 is adapted for damping or attenuating engine shake while the fluid flow through the short restrictive fluid flow passageway 34 is adapted for damping or attenuating engine idling vibration.
During engine shake:
For attenuating engine shake, which is of about 10 Hz and relatively large in amplitude (about lmm).
an oscillatory system, the mass of which is assumed to be constituted by the fluid "W within the longer restrictive fluid passageway 32 and the spring of which is assumed to be constituted by the diaphragms 26, 42 defining the working chamber 22 and the first compensation chamber 30, i.e., the resilience in expansion and contraction of the chambers 22 and 30, is designed to resonate at a frequency of about 10 Hz. By this, when the damping device 10 is subjected to engine vibrations at a frequency of about 10 Hz, it resonates to cause the fluid 'W' within the long restrictive fluid passageway 32 to move to-and-fro k 11 forcefully, whereby to damp or attenuate the engine shake by the ef f ect of loss of f luid f low due to the flow resistance of the longer restrictive fluid passageway 32.
During engine idling vibration:
During engine idling vibration of about 20 to 30 Hz and of a relatively small amplitude (about 0.3mm), little fluid flow occurs through the longer restrictive fluid passageway 32 since the loss of fluid f low through the longer restrictive passageway 32 becomes so large that fluid flow occurs between the working chamber 22 and the second compensation chamber 34 through the shorter restrictive f luid passageway 36, thus assisting deformation of the resilient deformable member 16 to reduce the dynamic spring constant thereof and thereby damping or attenuating the idling vibration.
In this connection. the damping device 10 is designed such that an oscillatory system. the mass of which is assumed to be constituted by the f luid I'Ll' within the shorter restrictive fluid passageway 36 and the spring of which oscillatory system is assumed to be constituted by the diaphragms 26, 44 defining the working chamber 22 and the second compensation chamber 34, resonates at a frequency of 30 Hz or a little larger frequency. By this, when engine vibrations are 12 equal to or less than 30 Hz, e.g. about 20 to 30 Hz, fluid flow through the shorter restrictive fluid passageway 36 occurs in response to variations in volume of the working chamber. 22 and the second compensation chamber 34, thus assisting deformation of the resilient deformable member 16 and thereby reducing the dynamic spring constant of the same efficiently.
From the foregoing, it will be understood that two restrictive fluid passageways, i.e., the longer restrictive fluid passageway 32 and shorter restrictive fluid passageway 36 are provided to communicate the working chamber 22 with the first and second compensation chambers 30, 34, respectively, thus making it possible to provide a desired damping action on both engine idling vibration and engine shake.
It will be further understood that since the longer restrictive fluid passageway 30 is formed along the outer periphery of the outer sleeve 14 it becomes possible to attain a sufficiently large length of the restrictive fluid passageway 30, thus making it possible to set the resonant frequency of an oscillatory system at about 10 Hz, the mass of which oscillatory system is assumed to be constituted by the fluid 'W, within the restrictive fluid passageway 30 13 and the spring of which oscillatory system is assumed to be constituted by the diaphragms 42, 44 defining the working chamber 22 and the first compensation chamber 30, i.e. the resilience in expansion and contraction of the chambers 42 and 44, and provide a desired damping action of the engine shake.
It will be further understood that since the resilient deformable member 16 is fitted in the outer sleeve 14 while being precompressed axially and radially thereof expansion of the resilient deformable member 16 causes the internal stress due to the above precompression to reduce, thus making it possible to reduce the load actually applied to the resilient deformable member 16 in response to variations in volume of the working chamber 22 and the compensation chambers 30, 34 and therefore making it possible to improve the durability considerably.
It will be further understood that the longer and shorter restrictive fluid passageways 32, 36 are formed by the stepped end portions 16c, 16d of the resilient deformable member 16 in which the reinforcement rings 46, 48 are embedded and by the inward flanges 54, 56 of the outer sleeve 14, sealed to the stepped end portions 16c, 16d by caulking, thus making it possible to attain the restrictive fluid passageways 32, 36 without requiring additional 14 independent parts or elements, A. e., with a minimum number of constituent parts, and therefore reduce the manufacturing and assembling expense.
While the damping device of. this invention has been described as shown as being applied to damp or attenuate engine idling vibration and engine shake, it is not limited to such vibrations but can be applied to other kinds of vibrations.
j _ 157- CLAM: 1. An elastomeric damping device comprising: rigid inner and outer sleeves having a space therebetween; 5 a resilient member precompressed axially and radially thereof, disposed within said space to connect said inner and outer sleeves together and thereby subdividing said space into two regions; a working chamber in one of said regions enclosed between said resilient member and said outer sleeve, said working chamber containing a fluid; first &nd second compensation chambers in the other of said regions and containing a fluid; and first and second restrictive fluid passageways between said outer sleeve and said resilient member and of different length; said first restrictive fluid passageway being located at an axial end of said outer sleeve to extend circumferentially thereof for providing communication between said working chamber and said first compensation chamber; said second restrictive fluid passageway being located at the other axial end of said outer sleeve to extend circumferentially thereof for providing communication between said working chamber and said 1 1 -K- second compensation chamber.
2. The damping device according to claim 1, wherein said resilient member has three axial openings extending along said working chamber and said first and second compensation chambers so that three diaphragms are defined between said chambers and said axial openings, respectively, and said diaphragms bounding said first and second compensation chambers differ in resilience.
3. The damping device according to claim 2, wherein said first restrictive fluid passageway is longer than said second restrictive fluid passageway, and said diaphragms bounding said working chamber and said first compensation chamber and said first restrictive fluid passageway are adapted for damping vibrations of relatively low frequency while said diaphragms bounding said working chamber and said second compensation chambers and said second restrictive fluid passageway are adapted for damping vibrations of relatively high frequency.
4. The damping device according to claim 3, wherein said vibration of relatively low frequency is engine shake, and said vibration of relatively high frequency k is engine idling vibration.
5. The damping device according to claim 4, wherein said diaphragms bounding said working chamber and said f irst compensation chamber constitute a spring of an oscillatory system while the f luid within said f irst restrictive fluid passageway constitutes a mass of said oscillatory system, said oscillatory system having a resonance frequency of about 10 Hz.
6. The damping device according to claim 4 or 5, wherein said diaphragms bounding said working chamber and said second compensation chamber constitute a spring of an oscillatory system while the fluid within said second restrictive fluid passageway constitutes a mass of said second mentioned oscillatory system, said second method oscillatory system attenuates at a frequency of 30 Hz or a little larger frequency.
7. The damping device according to any preceding claim, wherein said working chamber is bounded on one side of said resilient member while said f irst and second compensation chambers are bounded on the other side of said resilient member, said resilient member being axially separated on said other side into first and second sections so that said f irst and second 1 X -1g - compensation chambers are bounded by said axially separated sections of said resilient member, respectively.
8. The damping device according to any preceding claim, further comprising two axially aligned reinforcement rings of generally L-like section, said resilient member being reduced in diameter at opposite axial ends so as to provide stepped end portions in which said reinforcement rings are embedded at locations adjacent outer peripheries of said stepped end portions.
9. The damping device according to claim 8, wherein said outer sleeve has at the opposite axial ends inward f langes which co-operate with said stepped end portions of said resilient member to define therebetween arcuate spaces serving as said first and second restrictive fluid passageways.
10. The damping device according to claim 9, wherein said reinforcement rings have hollow part-cylindrical portions embedded in said axially separated sections of said resilient member at locations adjacent to outer peripheries thereof.
i 1 -1q- 11. A fluid filled elastomeric damping device having a working chamber and plural compensation chambers coupled thereto by respective f luid f low passageways, and wherein the working chamber def ines with each of the compensation chambers an oscillatory system having a predetermined fundamental frequency of vibration, whereby said device provides preferential damping at a plurality of different vibration frequencies.
12. An anti-vibration mounting comprising a fluid filled elastomeric damping device defining two mounting locations and having a working chamber communicating with a plurality of compensation chambers for selective resiliently damped fluid transfer therebetween in response to vibrations applied at said mounting locations, said working chamber and each of said compensation chambers together with the communicating f luid-f low passageway therebetween defining an oscillatory system having a selected fundamental frequency whereby said device provides preferential damping at a plurality of different frequencies.
13. A fluid filled elastomeric damping device substantially as herein described with reference to the accompanying drawings.
Published 1991 at Ile Patent Office, State House. 66171 High Holborn. London WC1 R 47P. Further copies may be obtained from Sales Branch. Unit 6. Nine Mile Point Cwmfelinfach. Cross Keys, Nm"rt NPI 7HZ. Printed by Multiplex techniques lid, St Mary Cray, Kent.
GB9026007A 1989-11-29 1990-11-29 Damping device Withdrawn GB2239507A (en)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
JP1309732A JP2616064B2 (en) 1989-11-29 1989-11-29 Fluid-filled power unit mount

Publications (2)

Publication Number Publication Date
GB9026007D0 GB9026007D0 (en) 1991-01-16
GB2239507A true GB2239507A (en) 1991-07-03

Family

ID=17996628

Family Applications (1)

Application Number Title Priority Date Filing Date
GB9026007A Withdrawn GB2239507A (en) 1989-11-29 1990-11-29 Damping device

Country Status (4)

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JP (1) JP2616064B2 (en)
DE (1) DE4037891A1 (en)
FR (1) FR2655113A1 (en)
GB (1) GB2239507A (en)

Cited By (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB2289110A (en) * 1994-05-05 1995-11-08 Pullman Co Fluid-filled elastomeric suspension bushing assembly
US5547172A (en) * 1993-12-09 1996-08-20 Hutchinson Hydraulic antivibration supports, and to methods of manufacturing them
GB2317667A (en) * 1996-09-25 1998-04-01 Draftex Ind Ltd An engine mount assembly having a one-piece moulded support
GB2381846A (en) * 2001-11-09 2003-05-14 Avon Vibration Man Syst Ltd A mounting device which is hydraulically damped

Families Citing this family (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE4137977C2 (en) * 1991-11-19 1995-06-14 Freudenberg Carl Fa Multi-chamber hydraulic bush
DE4305808C2 (en) * 1993-02-25 1995-05-11 Freudenberg Carl Fa Hydraulically damping sleeve rubber spring
FR2739669B1 (en) * 1995-10-05 1998-09-04 Hutchinson HYDRAULIC ANTIVIBRATORY SUPPORT
FR2814521B1 (en) * 2000-09-26 2003-06-06 C F Gomma Barre Thomas HYDROELASTIC ARTICULATION WITH HIGH FREQUENCY DYNAMIC BEHAVIOR
DE102010015579B4 (en) * 2010-04-19 2012-10-25 Carl Freudenberg Kg Decoupled hydraulic jack

Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB2207215A (en) * 1987-06-23 1989-01-25 Nissan Motor Vibration insulating bushing
US4895353A (en) * 1988-06-28 1990-01-23 The Pullman Company Fluid filled elastomeric damping device
EP0353700A2 (en) * 1988-08-02 1990-02-07 Bridgestone Corporation Vibration damping device

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* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS6288834A (en) * 1985-10-15 1987-04-23 Bridgestone Corp Vibro-isolator
FR2599450B1 (en) * 1986-06-03 1990-08-10 Hutchinson IMPROVEMENTS ON HYDRAULIC ANTI-VIBRATION SUPPORT SLEEVES
DE3724432A1 (en) * 1987-07-23 1989-02-02 Freudenberg Carl Fa SLEEVE RUBBER SPRING
JP2592077B2 (en) * 1987-11-06 1997-03-19 鬼怒川ゴム工業株式会社 Fluid filled type vibration damping device
FR2650356B1 (en) * 1989-07-31 1994-05-27 Hutchinson IMPROVEMENTS MADE TO MAN CHONS HYDRAULIC ANTI-VIBRATOR

Patent Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB2207215A (en) * 1987-06-23 1989-01-25 Nissan Motor Vibration insulating bushing
US4895353A (en) * 1988-06-28 1990-01-23 The Pullman Company Fluid filled elastomeric damping device
EP0353700A2 (en) * 1988-08-02 1990-02-07 Bridgestone Corporation Vibration damping device

Cited By (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US5547172A (en) * 1993-12-09 1996-08-20 Hutchinson Hydraulic antivibration supports, and to methods of manufacturing them
GB2289110A (en) * 1994-05-05 1995-11-08 Pullman Co Fluid-filled elastomeric suspension bushing assembly
GB2289110B (en) * 1994-05-05 1998-02-18 Pullman Co Fluid-filled elastomeric suspension bushing
GB2317667A (en) * 1996-09-25 1998-04-01 Draftex Ind Ltd An engine mount assembly having a one-piece moulded support
GB2381846A (en) * 2001-11-09 2003-05-14 Avon Vibration Man Syst Ltd A mounting device which is hydraulically damped

Also Published As

Publication number Publication date
GB9026007D0 (en) 1991-01-16
DE4037891A1 (en) 1991-06-06
FR2655113A1 (en) 1991-05-31
JPH03168441A (en) 1991-07-22
JP2616064B2 (en) 1997-06-04

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