CA1301787C - Fluid filled elastomeric damping device - Google Patents
Fluid filled elastomeric damping deviceInfo
- Publication number
- CA1301787C CA1301787C CA000542495A CA542495A CA1301787C CA 1301787 C CA1301787 C CA 1301787C CA 000542495 A CA000542495 A CA 000542495A CA 542495 A CA542495 A CA 542495A CA 1301787 C CA1301787 C CA 1301787C
- Authority
- CA
- Canada
- Prior art keywords
- fluid
- chamber
- elastomeric
- chambers
- rigid
- 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.)
- Expired - Lifetime
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Classifications
-
- B—PERFORMING OPERATIONS; TRANSPORTING
- B60—VEHICLES IN GENERAL
- B60G—VEHICLE SUSPENSION ARRANGEMENTS
- B60G13/00—Resilient suspensions characterised by arrangement, location or type of vibration dampers
- B60G13/02—Resilient suspensions characterised by arrangement, location or type of vibration dampers having dampers dissipating energy, e.g. frictionally
- B60G13/06—Resilient suspensions characterised by arrangement, location or type of vibration dampers having dampers dissipating energy, e.g. frictionally of fluid type
-
- 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
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- Engineering & Computer Science (AREA)
- General Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- Combined Devices Of Dampers And Springs (AREA)
Abstract
FLUID FILLED ELASTOMERIC DAMPING DEVICE
Abstract A fluid filled engine mount for absorbing shock and dampening structural agitation is provided in which an elastomeric diaphragm and an associated air chamber cooperate with a fluid filled chamber to allow high frequency, low amplitude structural agitation to the mount to occur with very little pressure developing in the fluid chambers and, accordingly, a slight damping response. The fluid chambers are included within an elastomeric shear spring spacing a rigid outer housing including the diaphragm and air chamber from a rigid inner member. The housing and inner rigid member are typically associated with an engine frame and engine, respectively. The diaphragm is restrained against exces-sive deflection by an outer sleeve which comprises a restraint stop for the diaphragm. Upon contact of the diaphragm to the outer sleeve, pressure is developed quickly in the fluid chambers which then activates either a tuned fluid resonance channel or a restrictive fluid flow path for dampening of the agitation.
Abstract A fluid filled engine mount for absorbing shock and dampening structural agitation is provided in which an elastomeric diaphragm and an associated air chamber cooperate with a fluid filled chamber to allow high frequency, low amplitude structural agitation to the mount to occur with very little pressure developing in the fluid chambers and, accordingly, a slight damping response. The fluid chambers are included within an elastomeric shear spring spacing a rigid outer housing including the diaphragm and air chamber from a rigid inner member. The housing and inner rigid member are typically associated with an engine frame and engine, respectively. The diaphragm is restrained against exces-sive deflection by an outer sleeve which comprises a restraint stop for the diaphragm. Upon contact of the diaphragm to the outer sleeve, pressure is developed quickly in the fluid chambers which then activates either a tuned fluid resonance channel or a restrictive fluid flow path for dampening of the agitation.
Description
1~0~7~
FLUID FILLED ELASTOMERIC D~PING DEVICE
Background of the Invention This invention relates generally to fluid filled elastomeric damping devices and more particularly relates to a flu~d damped device of the type which is mounted to vehicles and which uses both an elastomeric spring and flow of fluid for absorbing shock, structural leveling and energy dlssipation.
It has been a constant problem to control and/or eliminate vibration and noise in automotive vehicles, while continuously improving the ride and comfort.
Conventional spring dampers or elastomeric-hydraulic mounts typically have employed a housing having an elast-omeric spring in the housing disposed to provide a load-carrying capacity for the damper. Actuation of the flowof fluid is accomplished by stressing the elastomeric spring.
It is well known that for best performance, in a fluid engine mount, damping should be at a maximum at the natural frequency of the mount system. For ~large vibra-tion amplitudes in.the order of plus or minus 0.5 mm or greater, good performance is obtained when phase angles of twenty-five degrees or more occur at the resonant frequency. However, for small amplitudes, in the order of plus or minus 0.1 mm or less, damping is not desired as an associated high dynamic spring rate will occur.
Various schemes have addressed this problem with some success. Many of the schemes are based on moving a partition of some material to permit limited free motion between two fluid filled chambers.
One attempt has been the use of a fluid filled elastomeric bushing as described in U.S. Patent 3,698,703 assigned to the General Tire & Rubber Company. This type of device, however, when subjected to high frequency vibrations would have high dynamic spring rates and thus ~3~1~787 poor high frequency performance. Various other devl.ces have -tried to address h:i.gh frequency performance prob:l.ems by using two liquid fluid chambers in which a partition member permits onl.y limited free fluid mo-tion be-tween -t.he two fluid filled chambers. These devices are designed so that the damping should be at a maximum at the natural frequency of the mount system. These devices, although generally effective, are complex in design, involving moving parts with associa-ted high cost and reliability problems. Examples of such devices are U.S. Patent 4,159,091, to Le Sa].ver and Canadian Patent 1,240,346 issued August 9, 1988, N. deVries.
The present inventi~n contemplates a new and improved suspension member for load-carrying and selectively varying damping response to structural agitation which overcomes the problems recited above.
The subject suspension device is simple in design, economical to manufacture, readily adaptable to a plurality of suspension and mounting member uses with items having a variety of dimensional characteristics and operating vibrations and which provides improved load carrying suspension with improved shock absorption and energy dissipation.
Brief Descri -tlon of the Invention p Generally, the presen-t lnvention contemplates a new and improved fluid filled engine mount for decoupling the high frequency, low amplitude dynamic properties of the mount to improve high frequency performance. The device allows small movements of the mount, which are associated with high frequency vibration, without incurring damping or high dynamic spring rates. The device i.ncludes a rigid ou-ter housing and a rigid inner member which are associa-ted with the vehicle frame and engine, respectively.
An elastomeric shear spring spaces the housing from ~30~
the inner member and includes a fluid-containing chamber with a restricted fluid flow path. A pressure relief means is associated with the fluid chamber to decouple the dynamic properties produced by small movements of the 5 mount such as are normally associated with high frequency vibration. The pressure relief means preferably compris-es a restrained elastomeric diaphragm in association with a recess providing an air chamber in the wall of the outer housing. During small movements of the mount, the 10 elastomeric diaphragm deforms to relieve the pressure in the fluid chamber as opposed to deforming the shear spring or inducing fluid flow through the restricted flow path~
In accordance with another aspect of the present 15 invention, the pressure relief means comprises an elasto-meric coating and a rigid outer sleeve sandwiching an annular recess in the housing side wall portion. The sleeve restrains the diaphragm from excess radially outwardly directed deformation upon compression of the 20 mount.
In accordance with another aspect of the present invention, opposed pressure relief means are employed adjacent opposed fluid containing chambers in communica-tion through the restricted flow path.
- 25 The principal object of the invention is the provision of a fluid filled engine mount including a decoupling feature for decoupling high frequency struc-tural agitation from normal mount spring and damping structural components for improved high frequency perfor-30 mance of the mount.
Another object of the present invention is the provision of an engine mount that offers good operational damping at the natural frequency of the mount system for low frequency, high amplitude structural agitation, while 35 avoiding damping and consequently, a high dynamic spring ~3a~7a7 rate, for high fre~uency, low amplitude structural ayita-tion.
Still other objects and advantages of the invention will become apparent to those skilled in the art upon a 5 reading and understanding of the following specification.
Brief Description of the Drawi _ The invention may take physical form in certain parts and arrangements of parts, a preferred and alterna-tive embodiment of which will be described in detail ln 10 this specification and illustrated in the accompanying drawings which form a part hereof and wherein:
FIGURE 1 is an elevation view in partial section of an engine mount formed in accordance with the present invention;
FIGURE 2 is a cross-sectional view of the mount taken along lines 2-2 of FIGURE l;
FIGURE 3 is a cross-sectional view taken along lines 3-3 of FIGURE l; and, FIGURE 4 is a cross-sectional view illustrating an 20 alternative embodiment of an engine mount formed in accordance with the present invention.
Detailed Description of the Preferred Embodiment Referring now to the drawings wherein the showings are for purposes of illustrating the preferred embodi-25 ments of the invention only and not for purposes oflimiting same, the FIGURES show a fluid filled elastomer-ic damping device particularly configured for use as an engine mount. With particular reference to FIGURES 1 through 3, the device 10 includes a rigid outer housing 30 12 and a rigid inner member or sleeve 14 for association with an engine and an engine frame (not shown), respec-tively. The outer housing 12 and inner sleeve 14 are generally annular in cross-sectional configuration which is a conventional configuration for engine mount devices 35 or support bushings. An elastomeric shear spring 16 130iL~
spaces the inner sleeve 14 from the outer housing 12 and is bonded to the inner sleeve at a sleeve engaging wall 18 and is bonded to the housing at a housing engaging wall 20. An outer support ring 15 (See FIG. 2) may be used for bonding the outer portion of shear spring 16 instead of directly bonding it to engaging wall 20. The bond is achieved with conventional chemical bonding techniques.
The shear spring 16 includes first and second fluid chambers 26, 28 which are in fluid communication through a peripheral restricted flow path 30 for shock dampening upon deformation of the sprlng 16 and consequent expan-sion or compression of the chambers 26, 28 due to shocks emparted to the device 10. The fluid contained in the chambers 26, 28 and transmitted through the path 30 comprises a conventional hydraulic fluid. It should be noted that the chambers 26, 28 are sealed against the outer housing such that fluid may only be contained in the chambers 26, 28 or the path 30. Damping of structur-20 al agitation by restricted flow of a fluid in associationwith an elastomeric.shear spring is particularly suc-cessful against low frequency, high amplitude shocks to the device 10.
The spring 16 also includes voids 32 which 25 facilitate the elastic deformation of the spring.
It is a feature of the invention that a pressure relief means is disposed in the housing 12 for associa-tion with the fluid chambers for the selective relief of pressure formed in the chamber by structural agitation.
30 Such selective relief decouples the high frequency dynam-ic agitation to improve the high frequency performance of the mount. More particularly, the pressure relief means comprises a recess or void 40, 42 in the rigid housing side wall portion 44 which is sandwiched by an elastomer-35 ic inner wall coating 46 and a rigid outer sleeve 48.
Adjacent the recesses 40, 42 the coating 46 comprises anelastomeric d.iaphragm whlch can deform into the recess but is restrained against excessive deformati.on by the outer sleeve 48. Typically coating 46 is bonded to 5 housing 12.
In operation, the coating 46 essentially separates the fluid chambers 26, 28 from an associated pair of air or gas chambers comprising the recesses 40, 42. The coating 46 operates as a diaphragm which is allowed to 10 move with the fluid for small amplitude structural agita-tion to the mount 10, or motions of the mount 10 before restrainment of the diaphragm for larger motions. More particularly, small oscillations such as low amplitude structural shocks deflect the coating 46 into the recess-15 es 40, 42 to a lesser extent so that the coating does notcontact the outer sleeve restraint stop 48. As a result, very little pressure is developed within the fluid cham-bers to cause a damping operation. For larger ampli-tudes, the coating 46 will deform to the extent to con-20 tact the outer sleeve restraint. Once the outer sleeveis contacted, pressure is developed quickly in the fluid and the chambers 26, 28. This rise in pressure then activates either a tuned fluid resonance channel or a simple restriction orifice or path as shown~ With par-25 ticular reference to FIGURE 3 it should be noted that themount 10 is ali.gned preferably so that vibration and agitation occurs in a direction substantially aligned from recess to recess, or, in other words, from fluid chamber to fluid chamber, as generally indicated by the 30 arrows illustrated within the rigid inner member 14.
With particular reference to FIGURE 4, an alternative embodiment of the i.nvention is shown. For ease of understanding, like elements in the device shown in FIGURE 4 to the device of FIGURES 1 -3 are illustrated 35 with a like numeral with a primed suffix and new elements ~3~ 7 are identified by new numerals. In this embodiment an air chamber 54, which can be selectively pressurized, works with recess chamber 40' which is also selectively pressurizable so that the damping response of the mount 5 10' can be adjusted for selective operational response.
The feature provides for an active damping device. The pressurizing of the device being by conventional means is known in the art. In operation, fluid chamber 56 commu-nicates with generally opposite fluid chambers 58, 60 10 through restricted fluid flow paths 62, 64 disposed about the periphery of elastomeric shear spring 66. Diaphragm 46' and outer sleeve 48' sandwich the recess 40' in the housing sidewall 44'. The outer sleeve 48' similarly provides a restraining stop against deflection of the 15 diaphragm 46' into the recess 40'.
It is withLn the scope of the invention to provide a pressure relief recess in a wide variety of shapes or configurations. In addition, the coating diaphragm itself may alternately comprise a wide variety of config-20 uration and shapes such as support plates with restric-tive orifices, elastomers including a wire mesh or screen, and rigid walls or fabric molded into the coating material.
The invention has been described with reference to a 25 preferred and alternative embodiment. Obviously, modifi-cations and alterations will occur to others upon a reading and understanding of this specification. It is our intention to include all such modifications and alterations insofar as they come within the scope of the 30 appended claims or the equivalents thereof.
~ 7 --
FLUID FILLED ELASTOMERIC D~PING DEVICE
Background of the Invention This invention relates generally to fluid filled elastomeric damping devices and more particularly relates to a flu~d damped device of the type which is mounted to vehicles and which uses both an elastomeric spring and flow of fluid for absorbing shock, structural leveling and energy dlssipation.
It has been a constant problem to control and/or eliminate vibration and noise in automotive vehicles, while continuously improving the ride and comfort.
Conventional spring dampers or elastomeric-hydraulic mounts typically have employed a housing having an elast-omeric spring in the housing disposed to provide a load-carrying capacity for the damper. Actuation of the flowof fluid is accomplished by stressing the elastomeric spring.
It is well known that for best performance, in a fluid engine mount, damping should be at a maximum at the natural frequency of the mount system. For ~large vibra-tion amplitudes in.the order of plus or minus 0.5 mm or greater, good performance is obtained when phase angles of twenty-five degrees or more occur at the resonant frequency. However, for small amplitudes, in the order of plus or minus 0.1 mm or less, damping is not desired as an associated high dynamic spring rate will occur.
Various schemes have addressed this problem with some success. Many of the schemes are based on moving a partition of some material to permit limited free motion between two fluid filled chambers.
One attempt has been the use of a fluid filled elastomeric bushing as described in U.S. Patent 3,698,703 assigned to the General Tire & Rubber Company. This type of device, however, when subjected to high frequency vibrations would have high dynamic spring rates and thus ~3~1~787 poor high frequency performance. Various other devl.ces have -tried to address h:i.gh frequency performance prob:l.ems by using two liquid fluid chambers in which a partition member permits onl.y limited free fluid mo-tion be-tween -t.he two fluid filled chambers. These devices are designed so that the damping should be at a maximum at the natural frequency of the mount system. These devices, although generally effective, are complex in design, involving moving parts with associa-ted high cost and reliability problems. Examples of such devices are U.S. Patent 4,159,091, to Le Sa].ver and Canadian Patent 1,240,346 issued August 9, 1988, N. deVries.
The present inventi~n contemplates a new and improved suspension member for load-carrying and selectively varying damping response to structural agitation which overcomes the problems recited above.
The subject suspension device is simple in design, economical to manufacture, readily adaptable to a plurality of suspension and mounting member uses with items having a variety of dimensional characteristics and operating vibrations and which provides improved load carrying suspension with improved shock absorption and energy dissipation.
Brief Descri -tlon of the Invention p Generally, the presen-t lnvention contemplates a new and improved fluid filled engine mount for decoupling the high frequency, low amplitude dynamic properties of the mount to improve high frequency performance. The device allows small movements of the mount, which are associated with high frequency vibration, without incurring damping or high dynamic spring rates. The device i.ncludes a rigid ou-ter housing and a rigid inner member which are associa-ted with the vehicle frame and engine, respectively.
An elastomeric shear spring spaces the housing from ~30~
the inner member and includes a fluid-containing chamber with a restricted fluid flow path. A pressure relief means is associated with the fluid chamber to decouple the dynamic properties produced by small movements of the 5 mount such as are normally associated with high frequency vibration. The pressure relief means preferably compris-es a restrained elastomeric diaphragm in association with a recess providing an air chamber in the wall of the outer housing. During small movements of the mount, the 10 elastomeric diaphragm deforms to relieve the pressure in the fluid chamber as opposed to deforming the shear spring or inducing fluid flow through the restricted flow path~
In accordance with another aspect of the present 15 invention, the pressure relief means comprises an elasto-meric coating and a rigid outer sleeve sandwiching an annular recess in the housing side wall portion. The sleeve restrains the diaphragm from excess radially outwardly directed deformation upon compression of the 20 mount.
In accordance with another aspect of the present invention, opposed pressure relief means are employed adjacent opposed fluid containing chambers in communica-tion through the restricted flow path.
- 25 The principal object of the invention is the provision of a fluid filled engine mount including a decoupling feature for decoupling high frequency struc-tural agitation from normal mount spring and damping structural components for improved high frequency perfor-30 mance of the mount.
Another object of the present invention is the provision of an engine mount that offers good operational damping at the natural frequency of the mount system for low frequency, high amplitude structural agitation, while 35 avoiding damping and consequently, a high dynamic spring ~3a~7a7 rate, for high fre~uency, low amplitude structural ayita-tion.
Still other objects and advantages of the invention will become apparent to those skilled in the art upon a 5 reading and understanding of the following specification.
Brief Description of the Drawi _ The invention may take physical form in certain parts and arrangements of parts, a preferred and alterna-tive embodiment of which will be described in detail ln 10 this specification and illustrated in the accompanying drawings which form a part hereof and wherein:
FIGURE 1 is an elevation view in partial section of an engine mount formed in accordance with the present invention;
FIGURE 2 is a cross-sectional view of the mount taken along lines 2-2 of FIGURE l;
FIGURE 3 is a cross-sectional view taken along lines 3-3 of FIGURE l; and, FIGURE 4 is a cross-sectional view illustrating an 20 alternative embodiment of an engine mount formed in accordance with the present invention.
Detailed Description of the Preferred Embodiment Referring now to the drawings wherein the showings are for purposes of illustrating the preferred embodi-25 ments of the invention only and not for purposes oflimiting same, the FIGURES show a fluid filled elastomer-ic damping device particularly configured for use as an engine mount. With particular reference to FIGURES 1 through 3, the device 10 includes a rigid outer housing 30 12 and a rigid inner member or sleeve 14 for association with an engine and an engine frame (not shown), respec-tively. The outer housing 12 and inner sleeve 14 are generally annular in cross-sectional configuration which is a conventional configuration for engine mount devices 35 or support bushings. An elastomeric shear spring 16 130iL~
spaces the inner sleeve 14 from the outer housing 12 and is bonded to the inner sleeve at a sleeve engaging wall 18 and is bonded to the housing at a housing engaging wall 20. An outer support ring 15 (See FIG. 2) may be used for bonding the outer portion of shear spring 16 instead of directly bonding it to engaging wall 20. The bond is achieved with conventional chemical bonding techniques.
The shear spring 16 includes first and second fluid chambers 26, 28 which are in fluid communication through a peripheral restricted flow path 30 for shock dampening upon deformation of the sprlng 16 and consequent expan-sion or compression of the chambers 26, 28 due to shocks emparted to the device 10. The fluid contained in the chambers 26, 28 and transmitted through the path 30 comprises a conventional hydraulic fluid. It should be noted that the chambers 26, 28 are sealed against the outer housing such that fluid may only be contained in the chambers 26, 28 or the path 30. Damping of structur-20 al agitation by restricted flow of a fluid in associationwith an elastomeric.shear spring is particularly suc-cessful against low frequency, high amplitude shocks to the device 10.
The spring 16 also includes voids 32 which 25 facilitate the elastic deformation of the spring.
It is a feature of the invention that a pressure relief means is disposed in the housing 12 for associa-tion with the fluid chambers for the selective relief of pressure formed in the chamber by structural agitation.
30 Such selective relief decouples the high frequency dynam-ic agitation to improve the high frequency performance of the mount. More particularly, the pressure relief means comprises a recess or void 40, 42 in the rigid housing side wall portion 44 which is sandwiched by an elastomer-35 ic inner wall coating 46 and a rigid outer sleeve 48.
Adjacent the recesses 40, 42 the coating 46 comprises anelastomeric d.iaphragm whlch can deform into the recess but is restrained against excessive deformati.on by the outer sleeve 48. Typically coating 46 is bonded to 5 housing 12.
In operation, the coating 46 essentially separates the fluid chambers 26, 28 from an associated pair of air or gas chambers comprising the recesses 40, 42. The coating 46 operates as a diaphragm which is allowed to 10 move with the fluid for small amplitude structural agita-tion to the mount 10, or motions of the mount 10 before restrainment of the diaphragm for larger motions. More particularly, small oscillations such as low amplitude structural shocks deflect the coating 46 into the recess-15 es 40, 42 to a lesser extent so that the coating does notcontact the outer sleeve restraint stop 48. As a result, very little pressure is developed within the fluid cham-bers to cause a damping operation. For larger ampli-tudes, the coating 46 will deform to the extent to con-20 tact the outer sleeve restraint. Once the outer sleeveis contacted, pressure is developed quickly in the fluid and the chambers 26, 28. This rise in pressure then activates either a tuned fluid resonance channel or a simple restriction orifice or path as shown~ With par-25 ticular reference to FIGURE 3 it should be noted that themount 10 is ali.gned preferably so that vibration and agitation occurs in a direction substantially aligned from recess to recess, or, in other words, from fluid chamber to fluid chamber, as generally indicated by the 30 arrows illustrated within the rigid inner member 14.
With particular reference to FIGURE 4, an alternative embodiment of the i.nvention is shown. For ease of understanding, like elements in the device shown in FIGURE 4 to the device of FIGURES 1 -3 are illustrated 35 with a like numeral with a primed suffix and new elements ~3~ 7 are identified by new numerals. In this embodiment an air chamber 54, which can be selectively pressurized, works with recess chamber 40' which is also selectively pressurizable so that the damping response of the mount 5 10' can be adjusted for selective operational response.
The feature provides for an active damping device. The pressurizing of the device being by conventional means is known in the art. In operation, fluid chamber 56 commu-nicates with generally opposite fluid chambers 58, 60 10 through restricted fluid flow paths 62, 64 disposed about the periphery of elastomeric shear spring 66. Diaphragm 46' and outer sleeve 48' sandwich the recess 40' in the housing sidewall 44'. The outer sleeve 48' similarly provides a restraining stop against deflection of the 15 diaphragm 46' into the recess 40'.
It is withLn the scope of the invention to provide a pressure relief recess in a wide variety of shapes or configurations. In addition, the coating diaphragm itself may alternately comprise a wide variety of config-20 uration and shapes such as support plates with restric-tive orifices, elastomers including a wire mesh or screen, and rigid walls or fabric molded into the coating material.
The invention has been described with reference to a 25 preferred and alternative embodiment. Obviously, modifi-cations and alterations will occur to others upon a reading and understanding of this specification. It is our intention to include all such modifications and alterations insofar as they come within the scope of the 30 appended claims or the equivalents thereof.
~ 7 --
Claims (17)
1. A fluid filled engine mount comprising:
a rigid housing including a side wall void having a rigid outer void wall and a recessable inner void wall, an elastomeric shear spring received within the housing including a fluid containing chamber adjacent the side wall void and having a restricted fluid flow path; and a rigid inner support member whereby small movement of the mount is allowed by deflection of the elastomeric inner void wall without incurring damping or high dynamic spring rates for improved high frequency performance.
a rigid housing including a side wall void having a rigid outer void wall and a recessable inner void wall, an elastomeric shear spring received within the housing including a fluid containing chamber adjacent the side wall void and having a restricted fluid flow path; and a rigid inner support member whereby small movement of the mount is allowed by deflection of the elastomeric inner void wall without incurring damping or high dynamic spring rates for improved high frequency performance.
2. The engine mount as defined in claim 1, wherein said inner void wall comprises an elastomeric diaphragm.
3. The engine mount as defined in claim 1, wherein said inner void wall comprises an elastomeric sleeve.
4. The engine mount as defined in claim 1, wherein said void comprises an annular recess.
5. The engine mount as defined in claim 1, wherein said fluid chamber comprises a pair of oppositely spaced fluid chambers in fluid communi-cation by the restricted flow path, each of the pair being associated with one of a pair of contiguous recessable inner void walls.
6. An elastomeric damping device for load carrying and dampening of structural agitation comprising:
a rigid outer housing and a rigid inner member;
an elastomeric shear spring spacing the housing from the inner member and having a fluid chamber, containing a fluid, said chamber further having a restricted flow path;
said outer housing having an inner wall coating of an elastomeric material and a rigid outer sleeve providing for a first recessed air chamber;
pressure relief means having a recessable wall portion of the housing for association with the fluid chamber; and a second separate independent air chamber apart from said first air chamber operatively working with said fluid chamber through said restricted flow path and the first air chamber for selective relief of said pressure formed in the chambers by the structural agitation.
a rigid outer housing and a rigid inner member;
an elastomeric shear spring spacing the housing from the inner member and having a fluid chamber, containing a fluid, said chamber further having a restricted flow path;
said outer housing having an inner wall coating of an elastomeric material and a rigid outer sleeve providing for a first recessed air chamber;
pressure relief means having a recessable wall portion of the housing for association with the fluid chamber; and a second separate independent air chamber apart from said first air chamber operatively working with said fluid chamber through said restricted flow path and the first air chamber for selective relief of said pressure formed in the chambers by the structural agitation.
7. An elastomeric damping device for load carrying and damping of structural agitation, said device comprising a rigid outer housing and a rigid inner member supported therein by means of an elastomeric shear spring which spaces the housing from the inner member and defines within the housing a chamber filled with an incompressible fluid which is further provided with a restricted flow path, and wherein pressure relief means is provided in said housing in association with the fluid chamber for selective relief of pressure formed in the chamber by the structural agitation, said pressure relief means comprising a sealed pneumatic chamber isolated from said fluid filled chamber by a deformable diaphragm, the arrangement being such that said fluid filled chamber with its restricted flow path is effective in damping relatively low frequency and high amplitude structural agitations and said pressure relief means accommodates relatively high frequency and low amplitude structural agitations.
8. A damping device according to claim 7, wherein the fluid filled chamber comprises first and second spaced apart chamber portions interconnected by said restricted flow path.
9. A damping device according to claim 8, wherein first and second pressure relief means are provided for respective association with each of said first and second fluid filled chamber portions.
10. A damping device according to claim 8 or 9, wherein the first and second chamber portions are defined at opposed locations of said elastomeric shear spring whereby said device has a preferential damping orientation.
11. A damping device according to claim 7, 8 or 9, wherein said deformable diaphragm comprises an elasto-meric material.
12. A damping device according to claim 7, 8 or 9, wherein said diaphragm comprises a portion of a deformable sleeve sealed to the inner surface of said outer housing and closely spaced therefrom whereby the extent of deformation of the diaphragm is limited by contact with the said inner surface.
13. A device according to claim 7, 8 or 9 , wherein said sealed pneumatic chamber is selectively pressurizable for determining the operational response of the device.
14. A device according to claim 7, 8 or 9, wherein said elastomeric shear spring comprises an elastomer body and a pneumatic chamber provided within said elastomer body.
15. A device according to claim 14, wherein the pneumatic chamber provided in said elastomer body is selectively pressurizable.
16. A fluid filled elastomeric damping device comprising:
a generally cylindrical, rigid outer housing;
a rigid inner member extending within said outer housing generally parallel to the axis thereof; and an elastomeric shear spring supporting said inner member within said outer housing, said elastomeric shear spring comprising an elastomer body secured to both said inner member and said outer housing; and wherein:
said elastomeric shear spring is shaped so as to define within said outer housing first and second chambers spaced apart from each other generally on opposite sides of said rigid inner member and interconnected by a restricted flow path;
an incompressible fluid fills said first and second chambers and said restricted flow path; and an elastomeric sleeve is provided within said rigid outer housing and within locations thereof corresponding to the locations of said first and second chambers is spaced from the inner surface of the outer housing, said elastomeric sleeve defining with the spaced apart surface of the housing first and second sealed pneumatic chambers isolated from respective ones of said first and second fluid filled chambers by the deformable elastomeric material of the sleeve;
the arrangement being such that relatively low frequency and high amplitude vibrations applied between said outer housing and said inner member will be accommodated by flexing of said shear spring and damped by fluid transfer between said first and second fluid filled chambers, whereas relatively high frequency and low amplitude vibrations will be accommodated by said pneumatic chambers.
a generally cylindrical, rigid outer housing;
a rigid inner member extending within said outer housing generally parallel to the axis thereof; and an elastomeric shear spring supporting said inner member within said outer housing, said elastomeric shear spring comprising an elastomer body secured to both said inner member and said outer housing; and wherein:
said elastomeric shear spring is shaped so as to define within said outer housing first and second chambers spaced apart from each other generally on opposite sides of said rigid inner member and interconnected by a restricted flow path;
an incompressible fluid fills said first and second chambers and said restricted flow path; and an elastomeric sleeve is provided within said rigid outer housing and within locations thereof corresponding to the locations of said first and second chambers is spaced from the inner surface of the outer housing, said elastomeric sleeve defining with the spaced apart surface of the housing first and second sealed pneumatic chambers isolated from respective ones of said first and second fluid filled chambers by the deformable elastomeric material of the sleeve;
the arrangement being such that relatively low frequency and high amplitude vibrations applied between said outer housing and said inner member will be accommodated by flexing of said shear spring and damped by fluid transfer between said first and second fluid filled chambers, whereas relatively high frequency and low amplitude vibrations will be accommodated by said pneumatic chambers.
17. A fluid filled elastomer damping device comprising:
a generally cylindrical rigid outer body;
a rigid inner member extending within said outer body an elastomeric shear spring supporting said inner member within said outer body, said elastomeric shear spring comprising an elastomer body secured to both said inner member and said outer body;
and wherein:
said elastomer body is shaped so as to define a plurality of spaced apart chambers within said outer body, said chambers being interconnected by at least one restricted flow path;
an incompressible fluid fills said chambers and said at least one restricted flow path;
a pneumatic chamber is defined within said elastomer body; and at least one of said fluid filled chambers has a wall portion thereof defined by a deformable diaphragm which is sealed to and spaced from the inner surface of said outer body so as to define therewith a sealed pneumatic chamber;
the arrangement being such that relatively low frequency and high amplitude vibrations between said outer body and said inner member are damped by fluid transfer between said fluid filled chambers, whereas relatively high frequency and low amplitude vibrations are accommodated by deformation of said diaphragm.
a generally cylindrical rigid outer body;
a rigid inner member extending within said outer body an elastomeric shear spring supporting said inner member within said outer body, said elastomeric shear spring comprising an elastomer body secured to both said inner member and said outer body;
and wherein:
said elastomer body is shaped so as to define a plurality of spaced apart chambers within said outer body, said chambers being interconnected by at least one restricted flow path;
an incompressible fluid fills said chambers and said at least one restricted flow path;
a pneumatic chamber is defined within said elastomer body; and at least one of said fluid filled chambers has a wall portion thereof defined by a deformable diaphragm which is sealed to and spaced from the inner surface of said outer body so as to define therewith a sealed pneumatic chamber;
the arrangement being such that relatively low frequency and high amplitude vibrations between said outer body and said inner member are damped by fluid transfer between said fluid filled chambers, whereas relatively high frequency and low amplitude vibrations are accommodated by deformation of said diaphragm.
Applications Claiming Priority (2)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| US88859586A | 1986-07-23 | 1986-07-23 | |
| US06/888,595 | 1986-07-23 |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| CA1301787C true CA1301787C (en) | 1992-05-26 |
Family
ID=25393495
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CA000542495A Expired - Lifetime CA1301787C (en) | 1986-07-23 | 1987-07-20 | Fluid filled elastomeric damping device |
Country Status (6)
| Country | Link |
|---|---|
| JP (1) | JPS6334339A (en) |
| KR (1) | KR950004304B1 (en) |
| BR (1) | BR8703833A (en) |
| CA (1) | CA1301787C (en) |
| DE (1) | DE3723986A1 (en) |
| GB (1) | GB2192968B (en) |
Families Citing this family (37)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP3125290B2 (en) * | 1986-12-23 | 2001-01-15 | 日産自動車株式会社 | Inner / outer cylinder type fluid-filled power unit mount |
| DE3724432A1 (en) * | 1987-07-23 | 1989-02-02 | Freudenberg Carl Fa | SLEEVE RUBBER SPRING |
| DE3741260A1 (en) * | 1987-12-05 | 1989-06-15 | Freudenberg Carl Fa | SLEEVE RUBBER SPRING |
| DE3800656A1 (en) * | 1988-01-13 | 1989-08-03 | Freudenberg Carl Fa | HYDRAULICALLY DAMPING SLEEVE RUBBER SPRING |
| DE3804123A1 (en) * | 1988-02-11 | 1989-08-24 | Continental Ag | Hydraulically damped bearing bush |
| FR2628493B1 (en) * | 1988-03-08 | 1990-12-21 | Peugeot | ELASTIC ARTICULATION WITH HYDRAULIC RIGIDIFICATION |
| IT1216017B (en) * | 1988-03-08 | 1990-02-22 | Pirelli Sistemi Antivibranti | ELASTIC BUSH. |
| FR2628496B1 (en) | 1988-03-08 | 1990-12-21 | Peugeot | ELASTIC CONNECTION WITH HYDRAULIC RIGIDIFICATION |
| US5280885A (en) * | 1988-04-07 | 1994-01-25 | Bridgestone Corporation | Vibration isolating apparatus |
| JPH01168036U (en) * | 1988-05-18 | 1989-11-27 | ||
| US4895353A (en) * | 1988-06-28 | 1990-01-23 | The Pullman Company | Fluid filled elastomeric damping device |
| JP2793598B2 (en) * | 1988-08-02 | 1998-09-03 | 株式会社ブリヂストン | Anti-vibration device |
| DE3827905A1 (en) * | 1988-08-17 | 1990-03-08 | Boge Ag | HYDRAULIC DAMPING RUBBER BEARING |
| JPH0244139U (en) * | 1988-09-21 | 1990-03-27 | ||
| US4899997A (en) * | 1988-09-30 | 1990-02-13 | Lord Corporation | Fluid filled resilient bushing |
| JPH0650134B2 (en) * | 1988-11-25 | 1994-06-29 | 鬼怒川ゴム工業株式会社 | Anti-vibration rubber bush |
| DE3839914A1 (en) * | 1988-11-26 | 1990-05-31 | Freudenberg Carl Fa | SLEEVE RUBBER SPRING |
| JPH0277341U (en) * | 1988-12-01 | 1990-06-13 | ||
| DE3841193A1 (en) * | 1988-12-07 | 1990-06-21 | Boge Ag | HYDRAULIC DAMPING RUBBER BEARING |
| EP0389839B1 (en) * | 1989-03-25 | 1994-06-08 | Adam Opel Aktiengesellschaft | Elastic bearing element with hydraulic damping |
| FR2656907B1 (en) * | 1990-01-09 | 1994-07-01 | Hutchinson | IMPROVEMENTS TO HYDRAULIC ANTI-VIBRATION SLEEVES. |
| JP2583145B2 (en) * | 1990-05-22 | 1997-02-19 | 丸五ゴム工業株式会社 | Fluid filled type vibration damping device |
| JPH0442937U (en) * | 1990-08-09 | 1992-04-13 | ||
| DE4140854C2 (en) * | 1990-12-13 | 1995-12-07 | Tokai Rubber Ind Ltd | Cylindrical, elastic bearing with a fluid filling |
| JP2538464B2 (en) * | 1990-12-13 | 1996-09-25 | 東海ゴム工業株式会社 | Fluid filled cylinder mount |
| DE4244914C2 (en) * | 1992-03-17 | 1998-04-09 | Abb Daimler Benz Transp | Storage for the elastic connection of parts of a bogie |
| DE4228842C1 (en) * | 1992-08-29 | 1994-05-05 | Freudenberg Carl Fa | Hydraulically damping rubber bearing |
| DE4305173C2 (en) * | 1993-02-19 | 1998-03-12 | Metzeler Gimetall Ag | Hydraulically damping bearing bush |
| DE4320643C2 (en) * | 1993-06-22 | 1997-02-06 | Hubert Dipl Ing Bruehl | Hydraulically damping bush bearing |
| FR2710957B1 (en) * | 1993-10-05 | 1995-12-08 | Hutchinson | Improvements to hydraulic anti-vibration supports. |
| FR2747166B1 (en) * | 1996-04-04 | 1998-06-12 | Hutchinson | IMPROVEMENTS ON HYDRAULIC ANTI-VIBRATION SUPPORT SLEEVES |
| GB2347191A (en) * | 1999-02-23 | 2000-08-30 | Draftex Ind Ltd | Fluid filled vibration limiter having a different stiffness in two perpendicular directions |
| DE19948307B4 (en) * | 1999-10-06 | 2007-09-06 | ZF Lemförder Metallwaren AG | Hydraulically damping rubber bearing with decoupling element |
| DE10259624B4 (en) * | 2002-12-18 | 2012-04-05 | Contitech Vibration Control Gmbh | Hydraulic radial bearing |
| DE10260520A1 (en) * | 2002-12-21 | 2004-07-01 | Volkswagen Ag | Automobile wheel steering arm with elastomer bearing having stop for limiting relative movement transverse to radial freedom of movement |
| WO2009073701A2 (en) * | 2007-12-03 | 2009-06-11 | Z F Group North American Operations, Inc. | Variable compliance suspension bushing |
| CN113195270A (en) * | 2018-12-20 | 2021-07-30 | 株式会社普利司通 | Toe correction bushing and rear suspension device |
Family Cites Families (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| DE3566023D1 (en) * | 1984-08-07 | 1988-12-08 | Avon Ind Polymers | Hydraulically damped mounting device |
| JPH0536101Y2 (en) * | 1985-04-12 | 1993-09-13 |
-
1987
- 1987-07-03 GB GB8715705A patent/GB2192968B/en not_active Expired - Lifetime
- 1987-07-20 CA CA000542495A patent/CA1301787C/en not_active Expired - Lifetime
- 1987-07-20 DE DE19873723986 patent/DE3723986A1/en not_active Withdrawn
- 1987-07-22 BR BR8703833A patent/BR8703833A/en not_active IP Right Cessation
- 1987-07-23 JP JP62184657A patent/JPS6334339A/en active Pending
- 1987-07-23 KR KR1019870008003A patent/KR950004304B1/en not_active IP Right Cessation
Also Published As
| Publication number | Publication date |
|---|---|
| KR950004304B1 (en) | 1995-04-28 |
| BR8703833A (en) | 1988-03-29 |
| GB2192968A (en) | 1988-01-27 |
| DE3723986A1 (en) | 1988-02-04 |
| JPS6334339A (en) | 1988-02-15 |
| KR880001454A (en) | 1988-04-23 |
| GB8715705D0 (en) | 1987-08-12 |
| GB2192968B (en) | 1990-03-21 |
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Legal Events
| Date | Code | Title | Description |
|---|---|---|---|
| MKLA | Lapsed |