WO2001063143A1 - Vibration damping arrangements - Google Patents
Vibration damping arrangements Download PDFInfo
- Publication number
- WO2001063143A1 WO2001063143A1 PCT/IB2001/000341 IB0100341W WO0163143A1 WO 2001063143 A1 WO2001063143 A1 WO 2001063143A1 IB 0100341 W IB0100341 W IB 0100341W WO 0163143 A1 WO0163143 A1 WO 0163143A1
- Authority
- WO
- WIPO (PCT)
- Prior art keywords
- chamber
- valve
- engine
- valve member
- arrangement according
- Prior art date
Links
Classifications
-
- 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
- F16F13/26—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 characterised by adjusting or regulating devices responsive to exterior conditions
- F16F13/264—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 characterised by adjusting or regulating devices responsive to exterior conditions comprising means for acting dynamically on the walls bounding a working chamber
Definitions
- Vibration damping arrangements embodying the invention are n the form of engine mounts for mounting engines in motor vehicles. However, they may be used m other applications.
- a vibration damping arrangement for damping relative vibrations between two rigid members, comprising a first rigid element for connection to one of the rigid members, a second rigid element for connection to the other rigid member, stiff resilient support material interconnecting the two rigid elements for resiliently flexing in response to the relative vibrations of the two rigid members, means defining a hollow chamber containing hydraulic fluid, the hollow chamber having a flexible wall arranged to flex in response to the relative vibrations whereby to cause corresponding pressure variations within the hollow chamber, valve means operable to at least partially release the pressure in the chamber, and electromagnetically operative control means for selectively rendering the valve means operative.
- a hydroelastic engine mount for damping relative vibrations between the engine of a vehicle and the body of the vehicle, comprising a first rigid fixing element for connection to one of the engine and the vehicle body, a second rigid fixing element for attachment to the other of the engine and the body, resilient support material extending between the two rigid fixing elements for resiliently flexing m response to vibrations between the two fixing elements, a first flexible-walled chamber defined in part by the resilient support material, a second flexible-walled chamber, a conduit interconnecting the two chambers whereby hydraulic fluid can be passed through the conduit between the two chambers in response to resilient flexing of the resilient support material such that movement of the fluid through the conduit damps the vibrations, valve means comprising a movable valve member mounted to be subjected on one side to the pressure in the first chamber and to be subjected on the other side to the pressure m the second chamber, and electromagnetic control means acting on the valve member and operative to switch the valve means between a first setting in which the valve member
- Figure 1 is a section through one of the engine mounts
- Figure 2 is an enlarged view of part of Figure 1.
- the engine mount comprises a support 10 made of stiff resilient material such as rubber which is mounted between the engine of the vehicle and the vehicle body or chassis.
- the support 10 is generally frusto-conical in shape. Its upper end is fast with a metal stud 12 by means of which an attachment is made to the engine of the vehicle.
- the base of the rubber support 10 is bonded to a metal armature 14 which in turn is rigid with a metal cover 15 carrying a stud 16 for attachment to the vehicle body.
- the engine of the vehicle is connected to the vehicle body by means of the stiff rubber support 10, which provides a resilient connection and helps to isolate engine vibrations from the vehicle body.
- the support assembly provides hydraulic damping as will now be explained.
- the hollow interior of the support 10 provides a chamber ("working chamber") 22 of flattened conical shape and containing a suitable hydraulic fluid such as water with anti-freeze.
- the base of the working chamber 22 is defined by an upper plate or grill 24 which is supported by a valve body 26 made of stiff material, such as plastics material.
- the valve body 26 is held m position by a flange 28 surrounding an aperture in the lower part of the armature 14.
- the flange 28 supports the rigid metal cover 15 and a flexible membrane 34.
- the metal cover 15 defines a hollow interior 35 which is open to the atmosphere at 36.
- a chamber (“compensation chamber”) 37 is defined between the flexible membrane 34 and the underside of the valve body 26.
- the first of these interconnections is via a helical or part -circular conduit 38 which is connected at one end to the working chamber 22 via a hole (not visible in the Figures) through the plate 24. At its other end, the conduit 38 is connected to the compensation chamber 37; the latter connection is also not shown m the Figures.
- the second interconnection means between the chambers 22 and 37 is provided by a valve assembly 44.
- the valve assembly incorporates a flexible disc valve 46.
- the disc valve 46 may be made of rubber and has a flexible central portion 48 which is integral with a circular more rigid flange portion 50.
- the disc valve 46 is supported m a valve chamber 51 defined between the upper grill 24 and a lower grill 52.
- the upper grill 24 has apertures 58 and the lower grill 52 has apertures 60.
- the disc valve 46 is attached to a flanged pole plate 70 which extends over the end of a core piece 71 carrying an electrically energisable coil 72.
- the core piece is fixedly mounted within the valve chamber 51, in a circular recess 73.
- the core piece 71 and coil 72 are indicated diagrammatically at 74.
- the pole plate 70 becomes magnetically attracted to the core piece 71 and is prevented from moving within the valve chamber 51.
- the central flexible part of the valve 46 will be permitted a limited amount of flexibility.
- the coil 72 is de-energized (as shown m the right hand half of Figure 2) , the pole plate 70 is no longer attracted to the core piece 71. An amount of free play P therefore exists between the pole plate 70 and the core piece 71. A significantly greater corresponding vibratory movement of the disc valve 46 in the chamber 51 is thus possible.
- the support 10 acts as a piston or pump on the fluid within the working chamber 22. If the vibrations are of relatively high amplitude and relatively low frequency, the liquid is pumped to and fro between the working chamber 24 and the compensation chamber 37 through the conduit 38.
- the pressure m the compensation chamber 37 is maintained constant and substantially equal to atmospheric pressure, because of the flexibility of the membrane 34 and the connection to the ambient atmosphere via the aperture 36. Therefore, the compensation chamber 37 produces substantially no resistance to the fluctuating liquid movement. Damping is achieved by oscillation of the liquid mass in the conduit 38 which acts as a dynamic damper. Maximum damping is obtained at the resonant frequency which depends on the characteristics of the conduit.
- the condition will be considered m which the coil 72 is electrically energised, so that the disc valve 46 has substantially limited freedom of movement or play m the valve chamber 51.
- the central part of the disc valve 46 When the engine vibrations have relatively low amplitude, the central part of the disc valve 46 is able to vibrate to a small extent within tne valve chamber 51 and thus provides a pressure interconnection between the chambers 22 and 37, even though substantially no fluid flow is taking place under these conditions through the conduit 38 because the frequency of vibrations is substantially different from the resonant frequency of the conduit. Therefore, the flexibility of the disc valve 46 short-circuits the conduit 38 and reduces the effective stiffness of the engine mount so that transmission of vibrations from the engine to the vehicle body is correspondingly reduced.
- the disc valve 46 is given amount of play P as shown m Figure 2. It is therefore able to vibrate not only in response to low amplitude engine vibrations but also at higher amplitude vibrations. In this way, therefore, it can short-circuit the conduit 38 not only at low amplitude vibrations but also at higher amplitude vibrations.
- the dynamic stiffness of the engine mount can be adjusted to be similar to that of the static stiffness.
- the stiffness of the engine mount can m this way be reduced when the engine is at idling speed, thus reducing the transmission of acoustic vibration to the vehicle body. Since the disc valve 46 is not connected to the body 10, the disc valve 46 has low inertia and is thus very responsive to vibrations.
- Energisation of the coil 72, and thus the stiffness of the engine mount can be automatically controlled, in dependence on engine speed, by means of a suitable device which is responsive to engine speed.
Landscapes
- 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
An engine mount for a vehicle has a first rigid fixture (12) for attachment to the engine and a second rigid fixture (13) for attachment to the chassis or body, an armature (14) attached to the second rigid fixture (16), and a resilient rubber support (10) between the first fixture (12) and the armature (14). The rubber support (10) defines a working chamber (22) containing hydraulic fluid which is in communication with a compensation chamber (37) via a helical conduit (38). Two apertured grills (24, 52) define a valve chamber (51) in which a flexible disc valve (46) is oscillatable. The disc valve (46) is mounted on and within an armature (70) of an electromagnetic arrangement including an electrically energisable coil (72) positioned within and extending around the valve chamber (51). When the coil (72) is energised, it magnetically clamps the disc valve (46) to restrict its oscillation.
Description
VTBRATTON DAMPTNG ARRANGEMENTS
The invention relates to vibration damping arrangements. Vibration damping arrangements embodying the invention, and to be described in more detail below by way of example only, are n the form of engine mounts for mounting engines in motor vehicles. However, they may be used m other applications.
According to the invention, there is provided a vibration damping arrangement for damping relative vibrations between two rigid members, comprising a first rigid element for connection to one of the rigid members, a second rigid element for connection to the other rigid member, stiff resilient support material interconnecting the two rigid elements for resiliently flexing in response to the relative vibrations of the two rigid members, means defining a hollow chamber containing hydraulic fluid, the hollow chamber having a flexible wall arranged to flex in response to the relative vibrations whereby to cause corresponding pressure variations within the hollow chamber, valve means operable to at least partially release the pressure in the chamber, and electromagnetically operative control means for selectively rendering the valve means operative.
According to the invention, there is further provided a
hydroelastic engine mount for damping relative vibrations between the engine of a vehicle and the body of the vehicle, comprising a first rigid fixing element for connection to one of the engine and the vehicle body, a second rigid fixing element for attachment to the other of the engine and the body, resilient support material extending between the two rigid fixing elements for resiliently flexing m response to vibrations between the two fixing elements, a first flexible-walled chamber defined in part by the resilient support material, a second flexible-walled chamber, a conduit interconnecting the two chambers whereby hydraulic fluid can be passed through the conduit between the two chambers in response to resilient flexing of the resilient support material such that movement of the fluid through the conduit damps the vibrations, valve means comprising a movable valve member mounted to be subjected on one side to the pressure in the first chamber and to be subjected on the other side to the pressure m the second chamber, and electromagnetic control means acting on the valve member and operative to switch the valve means between a first setting in which the valve member is substantially limited m movement and a second setting in which the valve member is substantially free to move.
Vibration damping arrangements embodying the invention, and m the form of engine mounts for motor vehicles, will now be described, by way of example only, with reference to the
accompanying diagrammatic drawings m which:
Figure 1 is a section through one of the engine mounts; and
Figure 2 is an enlarged view of part of Figure 1.
As shown m Figure 1, the engine mount comprises a support 10 made of stiff resilient material such as rubber which is mounted between the engine of the vehicle and the vehicle body or chassis. The support 10 is generally frusto-conical in shape. Its upper end is fast with a metal stud 12 by means of which an attachment is made to the engine of the vehicle. The base of the rubber support 10 is bonded to a metal armature 14 which in turn is rigid with a metal cover 15 carrying a stud 16 for attachment to the vehicle body. In this way, therefore, the engine of the vehicle is connected to the vehicle body by means of the stiff rubber support 10, which provides a resilient connection and helps to isolate engine vibrations from the vehicle body. In addition, however, the support assembly provides hydraulic damping as will now be explained.
The hollow interior of the support 10 provides a chamber ("working chamber") 22 of flattened conical shape and containing a suitable hydraulic fluid such as water with anti-freeze. The base of the working chamber 22 is defined by an upper plate or
grill 24 which is supported by a valve body 26 made of stiff material, such as plastics material. The valve body 26 is held m position by a flange 28 surrounding an aperture in the lower part of the armature 14. The flange 28 supports the rigid metal cover 15 and a flexible membrane 34. The metal cover 15 defines a hollow interior 35 which is open to the atmosphere at 36. A chamber ("compensation chamber") 37 is defined between the flexible membrane 34 and the underside of the valve body 26.
Two means of interconnection between the working and compensation chambers 22,37 are provided. The first of these interconnections is via a helical or part -circular conduit 38 which is connected at one end to the working chamber 22 via a hole (not visible in the Figures) through the plate 24. At its other end, the conduit 38 is connected to the compensation chamber 37; the latter connection is also not shown m the Figures.
The second interconnection means between the chambers 22 and 37 is provided by a valve assembly 44. The valve assembly incorporates a flexible disc valve 46. The disc valve 46 may be made of rubber and has a flexible central portion 48 which is integral with a circular more rigid flange portion 50. The disc valve 46 is supported m a valve chamber 51 defined between the upper grill 24 and a lower grill 52. The upper grill 24 has apertures 58 and the lower grill 52 has apertures 60.
As shown in more detail m Figure 2, the disc valve 46 is attached to a flanged pole plate 70 which extends over the end of a core piece 71 carrying an electrically energisable coil 72. The core piece is fixedly mounted within the valve chamber 51, in a circular recess 73. In Figure 1, the core piece 71 and coil 72 are indicated diagrammatically at 74.
When the coil 72 is electrically energised (as shown in the left hand half of Figure 2) , the pole plate 70 becomes magnetically attracted to the core piece 71 and is prevented from moving within the valve chamber 51. The central flexible part of the valve 46 will be permitted a limited amount of flexibility. When the coil 72 is de-energized (as shown m the right hand half of Figure 2) , the pole plate 70 is no longer attracted to the core piece 71. An amount of free play P therefore exists between the pole plate 70 and the core piece 71. A significantly greater corresponding vibratory movement of the disc valve 46 in the chamber 51 is thus possible.
In use, vibrations of the engine relative to the body are partly damped by the resilience and stiffness of the rubber support 10. In addition, however, the support 10 acts as a piston or pump on the fluid within the working chamber 22. If the vibrations are of relatively high amplitude and relatively low frequency, the liquid is pumped to and fro between the working chamber 24 and
the compensation chamber 37 through the conduit 38. The pressure m the compensation chamber 37 is maintained constant and substantially equal to atmospheric pressure, because of the flexibility of the membrane 34 and the connection to the ambient atmosphere via the aperture 36. Therefore, the compensation chamber 37 produces substantially no resistance to the fluctuating liquid movement. Damping is achieved by oscillation of the liquid mass in the conduit 38 which acts as a dynamic damper. Maximum damping is obtained at the resonant frequency which depends on the characteristics of the conduit.
However, the operation of the engine mount is modified by the valve assembly 44.
Initially, the condition will be considered m which the coil 72 is electrically energised, so that the disc valve 46 has substantially limited freedom of movement or play m the valve chamber 51.
In this condition and when the vibrations are of relatively high amplitude, the disc valve 46 is unable to follow the vibrations and is held substantially in a fixed position against the grill 52. There is therefore substantially no transfer of fluid pressure between the working and compensation chambers 22,37 via the valve 44. Pressure transfer therefore can only take place
through the conduit 38.
When the engine vibrations have relatively low amplitude, the central part of the disc valve 46 is able to vibrate to a small extent within tne valve chamber 51 and thus provides a pressure interconnection between the chambers 22 and 37, even though substantially no fluid flow is taking place under these conditions through the conduit 38 because the frequency of vibrations is substantially different from the resonant frequency of the conduit. Therefore, the flexibility of the disc valve 46 short-circuits the conduit 38 and reduces the effective stiffness of the engine mount so that transmission of vibrations from the engine to the vehicle body is correspondingly reduced.
If, now, the coil 72 is de-energised, the disc valve 46 is given amount of play P as shown m Figure 2. It is therefore able to vibrate not only in response to low amplitude engine vibrations but also at higher amplitude vibrations. In this way, therefore, it can short-circuit the conduit 38 not only at low amplitude vibrations but also at higher amplitude vibrations.
Therefore, the dynamic stiffness of the engine mount can be adjusted to be similar to that of the static stiffness. The stiffness of the engine mount can m this way be reduced when the engine is at idling speed, thus reducing the transmission of
acoustic vibration to the vehicle body. Since the disc valve 46 is not connected to the body 10, the disc valve 46 has low inertia and is thus very responsive to vibrations.
Energisation of the coil 72, and thus the stiffness of the engine mount, can be automatically controlled, in dependence on engine speed, by means of a suitable device which is responsive to engine speed.
Claims
1. A vibration damping arrangement for damping relative vibrations between two rigid members, comprising a first rigid element (12) for connection to one of the rigid members, a second rigid element (16) for connection to the other rigid member, stiff resilient support material (10) interconnecting the two rigid elements for resiliently flexing m response to the relative vibrations of the two rigid members, means defining a hollow chamber (22) containing hydraulic fluid, the hollow chamber (22) having a flexible wall (34) arranged to flex in response to the relative vibrations whereby to cause corresponding pressure variations within the hollow chamber (22), valve means (44) operable to at least partially release the pressure m the chamber (22), and electromagnetically operative control means (74) for selectively rendering the valve means (44) operative .
2. An arrangement according to claim 1, m which the control means (74) selectively renders the valve means (44) operative m dependence on the vibrations.
3. An arrangement according to claim 1 or 2 , m which the valve means (44) comprises a valve member (46) subjected on one side to the pressure within the chamber (22) and capable when the valve means (44) is m a first setting of moving substantially freely m response to the pressure variations in the hollow chamber (22) and substantially incapable, when the valve means (44) is in a second setting, of so moving, and m that the control means (74) comprises electromagnetic means (70,71,72) for switching the valve means (44) between the first and second settings .
4. An arrangement according to claim 3, in which the valve member (46) is a flexible member (48) mounted on an armature (70) of an electromagnetic means (72) , and m which the control means
(74) comprises an electrically energisable coil (72) for selectively producing a magnetic field to block movement of the armature (70) and thereby to adjust the degree of permitted flexing of the valve member (46) .
5. An arrangement according to claim 4, in which the valve member (46) has a peripheral portion (50) held by the armature
(70) and integral with and surrounding a more flexible portion (48) .
6. An arrangement according to claim 5, comprising housing means (26) for embracingly receiving the armature (70), and m which the electrically energisable coil (72) is mounted peripherally within the housing (26) .
7. An arrangement according to any one of claims 3 to 6 , m which the valve member (44) is mounted between two apertured members (24,52), through one of which the pressure within the hollow chamber (22) is applied to one side of the valve member
(44) and through the other of which an external pressure is applied to the other side of the valve member (44) .
8. An arrangement according to claims 7, m which the external pressure is atmospheric pressure.
9. An arrangement according to any preceding claim, including a second hollow chamber (37), and a conduit (38) extending between the two chambers (22,37) whereby the pressure variations in the first-mentioned chamber (22) tend to cause transfer of the fluid between the two chambers (22,37) through the conduit (38) such that resistance to fluid flow through the conduit (38) tends to damp the vibrations.
10. An arrangement according to claim 9, m which the valve means (44) comprises movable means (46) forming part of a wall between the two hollow chambers (22,37).
11. An arrangement according to claim 9 or 10, in which the pressure m the second hollow chamber (37) is substantially atmospheric pressure.
12. An arrangement according to any preceding claim, m which the means defining the flexible wall (34) of the first-mentioned hollow chamber (22) comprises the stiff resilient material (10) .
13. An arrangement according to any preceding claim for damping relative vibrations between the engine of a vehicle and the body of the vehicle, in which one said rigid element (12) is adapted for connection to one of the engine and the vehicle body and the other said rigid element (16) is adapted for attachment to the other of the engine and the body.
14. An arrangement according to claim 13, in which the control means includes means (74) responsive to the speed of the engine.
15. A hydroelastic engine mount for damping relative vibrations between the engine of a vehicle and the body of the vehicle, comprising a first rigid fixing element (12) for connection to one of the engine and the vehicle body, a second rigid fixing element (16) for attachment to the other of the engine and the body, resilient support material (10) extending between the two rigid fixing elements (12,16) for resiliently flexing in response to vibrations between the two fixing elements (12,16), a first flexible-walled chamber (22) defined in part by the resilient support material (10), a second flexible-walled chamber (37), a conduit (38) interconnecting the two chambers (22,37) whereby hydraulic fluid can be passed through the conduit (38) between the two chambers (22,37) in response to resilient flexing of the resilient support material (10) such that movement of the fluid through the conduit (38) damps the vibrations, valve means (44) comprising a movable valve member (46) mounted to be subjected on one side to the pressure in the first chamber (22) and to be subjected on the other side to the pressure m the second chamber (37), and electromagnetic control means (74) acting on the valve member (46) and operative to switch the valve means (44) between a first setting in which the valve member (46) is substantially limited in movement and a second setting m which the valve member (44) is substantially free to move.
16. An engine mount according to claim 15, in which the valve member (46) comprises a flexible flap mounted for flexing movement between first and second apertured members (24,52) , the first apertured member (24) being positioned between the flexible flap and the interior of the first chamber (22) and the second apertured member (52) being positioned between the flexible flap and the second chamber (37) .
17. An engine mount according to claim 16, in which the flexible flap of the valve member (44) is mounted on an armature (70) arranged peripherally of the valve member (44) , the control means
(74) including an electrically energisable coil (72) for selectively producing a magnetic field to block movement of the armature (70) and thereby to restrain the flexing movement of the flexible flap.
18. An engine mount according to claim 17, in which the valve member (44) is substantially circular and is mounted m a circular housing (26) , the coil (72) extending around the periphery of and within the housing (26) .
19. An engine mount according to any one of claims 15 to 18, m which the control means (74) includes means responsive to the speed of the engine .
20. A hydroelastic engine mount, substantially as described with reference to the accompanying drawings.
Applications Claiming Priority (2)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| GB0004426A GB2359607B (en) | 2000-02-24 | 2000-02-24 | Vibration damping arrangements |
| GB0004426.3 | 2000-02-24 |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| WO2001063143A1 true WO2001063143A1 (en) | 2001-08-30 |
Family
ID=9886354
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| PCT/IB2001/000341 WO2001063143A1 (en) | 2000-02-24 | 2001-02-23 | Vibration damping arrangements |
Country Status (2)
| Country | Link |
|---|---|
| GB (1) | GB2359607B (en) |
| WO (1) | WO2001063143A1 (en) |
Cited By (8)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| GB2407359A (en) * | 2003-09-16 | 2005-04-27 | Tokai Rubber Ind Ltd | A vibrations damping device having a rubber support |
| CN100387862C (en) * | 2002-11-07 | 2008-05-14 | 特雷里博格汽车技术中心有限责任公司 | Hydraulic damping mount, particularly for mounting an automotive engine |
| DE102007014708A1 (en) * | 2007-03-23 | 2008-09-25 | Carl Freudenberg Kg | Hydraulic bearing for motor vehicle combustion engine, has membrane positioned to isolate high-frequency, low-amplitude vibrations |
| DE102007014710A1 (en) * | 2007-03-23 | 2008-10-02 | Carl Freudenberg Kg | hydromount |
| CN102588502A (en) * | 2011-12-30 | 2012-07-18 | 宁波泛亚汽车部件有限公司 | Hydraulic suspension of engine |
| CN102829127A (en) * | 2012-09-20 | 2012-12-19 | 重庆大学 | Magneto-rheological damper of automobile engine suspension system |
| KR20210054693A (en) * | 2019-11-06 | 2021-05-14 | 주식회사 대흥알앤티 | Engine mount device |
| CN113494553A (en) * | 2020-04-01 | 2021-10-12 | 现代自动车株式会社 | Engine mount for vehicle |
Families Citing this family (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| KR101462911B1 (en) * | 2013-03-19 | 2014-11-19 | 현대자동차주식회사 | Electro-magnetic active mount controlling two-way |
| US9267567B2 (en) * | 2013-05-16 | 2016-02-23 | Ford Global Technologies, Llc | Switchable engine mount and method for operation thereof |
| DE102020120176A1 (en) | 2020-07-30 | 2022-02-03 | Vibracoustic Se | Reversible hydro bearing |
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| JPS59231233A (en) * | 1983-06-10 | 1984-12-25 | Toyoda Gosei Co Ltd | Vibration isolating device sealed with liquid |
| JPS60231038A (en) * | 1984-04-28 | 1985-11-16 | Toyoda Gosei Co Ltd | Liquid-seal vibro-isolating device |
| US4635910A (en) * | 1984-05-03 | 1987-01-13 | Toyoda Gosei Co., Ltd. | Fluid-filled damper device |
| FR2711408A1 (en) * | 1993-10-19 | 1995-04-28 | Hutchinson | Improvements to hydraulic anti-vibration devices |
| EP0972964A2 (en) * | 1998-07-16 | 2000-01-19 | Draftex Industries Limited | Vibration damping arrangements |
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| JPS62215141A (en) * | 1986-03-14 | 1987-09-21 | Bridgestone Corp | Vibration isolating device |
| US4872652A (en) * | 1986-06-11 | 1989-10-10 | Firma Carl Freudenberg | Two chamber engine mount |
| JPH0756638B2 (en) * | 1993-02-03 | 1995-06-14 | 日本電気株式会社 | Memory address space expansion device |
| JP3016060B2 (en) * | 1993-04-28 | 2000-03-06 | 本田技研工業株式会社 | Anti-vibration mounting device |
| JPH07208537A (en) * | 1994-01-20 | 1995-08-11 | Nippondenso Co Ltd | Liquid seal type mounting device |
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2000
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2001
- 2001-02-23 WO PCT/IB2001/000341 patent/WO2001063143A1/en active Application Filing
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| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPS59231233A (en) * | 1983-06-10 | 1984-12-25 | Toyoda Gosei Co Ltd | Vibration isolating device sealed with liquid |
| JPS60231038A (en) * | 1984-04-28 | 1985-11-16 | Toyoda Gosei Co Ltd | Liquid-seal vibro-isolating device |
| US4635910A (en) * | 1984-05-03 | 1987-01-13 | Toyoda Gosei Co., Ltd. | Fluid-filled damper device |
| FR2711408A1 (en) * | 1993-10-19 | 1995-04-28 | Hutchinson | Improvements to hydraulic anti-vibration devices |
| EP0972964A2 (en) * | 1998-07-16 | 2000-01-19 | Draftex Industries Limited | Vibration damping arrangements |
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| Title |
|---|
| PATENT ABSTRACTS OF JAPAN vol. 009, no. 111 (M - 379) 15 May 1985 (1985-05-15) * |
| PATENT ABSTRACTS OF JAPAN vol. 010, no. 096 (M - 469) 12 April 1986 (1986-04-12) * |
Cited By (11)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN100387862C (en) * | 2002-11-07 | 2008-05-14 | 特雷里博格汽车技术中心有限责任公司 | Hydraulic damping mount, particularly for mounting an automotive engine |
| GB2407359A (en) * | 2003-09-16 | 2005-04-27 | Tokai Rubber Ind Ltd | A vibrations damping device having a rubber support |
| GB2407359B (en) * | 2003-09-16 | 2005-11-16 | Tokai Rubber Ind Ltd | Vibration damping device having rubber support |
| DE102007014708A1 (en) * | 2007-03-23 | 2008-09-25 | Carl Freudenberg Kg | Hydraulic bearing for motor vehicle combustion engine, has membrane positioned to isolate high-frequency, low-amplitude vibrations |
| DE102007014710A1 (en) * | 2007-03-23 | 2008-10-02 | Carl Freudenberg Kg | hydromount |
| DE102007014710B4 (en) * | 2007-03-23 | 2009-02-26 | Carl Freudenberg Kg | hydromount |
| CN102588502A (en) * | 2011-12-30 | 2012-07-18 | 宁波泛亚汽车部件有限公司 | Hydraulic suspension of engine |
| CN102829127A (en) * | 2012-09-20 | 2012-12-19 | 重庆大学 | Magneto-rheological damper of automobile engine suspension system |
| KR20210054693A (en) * | 2019-11-06 | 2021-05-14 | 주식회사 대흥알앤티 | Engine mount device |
| KR102275555B1 (en) * | 2019-11-06 | 2021-07-09 | 주식회사 대흥알앤티 | Engine mount device |
| CN113494553A (en) * | 2020-04-01 | 2021-10-12 | 现代自动车株式会社 | Engine mount for vehicle |
Also Published As
| Publication number | Publication date |
|---|---|
| GB2359607A (en) | 2001-08-29 |
| GB2359607B (en) | 2003-09-17 |
| GB0004426D0 (en) | 2000-04-12 |
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