CA2024894C - Hydraulically dampened rubber support - Google Patents
Hydraulically dampened rubber supportInfo
- Publication number
- CA2024894C CA2024894C CA002024894A CA2024894A CA2024894C CA 2024894 C CA2024894 C CA 2024894C CA 002024894 A CA002024894 A CA 002024894A CA 2024894 A CA2024894 A CA 2024894A CA 2024894 C CA2024894 C CA 2024894C
- Authority
- CA
- Canada
- Prior art keywords
- support
- rubber support
- spring
- connecting element
- working chamber
- 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 - Fee Related
Links
- 238000013016 damping Methods 0.000 claims abstract description 35
- 239000007788 liquid Substances 0.000 claims abstract description 10
- 239000000463 material Substances 0.000 claims abstract description 3
- 238000005192 partition Methods 0.000 claims description 11
- 238000007596 consolidation process Methods 0.000 claims description 2
- 239000012530 fluid Substances 0.000 claims description 2
- 238000007493 shaping process Methods 0.000 claims description 2
- 238000009413 insulation Methods 0.000 description 5
- 230000000694 effects Effects 0.000 description 4
- 238000000926 separation method Methods 0.000 description 4
- 230000005540 biological transmission Effects 0.000 description 3
- LYCAIKOWRPUZTN-UHFFFAOYSA-N Ethylene glycol Chemical compound OCCO LYCAIKOWRPUZTN-UHFFFAOYSA-N 0.000 description 2
- 238000004519 manufacturing process Methods 0.000 description 2
- 239000002184 metal Substances 0.000 description 2
- 230000035939 shock Effects 0.000 description 2
- 230000003068 static effect Effects 0.000 description 2
- 239000000725 suspension Substances 0.000 description 2
- 239000006096 absorbing agent Substances 0.000 description 1
- 238000004891 communication Methods 0.000 description 1
- 230000006835 compression Effects 0.000 description 1
- 238000007906 compression Methods 0.000 description 1
- 238000006073 displacement reaction Methods 0.000 description 1
- 230000005489 elastic deformation Effects 0.000 description 1
- 239000006260 foam Substances 0.000 description 1
- WGCNASOHLSPBMP-UHFFFAOYSA-N hydroxyacetaldehyde Natural products OCC=O WGCNASOHLSPBMP-UHFFFAOYSA-N 0.000 description 1
- 239000007769 metal material Substances 0.000 description 1
- 239000000203 mixture Substances 0.000 description 1
- 230000010355 oscillation Effects 0.000 description 1
- 230000001681 protective effect Effects 0.000 description 1
- 230000002787 reinforcement Effects 0.000 description 1
- 238000007789 sealing Methods 0.000 description 1
- XLYOFNOQVPJJNP-UHFFFAOYSA-N water Substances O XLYOFNOQVPJJNP-UHFFFAOYSA-N 0.000 description 1
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
- F16F13/06—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
- F16F13/10—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 the wall being at least in part formed by a flexible membrane or the like
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)
- Springs (AREA)
- Support Of The Bearing (AREA)
Abstract
ABSTRACT
A hydraulically dampened rubber support includes a load bearing support, an annular spring element of elastic rubber material and a support base, which together enclose a working chamber and a compensation chamber.
These chambers are connected through a first damping passage. The working chamber, the compensation chamber and the damping passage are filled with liquid. The spring element has at least two spring sections in the shape of hollow cones arrange symmetrically to a plane which extends transversely to the axis of movement. The spring sections are secured with their adjacent ends to a rigid connecting element which defines a second damping passage.
Such a hydraulically dampened rubber support provides a good damping of vibrations of a supported load over a wider range of frequencies whilst ensuring a long spring travel.
A hydraulically dampened rubber support includes a load bearing support, an annular spring element of elastic rubber material and a support base, which together enclose a working chamber and a compensation chamber.
These chambers are connected through a first damping passage. The working chamber, the compensation chamber and the damping passage are filled with liquid. The spring element has at least two spring sections in the shape of hollow cones arrange symmetrically to a plane which extends transversely to the axis of movement. The spring sections are secured with their adjacent ends to a rigid connecting element which defines a second damping passage.
Such a hydraulically dampened rubber support provides a good damping of vibrations of a supported load over a wider range of frequencies whilst ensuring a long spring travel.
Description
- 202489~
HYDRAULICALLY DAMPENED RUBBER SUPPORT
' The present invention relates to a hydraulically dampened rubber support for supporting static loads and in particular to a hydraulically dampened rubber support for supporting, for example, an engine of a motor vehicle, a vehicle body on a vehicle frame or a chassis on the suspension of a motor vehicle.
` In prior art rubber supports, an annular spring element of elastic rubber ~aterial and a support base define a working chamber which is ~ connected with a compensation chamber through a damping passage. The ; working chamber, the compensation chamber and the damping passage are filled with liquid and the spring element includes at least two spring sections, which enclose the axis of Lovement, essentially have the shape of a hollow cone, are secured with their adjacent ends to a rigid connecting element, and are connected in series in the direction of movement.
Such a support is known from DE-PS 945 899. The spring travel which i~ is achievable with such a support is considerable, but acoustically prominent vibrations of the supported load can only be damped in a narrow frequency range.
It i9 an object of the present invention to further develop such a rubber support so that good damping over a considerably wider range of frequencies is achieved whilst, at the same time, a long spring travel is ensured.
Accordingly the present invention provldeq a hydraulically dampened rubber support comprising a load bearing support, an annular spring element :i 30 of elastic rubber material and a support base, which together define a working chamber, and a compensation chamber. The load bearing support and the support base are connected with each other by the spring element. The compensation chamber is at least partly defined by a flexible wall and a partition wall which separates the working chamber from the compensation chamber. The partition wall includes a first damping passage providing for " , ' ' ?
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a liquid communication between the working chamber and the compensation chamber. The working chamber, the compensation chamber and the first damping passage are filled with a liquid. The spring element includes at least first and second spring sections which surround an axis of movement and have substantially the shape of a hollow cone. The spring sections are secured with their adjacent ends to a rigid connecting element and are arranged in series in the direction of movement. The spring sections are arranged symmetrical to the connecting element and to a plane extending transversely to the axis of movement. A second damping passage pierces the connecting element. The number of spring sections may be selected to permit long spring travel with a comparatively small outside diameter of the support. Between each pair of sequentially arranged spring sections a connecting element with a second damping passage is provided. The resulting damping passages are arranged in series and are not rigidly associated, but may be displaced relative to each other. Because of this arrangement and the possibility to construct the individual passages with different dimensions, it is possible to achieve a good damping effect in a ~, considerably wider range of frequencies than with prior art supports.
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..j ~' 20 In this context, it is extremely important that means which are : 3 commonly employed for insulating acoustically prominent high frequency vibrations and which are readily apparent to a person skilled in the art, , may also be employed in a rubber ~upport in accordance with the present `;; invention. The partition wall may include, for example, a disk which is easily movable between stops and which defines the working chamber at least at one point.
In a preferred embodiment, the spring sections may engage the i connecting element at their outer perimeter for improving the guiding of the `. 30 load bearing support in relation to the support base. Such a configuration has proven to be effective, in particular, in those applications where canting may occur.
According to another preferred embodiment, the spring sections .~ 35 contact the connecting element at their inner perimeter. Such an embodiment .j - 2 -~ PAT 15749-1 :. .
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. .: , , -: . - , has proven advantageous for applications where canting of the load bearing support in relation to the support base may occur.
The connecting element may also function as an inertial mass which is resonantly reciprocatable upon transmission of vibrations of a selected frequency into the rubber support. This improves the vibration technological decoupling of the load bearing support from the support base.
,:, A particularly broad-band damping effect may be achieved by using a restricted second damping passage. In addition, it is also possible to construct the second damping passage as a channel and to dimension it so that the mass of liquid contained therein is induced to move resonantly when vibrations of a selected frequency are transmitted. Vibrations of such a frequency, which may be particularly annoying, may thus be effectively damped.
The connecting element may also include two sub-elements, which are i~ respectively affixed to the first and second spring sections during shaping and consolidation of the spring sectior.s, and may be interconnected independently thereof, for example, by riveting or by bolts. This greatly simplifies the manufacture of a rubber support in accordance with the present invention.
The invention will now be further described by way of example only and with reference to the following drawings, wherein Figure 1 is a cross-section of a hydraulically dampened rubber support in accordance with the invention:
Figure 2 is a cross-section of a preferred embodiment of a hydraulically tampenet rubber support in accortance with the invention:
.
Figure 3 is a cross-section of a preferred embodiment of the rubber support shown in Figure 1:
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Figure 4 is a cross-section of another preferred embodiment of the rubber support shown in Figure l; and Figure 5 is a cross-section of a third preferred embodiment of the rubber S support shown in Figure 1.
~ A rubber support in accordance with the invention as shown in Figures - 1 to 5 serves, for example, to support a motor vehicle body on the wheel suspension of a motor vehicle. The rubber support includes a load bearing support 1, which is, for example, secured to a vehicle body upon which the rubber support is used, and a support base 3 which, for example, rests on springs or shock absorbers of a vehicle wheel control arm. The rubber support may also be used as a connecting element between an engine and a vehicle body or an engine and a chassis. The loaa bearing support 1 and the support base 3 are supported on top of each other by a hollow cone-shaped spring element 2, which comprises first and second spring sections 2.1, ?; 2.2. The rubber support further includes a working chamber 4 and a ~; compensation chamber 6. Working chamber 4 is defined by a separation wall 11 which separates working chamber 4 from compensation chamber 6, support base 3 and spring sections 2.1, 2.2, and compensation chamber 6 is at least partly defined by a flexible wall 14 and separation wall 11. Spring sections 2.1 and 2.2 are arranged symmetrically and are affixed to first and second connecting members 8.1 and 8.2 respectively, which are interlinked in a plane transversely to the axis of movement 7. First sub-chamber 4.1 is defined by first spring section 2.1 and separation wall 11. Second sub-chamber 4.2 is defined by second spring section 2.2 and support base 3.
Separation wall 11 is secured to load bearing support 1 above second sub-chamber 4.1 of the working chamber and separates the second sub-chamber 4.1 from a compensation chamber 6. The partitlon wall 11 consists of an inflexible mesh plate of metal and is pierced, at its outer perimeter, by a ~ helical first damping passage 5. Connecting members ô.l and 8.2 are :~ pierced, parallel to the axis of movement 7, by a second damping passage 9 which connects first and second sub-chambers 4.1, 4.2 of working chamber 4.
The first damping passage 5 is constructed in the form of a channel and is dimensioned so that upon introduction of vibrations of a frequency which is i~
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preferably to be damped, the volume of liquid contained in the first damping - passage 5 i8 induced to move resonantly, which assures a good damping of such vibrations.
,, :, 5 In its central area, the partition wall 11 is formed by a mesh cage 26 which encloses a compensation wall 12. Compensation wall 12 is easily - movable parallel to the axis of movement 7 when pressure differences between - compensation chamber 6 and first sub-chamber 4.1 occur. The available free play of compensation wall 12 is selected so that when acoustically prominent high frequency oscillations of a frequency of at least 30 Hz are transmitted s into the rubber support, a sealing engagement of compensation wall 12 and,; the mesh cage 26 is prevented. This means that absolute pressure increases in first sub-chamber 4.1 and in compensation chamber 6 are prevented when vibrations of such a frequency are introduced, which provides for an effective insulation of such vibrations.
In the embodiment, illustrated in Figure 1, compensation chamber 6 is sealed to tbe outside by a roll bellows 14.1 which incorporates a central reinforcement plate 23 connected to the support base 3 through a rod 13 which passes through partition wall 11. Thus, relative displacements of ~$ support base 3 relative to load bearing support 1 are transferred directly , to compensation chamber 6, which promotes a reciprocation of the volume of - liquid contained in first damping passage 5, upon introduction of low frequency vibrations to be damped. The length of rod 13 and the elastic ; 25 flexibility of the roll bellows 14.1 are dimensioned and matched in such a way that the pressure in the compensation chamber 6 and the additional chambers connected therewith is always above atmospheric pressure. This prevents the occurrence of cavitation phenomena in the rubber bearing. The roll bellows 14.1 i9 arranged within a metal protective cap 16 which has openings 15 and forms part of load bearing support 1 in this embodiment.
$~, The intermediate space 19 between bellows 14.1 and cap 16 is thus connected to the atmosphere. All the other chambers are filled with a hydraulic liquid, preferably with a mixture of glycol and water.
., ~ _ 5 _ -' PAT 15749-1 .,:, .,. ~ . : . .
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Because of the serial arrangement of first and second spring sections 2.1 and 2.2, vibrations of a very large amplitude may be absorbed by a rubber support in accordance with the invention, without excessive deformation of first and second spring sections 2.1 and 2.2. This results in a good durability of the rubber support even under continuous transmission of vibrations of this ~ind. When vibrations of large amplitude are transmitted, an elastic deformation of first and second spring sectiGns 2.1 and 2.2 and of roll bellows 14 occurs. This results in a damping effect in the area of first and second damping passages S and 9. Spring sections 2.1 and 2.2 are constructed as hollow cones and are along their inner :.:
perimeter each connected with a connecting element 8 and, along their outer ; perlmeter, with load bearing support I and support base 3 respectively.
s This provides a good angular mobility whlch, in turn, provides for a good insulation of acoustically prominent vibrations even during tipping or 15 canting movements which may occur during normal operating conditions. First and second connecting elements 8.1 and 8.2 of spring sections 2.1 and 2.2 .~ respectively are rigidly interlinked by a hollow rivet 10 which also defines second damping passage 9. The linked connecting elements 8.1 and 8.2 which ' are of metallic material have a large inertial mass and are arranged between first and second spring sections 2.1 and 2.2 thus preventing the transfer of acoustically prominent vibrations from one spring section to the other.
Therefore, the insulation of such vibrations is correspondingly improved.
The support base 3 includes a collar 18 of substantially s-shaped cross-section which collar is embedded in second spring section 2.2. The outwardly protruding end 24 of collar 18 remote from support base 3 is, in the direction of the axis of movement, positioned opposite an inwardly pro~ecting shoulder 17 of load bearing support 1 which shoulder 17 may be ~, continuous or positioned at intervals around the central axis of the rubber support. End 24 of collar 18 and opposite shoulder or shoulders 17 form .1 movement limiting stops which prevent damage to the rubber support of the invention, and in particular to first and second spring sections 2.1 and ~ 2.2, if overloads are generated during operation. The rubber support is ; generally mounted in a motor vehicle by means of a mounting bracket 25.
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Figure 2 shows a further preferred embodiment of a rubber support in accordance vith the invention which mainly differs from the embodiment described above in that it does not include a connecting rod 13 and in that s first and second æpring sections 2.1 and 2.2 engage connecting element 8, 5 vhlch, in tbis embodiment, includes a disk 8.3, to which the spring sections 2.1 and 2.2 are connected about the outer perimeter of the disk.
Accordingly, spring sections 2.1 and 2.2 are, at their inner perimeter, :~ connected vith load bearing support 1 and support base 3 respectively. This provides for a good guidance of load bearing support 1 by the supporting ,; 10 bearing 3. Furthermore, connecting element 8 is constructed of a first ~;i connecting member 8.1, a second connecting member 8.2 and the intermediate apertured connecting disk 8.3 which includes second damping passage 9.
Second connecting member 8.2 is crimped around first connecting member 8.1 ~, and connecting disk 8.3. Second damping passage 9 is in this embodiment constructed as a restricted opening 9.1, which provides for a broad-band damping effect.
Partition vall 11, which is rigidly secured to support base 3 is constructed as shown in Figure 1. There is also a connecting channel forming a first damping passage 5 which extends between first sub-chamber 4.1 and compensation chamber 6. Compensation chamber 6 is defined at the outside by an elastic wall 14. As a result, after application of the static load vhich is to be supported, the pressure within the fluid-filled inner chambers is increased, which substantially prevents cavitation phenomena in the rubber support during transmission of vibrations.
The embodiment shown in Figure 3 is constructed similarly to the embodiment shown in Figure 1. However, there is no connecting rod 13 and partition wall 11, which separates first sub-chamber 4.1 from compensation chamber 6 is configured differently. Partition wall 11 i8 formed by a valve plate 28 having valves 29 which permit a greater through-put towards compensation chamber 6 than towards first sub-chamber 4.1. Abrupt pressure shocks may thus be gradually and elastically absorbed. Compensation chamber 6 is defined by partition wall 11, rigid cap 16 and a spring bellows 20 which may be compressed upon introduction of an additional volume of liquid ~:: - 7 -, ~ .
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into the compensation chamber, which compression provides for an elastic pretensioning of bellows 20. The intermediate space 19 enclosed by spring bellows 20 is connected to atmosphere through a vent 21. Vent 21 may be selectively closed, in order to reduce the flexibility of the spring bellows 20 and thus increases the load bearing capacity of the rubber support.
.s . The embodiment described in Figure 4 is similar to those described above. However, spring bellows 20, which defines compensation chamber 6 is .~ of a bubble shape and is thus relatively easy to manufacture. In addition, its low inertial mass provides for the achievement of a comparatively better :, insulation of acoustically prominent vibrations. Second sub-chamber 4.2 of ~; working chamber 4 is defined by second spring section 2.2 and a buffer wall ~j~ 22, which engages support base 3 along its outer periphery, is easily deformable and is supported, towards its center, on rubber feet 30. Buffer :i 15 wall 22 and support base 3 together enclose a buffer chamber 21 which is open to ambient through bores 27. This improves the insulation of acoustically prominent vibrations.
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The embodiment shown in Figure 5 substantially corresponds to those shown in Figures 1, 3 and 4. However, buffer wall 22 is made from a block - of closed-cell foam, which results in good damping of acoustically prominent vibrations.
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HYDRAULICALLY DAMPENED RUBBER SUPPORT
' The present invention relates to a hydraulically dampened rubber support for supporting static loads and in particular to a hydraulically dampened rubber support for supporting, for example, an engine of a motor vehicle, a vehicle body on a vehicle frame or a chassis on the suspension of a motor vehicle.
` In prior art rubber supports, an annular spring element of elastic rubber ~aterial and a support base define a working chamber which is ~ connected with a compensation chamber through a damping passage. The ; working chamber, the compensation chamber and the damping passage are filled with liquid and the spring element includes at least two spring sections, which enclose the axis of Lovement, essentially have the shape of a hollow cone, are secured with their adjacent ends to a rigid connecting element, and are connected in series in the direction of movement.
Such a support is known from DE-PS 945 899. The spring travel which i~ is achievable with such a support is considerable, but acoustically prominent vibrations of the supported load can only be damped in a narrow frequency range.
It i9 an object of the present invention to further develop such a rubber support so that good damping over a considerably wider range of frequencies is achieved whilst, at the same time, a long spring travel is ensured.
Accordingly the present invention provldeq a hydraulically dampened rubber support comprising a load bearing support, an annular spring element :i 30 of elastic rubber material and a support base, which together define a working chamber, and a compensation chamber. The load bearing support and the support base are connected with each other by the spring element. The compensation chamber is at least partly defined by a flexible wall and a partition wall which separates the working chamber from the compensation chamber. The partition wall includes a first damping passage providing for " , ' ' ?
:
':
a liquid communication between the working chamber and the compensation chamber. The working chamber, the compensation chamber and the first damping passage are filled with a liquid. The spring element includes at least first and second spring sections which surround an axis of movement and have substantially the shape of a hollow cone. The spring sections are secured with their adjacent ends to a rigid connecting element and are arranged in series in the direction of movement. The spring sections are arranged symmetrical to the connecting element and to a plane extending transversely to the axis of movement. A second damping passage pierces the connecting element. The number of spring sections may be selected to permit long spring travel with a comparatively small outside diameter of the support. Between each pair of sequentially arranged spring sections a connecting element with a second damping passage is provided. The resulting damping passages are arranged in series and are not rigidly associated, but may be displaced relative to each other. Because of this arrangement and the possibility to construct the individual passages with different dimensions, it is possible to achieve a good damping effect in a ~, considerably wider range of frequencies than with prior art supports.
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..j ~' 20 In this context, it is extremely important that means which are : 3 commonly employed for insulating acoustically prominent high frequency vibrations and which are readily apparent to a person skilled in the art, , may also be employed in a rubber ~upport in accordance with the present `;; invention. The partition wall may include, for example, a disk which is easily movable between stops and which defines the working chamber at least at one point.
In a preferred embodiment, the spring sections may engage the i connecting element at their outer perimeter for improving the guiding of the `. 30 load bearing support in relation to the support base. Such a configuration has proven to be effective, in particular, in those applications where canting may occur.
According to another preferred embodiment, the spring sections .~ 35 contact the connecting element at their inner perimeter. Such an embodiment .j - 2 -~ PAT 15749-1 :. .
~"' .,, .: , :
. .: , , -: . - , has proven advantageous for applications where canting of the load bearing support in relation to the support base may occur.
The connecting element may also function as an inertial mass which is resonantly reciprocatable upon transmission of vibrations of a selected frequency into the rubber support. This improves the vibration technological decoupling of the load bearing support from the support base.
,:, A particularly broad-band damping effect may be achieved by using a restricted second damping passage. In addition, it is also possible to construct the second damping passage as a channel and to dimension it so that the mass of liquid contained therein is induced to move resonantly when vibrations of a selected frequency are transmitted. Vibrations of such a frequency, which may be particularly annoying, may thus be effectively damped.
The connecting element may also include two sub-elements, which are i~ respectively affixed to the first and second spring sections during shaping and consolidation of the spring sectior.s, and may be interconnected independently thereof, for example, by riveting or by bolts. This greatly simplifies the manufacture of a rubber support in accordance with the present invention.
The invention will now be further described by way of example only and with reference to the following drawings, wherein Figure 1 is a cross-section of a hydraulically dampened rubber support in accordance with the invention:
Figure 2 is a cross-section of a preferred embodiment of a hydraulically tampenet rubber support in accortance with the invention:
.
Figure 3 is a cross-section of a preferred embodiment of the rubber support shown in Figure 1:
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Figure 4 is a cross-section of another preferred embodiment of the rubber support shown in Figure l; and Figure 5 is a cross-section of a third preferred embodiment of the rubber S support shown in Figure 1.
~ A rubber support in accordance with the invention as shown in Figures - 1 to 5 serves, for example, to support a motor vehicle body on the wheel suspension of a motor vehicle. The rubber support includes a load bearing support 1, which is, for example, secured to a vehicle body upon which the rubber support is used, and a support base 3 which, for example, rests on springs or shock absorbers of a vehicle wheel control arm. The rubber support may also be used as a connecting element between an engine and a vehicle body or an engine and a chassis. The loaa bearing support 1 and the support base 3 are supported on top of each other by a hollow cone-shaped spring element 2, which comprises first and second spring sections 2.1, ?; 2.2. The rubber support further includes a working chamber 4 and a ~; compensation chamber 6. Working chamber 4 is defined by a separation wall 11 which separates working chamber 4 from compensation chamber 6, support base 3 and spring sections 2.1, 2.2, and compensation chamber 6 is at least partly defined by a flexible wall 14 and separation wall 11. Spring sections 2.1 and 2.2 are arranged symmetrically and are affixed to first and second connecting members 8.1 and 8.2 respectively, which are interlinked in a plane transversely to the axis of movement 7. First sub-chamber 4.1 is defined by first spring section 2.1 and separation wall 11. Second sub-chamber 4.2 is defined by second spring section 2.2 and support base 3.
Separation wall 11 is secured to load bearing support 1 above second sub-chamber 4.1 of the working chamber and separates the second sub-chamber 4.1 from a compensation chamber 6. The partitlon wall 11 consists of an inflexible mesh plate of metal and is pierced, at its outer perimeter, by a ~ helical first damping passage 5. Connecting members ô.l and 8.2 are :~ pierced, parallel to the axis of movement 7, by a second damping passage 9 which connects first and second sub-chambers 4.1, 4.2 of working chamber 4.
The first damping passage 5 is constructed in the form of a channel and is dimensioned so that upon introduction of vibrations of a frequency which is i~
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preferably to be damped, the volume of liquid contained in the first damping - passage 5 i8 induced to move resonantly, which assures a good damping of such vibrations.
,, :, 5 In its central area, the partition wall 11 is formed by a mesh cage 26 which encloses a compensation wall 12. Compensation wall 12 is easily - movable parallel to the axis of movement 7 when pressure differences between - compensation chamber 6 and first sub-chamber 4.1 occur. The available free play of compensation wall 12 is selected so that when acoustically prominent high frequency oscillations of a frequency of at least 30 Hz are transmitted s into the rubber support, a sealing engagement of compensation wall 12 and,; the mesh cage 26 is prevented. This means that absolute pressure increases in first sub-chamber 4.1 and in compensation chamber 6 are prevented when vibrations of such a frequency are introduced, which provides for an effective insulation of such vibrations.
In the embodiment, illustrated in Figure 1, compensation chamber 6 is sealed to tbe outside by a roll bellows 14.1 which incorporates a central reinforcement plate 23 connected to the support base 3 through a rod 13 which passes through partition wall 11. Thus, relative displacements of ~$ support base 3 relative to load bearing support 1 are transferred directly , to compensation chamber 6, which promotes a reciprocation of the volume of - liquid contained in first damping passage 5, upon introduction of low frequency vibrations to be damped. The length of rod 13 and the elastic ; 25 flexibility of the roll bellows 14.1 are dimensioned and matched in such a way that the pressure in the compensation chamber 6 and the additional chambers connected therewith is always above atmospheric pressure. This prevents the occurrence of cavitation phenomena in the rubber bearing. The roll bellows 14.1 i9 arranged within a metal protective cap 16 which has openings 15 and forms part of load bearing support 1 in this embodiment.
$~, The intermediate space 19 between bellows 14.1 and cap 16 is thus connected to the atmosphere. All the other chambers are filled with a hydraulic liquid, preferably with a mixture of glycol and water.
., ~ _ 5 _ -' PAT 15749-1 .,:, .,. ~ . : . .
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Because of the serial arrangement of first and second spring sections 2.1 and 2.2, vibrations of a very large amplitude may be absorbed by a rubber support in accordance with the invention, without excessive deformation of first and second spring sections 2.1 and 2.2. This results in a good durability of the rubber support even under continuous transmission of vibrations of this ~ind. When vibrations of large amplitude are transmitted, an elastic deformation of first and second spring sectiGns 2.1 and 2.2 and of roll bellows 14 occurs. This results in a damping effect in the area of first and second damping passages S and 9. Spring sections 2.1 and 2.2 are constructed as hollow cones and are along their inner :.:
perimeter each connected with a connecting element 8 and, along their outer ; perlmeter, with load bearing support I and support base 3 respectively.
s This provides a good angular mobility whlch, in turn, provides for a good insulation of acoustically prominent vibrations even during tipping or 15 canting movements which may occur during normal operating conditions. First and second connecting elements 8.1 and 8.2 of spring sections 2.1 and 2.2 .~ respectively are rigidly interlinked by a hollow rivet 10 which also defines second damping passage 9. The linked connecting elements 8.1 and 8.2 which ' are of metallic material have a large inertial mass and are arranged between first and second spring sections 2.1 and 2.2 thus preventing the transfer of acoustically prominent vibrations from one spring section to the other.
Therefore, the insulation of such vibrations is correspondingly improved.
The support base 3 includes a collar 18 of substantially s-shaped cross-section which collar is embedded in second spring section 2.2. The outwardly protruding end 24 of collar 18 remote from support base 3 is, in the direction of the axis of movement, positioned opposite an inwardly pro~ecting shoulder 17 of load bearing support 1 which shoulder 17 may be ~, continuous or positioned at intervals around the central axis of the rubber support. End 24 of collar 18 and opposite shoulder or shoulders 17 form .1 movement limiting stops which prevent damage to the rubber support of the invention, and in particular to first and second spring sections 2.1 and ~ 2.2, if overloads are generated during operation. The rubber support is ; generally mounted in a motor vehicle by means of a mounting bracket 25.
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-- - 202~894 ,. -.
Figure 2 shows a further preferred embodiment of a rubber support in accordance vith the invention which mainly differs from the embodiment described above in that it does not include a connecting rod 13 and in that s first and second æpring sections 2.1 and 2.2 engage connecting element 8, 5 vhlch, in tbis embodiment, includes a disk 8.3, to which the spring sections 2.1 and 2.2 are connected about the outer perimeter of the disk.
Accordingly, spring sections 2.1 and 2.2 are, at their inner perimeter, :~ connected vith load bearing support 1 and support base 3 respectively. This provides for a good guidance of load bearing support 1 by the supporting ,; 10 bearing 3. Furthermore, connecting element 8 is constructed of a first ~;i connecting member 8.1, a second connecting member 8.2 and the intermediate apertured connecting disk 8.3 which includes second damping passage 9.
Second connecting member 8.2 is crimped around first connecting member 8.1 ~, and connecting disk 8.3. Second damping passage 9 is in this embodiment constructed as a restricted opening 9.1, which provides for a broad-band damping effect.
Partition vall 11, which is rigidly secured to support base 3 is constructed as shown in Figure 1. There is also a connecting channel forming a first damping passage 5 which extends between first sub-chamber 4.1 and compensation chamber 6. Compensation chamber 6 is defined at the outside by an elastic wall 14. As a result, after application of the static load vhich is to be supported, the pressure within the fluid-filled inner chambers is increased, which substantially prevents cavitation phenomena in the rubber support during transmission of vibrations.
The embodiment shown in Figure 3 is constructed similarly to the embodiment shown in Figure 1. However, there is no connecting rod 13 and partition wall 11, which separates first sub-chamber 4.1 from compensation chamber 6 is configured differently. Partition wall 11 i8 formed by a valve plate 28 having valves 29 which permit a greater through-put towards compensation chamber 6 than towards first sub-chamber 4.1. Abrupt pressure shocks may thus be gradually and elastically absorbed. Compensation chamber 6 is defined by partition wall 11, rigid cap 16 and a spring bellows 20 which may be compressed upon introduction of an additional volume of liquid ~:: - 7 -, ~ .
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--- 2n24~9~L
into the compensation chamber, which compression provides for an elastic pretensioning of bellows 20. The intermediate space 19 enclosed by spring bellows 20 is connected to atmosphere through a vent 21. Vent 21 may be selectively closed, in order to reduce the flexibility of the spring bellows 20 and thus increases the load bearing capacity of the rubber support.
.s . The embodiment described in Figure 4 is similar to those described above. However, spring bellows 20, which defines compensation chamber 6 is .~ of a bubble shape and is thus relatively easy to manufacture. In addition, its low inertial mass provides for the achievement of a comparatively better :, insulation of acoustically prominent vibrations. Second sub-chamber 4.2 of ~; working chamber 4 is defined by second spring section 2.2 and a buffer wall ~j~ 22, which engages support base 3 along its outer periphery, is easily deformable and is supported, towards its center, on rubber feet 30. Buffer :i 15 wall 22 and support base 3 together enclose a buffer chamber 21 which is open to ambient through bores 27. This improves the insulation of acoustically prominent vibrations.
:~ .
The embodiment shown in Figure 5 substantially corresponds to those shown in Figures 1, 3 and 4. However, buffer wall 22 is made from a block - of closed-cell foam, which results in good damping of acoustically prominent vibrations.
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Claims (8)
1. A hydraulically dampened rubber support comprising a load bearing support interconnected by an annular spring element made of elastic rubber material with a support base; a working chamber at least partly defined by said load bearing support, said spring element and said support base; and a compensation chamber at least partly defined by a flexible wall and separated from said working chamber by a partition wall; said partition wall having a first damping passage for connecting said working chamber with said compensation chamber, said working chamber, said compensation chamber and said first damping passage being filled with a liquid, said spring element comprising at least first and second spring sections which surround an axis of movement, have substantially the shape of a hollow cone, are secured with their adjacent ends to a rigid connecting element and are arranged in series, said first and second spring sections being symmetrically arranged to said connecting element and to a plane extending transversely to said axis of movement, said connecting element separating said working chamber into first and second sub-chambers and defining a second damping passage connecting said sub-chambers.
2. A rubber support as defined in claim 1, wherein said first and second spring sections engage said connecting element at their outer perimeter.
3. A rubber support as defined in claim 1, wherein said first and second spring sections engage said connecting element at their inner perimeter.
4. A rubber support as defined in claim 1, 2 or 3, wherein said connecting element has an inertial mass and is resonantly reciprocatable upon introduction of vibrations of a selected frequency.
5. A rubber support as defined in claim 4, wherein said second damping passage is a restricted passage.
6. A rubber support as defined in claim 4, wherein said second damping passage is constructed is a channel and is dimensioned so that a mass of fluid contained therein is resonantly reciprocatable upon introduction of vibrations of a selected frequency.
7. A rubber support as defined in claim 6, wherein said connecting element consists of two sub-elements which are connected with said spring sections during shaping and consolidation thereof and are mutually interconnected in a separate step.
8. A rubber support as defined in claim 7, wherein said sub-elements are connected by means of a hollow rivet.
:
:
Applications Claiming Priority (2)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| DE3937332 | 1989-11-09 | ||
| DEP3937332.0 | 1989-11-09 |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CA2024894A1 CA2024894A1 (en) | 1991-05-10 |
| CA2024894C true CA2024894C (en) | 1994-05-24 |
Family
ID=6393205
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CA002024894A Expired - Fee Related CA2024894C (en) | 1989-11-09 | 1990-09-07 | Hydraulically dampened rubber support |
Country Status (7)
| Country | Link |
|---|---|
| EP (1) | EP0426938B1 (en) |
| JP (1) | JPH0743001B2 (en) |
| AT (1) | ATE104029T1 (en) |
| BR (1) | BR9004009A (en) |
| CA (1) | CA2024894C (en) |
| DE (1) | DE59005260D1 (en) |
| ES (1) | ES2050876T3 (en) |
Families Citing this family (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP6761832B2 (en) * | 2017-12-22 | 2020-09-30 | 住友理工株式会社 | Anti-vibration device |
| CN110686037B (en) * | 2019-10-24 | 2024-06-07 | 中国人民解放军陆军工程大学 | High-bearing-capacity cylindrical spring rubber combined shock isolator |
| CN113090698B (en) * | 2021-03-26 | 2022-09-13 | 北京三快在线科技有限公司 | Damper, unmanned aerial vehicle foot rest and unmanned aerial vehicle |
Family Cites Families (7)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| DE2659844C3 (en) * | 1976-05-15 | 1981-04-23 | Audi Nsu Auto Union Ag, 7107 Neckarsulm | Rubber mount with hydraulic damping |
| JPS5636519U (en) * | 1979-08-29 | 1981-04-08 | ||
| US4401298A (en) * | 1980-11-18 | 1983-08-30 | Imperial Clevite Inc. | Flexible column viscous spring damper |
| DE3225700C1 (en) * | 1982-07-09 | 1983-11-17 | Fa. Carl Freudenberg, 6940 Weinheim | Elastic rubber bearing |
| JP2773796B2 (en) * | 1986-03-07 | 1998-07-09 | 本田技研工業株式会社 | Anti-vibration support device |
| FR2602292B1 (en) * | 1986-07-30 | 1990-09-07 | Hutchinson | IMPROVEMENTS ON HYDRAULIC SHOCK ABSORBERS |
| JPS6479442A (en) * | 1987-09-21 | 1989-03-24 | Tokai Rubber Ind Ltd | Fluid-sealed type mounting device |
-
1990
- 1990-05-25 DE DE90109972T patent/DE59005260D1/en not_active Expired - Fee Related
- 1990-05-25 ES ES90109972T patent/ES2050876T3/en not_active Expired - Lifetime
- 1990-05-25 EP EP90109972A patent/EP0426938B1/en not_active Expired - Lifetime
- 1990-05-25 AT AT90109972T patent/ATE104029T1/en not_active IP Right Cessation
- 1990-07-11 JP JP2183849A patent/JPH0743001B2/en not_active Expired - Lifetime
- 1990-08-14 BR BR909004009A patent/BR9004009A/en not_active IP Right Cessation
- 1990-09-07 CA CA002024894A patent/CA2024894C/en not_active Expired - Fee Related
Also Published As
| Publication number | Publication date |
|---|---|
| DE59005260D1 (en) | 1994-05-11 |
| EP0426938B1 (en) | 1994-04-06 |
| JPH03163236A (en) | 1991-07-15 |
| EP0426938A1 (en) | 1991-05-15 |
| BR9004009A (en) | 1991-09-03 |
| JPH0743001B2 (en) | 1995-05-15 |
| ES2050876T3 (en) | 1994-06-01 |
| CA2024894A1 (en) | 1991-05-10 |
| ATE104029T1 (en) | 1994-04-15 |
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Legal Events
| Date | Code | Title | Description |
|---|---|---|---|
| EEER | Examination request | ||
| MKLA | Lapsed |