GB2172083A - Vibration absorbing mounting - Google Patents
Vibration absorbing mounting Download PDFInfo
- Publication number
- GB2172083A GB2172083A GB08604115A GB8604115A GB2172083A GB 2172083 A GB2172083 A GB 2172083A GB 08604115 A GB08604115 A GB 08604115A GB 8604115 A GB8604115 A GB 8604115A GB 2172083 A GB2172083 A GB 2172083A
- Authority
- GB
- United Kingdom
- Prior art keywords
- diaphragm
- vibration absorbing
- absorbing mounting
- rubber
- end wall
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
- Withdrawn
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
- F16F13/06—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)
Abstract
In a vibration absorbing mounting of the rubber/hydraulic type, particularly for motor vehicle engines, a pair of end members (110, 170) comprises a piston (111) and a casing (133) with an annular inextensibly reinforced rolling lobe first diaphragm (115) secured between the end members. Rubber spring members of substantial thickness in the form of an intermediate diaphragm (141) and a second diaphragm (151) define, with the first diaphragm, two liquid-filled chambers (160, 161) which intercommunicate via a restricted passageway (162). A space on the side of the second diaphragm remote from the liquid-filled chambers is vented to atmosphere at (180). <IMAGE>
Description
SPECIFICATION
Vibration absorbing mountings
This invention relates to vibration absorbing mountings, and particularly, but not exclusively, to engine mountings for motor vehicles.
The engine of a motor car is normally mounted on vehicle chassis members by mounting devices which each incorporate a block or ring of rubber bonded to metal end members which are fastened respectively to the engine and to the chassis member. Such mountings are arranged to provide support against vertical loads and/or against torque reaction loads: in the latter case the mounting may be positioned with its axis horizontal.
Engine mountings of the rubber/hydraulic type are also known, such as that described in our U.K. Patent Application No. 8406639 which has two liquid-filled chambers communicating with one another through a restricted passageway and separated by an intermediate rubber diaphragm. The chambers are bounded at their other sides, respectively, by a rubber spring member which is attached to one end member and a second diaphragm which is attached to another end member.
In a rubber/hydraulic mounting of the kind described in U.K. Application No. 8406639 the rubber spring member is an annular rubber block bonded to part-conical surfaces of the associated end member and a casing member (the casing member forming part of the other end member). Functionally, the rubber spring member provides a major portion of the stiffness of the mounting at both low and high frequencies. It is however desirable for certain applications to reduce the stiffness of the mounting at low frequence is whilst retaining a higher stiffness at high frequencies, greater than 200 Hertz, and one object of the present invention is to provide a mounting having such characteristics.
According to the present invention, a vibration absorbing mounting comprises a pair of end members, an annular reinforced rollinglobe first diaphragm secured at one peripheral edge to a piston member forming part of a first end member and at the other peripheral edge to a casing member forming part of a second end member, a rubber intermediate diaphragm of substantial thickness constituting a rubber spring member secured to the casing member and defining with the first diaphragm a first liquid-filled chamber, and an annular rubber second diaphragm also of substantial thickness constituting a rubber spring member secured in the casing member at its outer periphery and defining a second liquid-filled chamber between one side of the second diaphragm and the intermediate diaphragm, a restricted passageway being provided between the two liquid-filled chambers and a space on the other side of the second diaphragm being vented to atmosphere.
Whilst the first diaphragm is reinforced so as to be substantially inextensible, the intermediate diaphragm may be of unreinforced rubber so as to provide compliance at higher frequencies, when the restricted passageway throttles the flow of fluid between the two chambers and pressure in the first chamber then causes the intermediate diaphragm to bulge towards the second chamber. The second diaphragm is also normally of unreinforced rubber and may be of thinner construction or of thicker construction than the intermediate diaphragm, its function being to bulge under pressure so as to permit the second chamber to be enlarged to accommodate additional liquid forced into the second chamber as the mounting is compressed.Both the intermediate diaphragm and the second diaphragm need to be of substantial thickness to enable them to resist, elastically, the pressures in the first and second chambers and thus impart required stiffness characteristics.
The second diaphragm may be provided with a central support which may co-operate with a central rigid block bonded in the intermediate diaphragm to constitute a bump stop for limiting the axial movement of the end members towards one another, or the central support may be omitted and in accordance with another aspect of the invention the second end member may comprise an end wall suitably positioned to restrain excessive bulging of the second diaphragm. By restraining such excessive bulging a hydraulic lock may be created in the mounting between the reinforced first diaphragm and the restrained second diaphragm to limit movement of the first end member towards the second end member and thus provide a bump stop.
The term "rubber" as used in this Description is intended to embrace any suitable natural or synthetic elastomeric material.
Three embodiments of the invention will now be described, by way of example, with reference to the accompanying drawings in which:
Figure 1 is an axial cross-section through a vibration absorbing engine mounting;
Figure 2 is a similar view to Fig. 1 showing a second embodiment of the invention, and
Figure 3 is a similar view to Fig. 2 showing a further embodiment of the invention.
The mounting shown in Fig. 1 comprises a first end member 10 which comprises a piston 11 and a piston rod 12 having a screw thread 13 for attachment to a suitable bracket on an engine or chassis member. The piston 11 has a suitably curved side profile to engage a rolling-lobe first diaphragm 15 having an impermeable inner lining 16 and inner and outer annular bead wires 17 and 18 respectively around which the edges of a ply of reinforcement fabric (not shown) are secured.
The reinforcement fabric, which is of conventional form for the reinforcement of rubber articles, extends between the bead wires 17 and 18 around the whole diaphragm area to render the rolling lobe 25 substantially inextensible.
The inner bead region 26 of the diaphragm 15 is clamped in fluid-tight engagement with the piston 11 by a flange portion 27 secured to the piston body by a screw 28, and the outer bead region 29 is fluid-tightly clamped between flanges 30 and 31 of a cover member 32 and a casing member 33 respectively by screws 34. The cover member 32 extends inwardly to provide a seating 35 for a rebound stop in the form of a rubber grommet 37 for engagement by the rear face 40 of the piston 11 whenever the mounting is subjected to tension loads which might otherwise overextend it.
The casing member 33, which forms part of a "second end member" is of hollow cylindrical form and incorporates an annular shoulder 45 against which a rigid support ring 46 of an intermediate unreinforced rubber diaphragm 47, which is a sliding fit within the casing bore, is located. The diaphragm 47 is bonded to the ring 46 and a rigid metal block 48 is bonded in the centre of the diaphragm 47 to form part of a bump stop.
A second support ring 50 which is a sliding fit within the casing bore has bonded within it a second unreinforced rubber diaphragm 51 incorporating a bonded-in central support boss 52 formed as a hollow metal pressing coated with the rubber of the diaprahgm 51 which extends over the flat end surface of the boss 52 as a layer 53 and under the skirt of the boss 52 as an annular lip 54.
The second diaphragm also extends to form an annular lip 55 for resilient sealing engagement with an end plate 60 which is held in position against the casing member by a retaining ring 61 secured by screws 62 to a flange 63 of the casing member. A screwthreaded bolt 64 passes through and is welded to the centre of the end plate 60 for attachment to a suitable bracket on the engine or chassis member, the casing member, end plate 60, and bolt 64 constituting parts of the "second end member" 66. A vent 70 connects the annular space 71 under the second diaphragm 51 to atmosphere, and an O-ring seal 72, together with the sealing lip 55, seals the joint areas between the end plate 60, ring 50, and the casing member 33.
A first chamber 80 is formed between the first diaphragm 15 and the intermediate diaphragm 47, and a second chamber 81 is formed between the intermediate diaphragm 47 and the second diaphragm 51.
The chambers 80 and 81 communicate with one another through an annular restricted passageway 82 having a port 83 at one point of its circumference leading into the chamber 81 and a second port (not shown) at an adjacent point of its circumference leading into the chamber 80, the arrangement being such that flow through the passageway 82 between the two chambers has to pass around substantially the entire circumference of the ring 46.
The two chambers 80 and 81 are filled with a suitable liquid through a charging valve (not shown) in the casing member.
The action of the mounting described above is as follows:
Relatively low-frequency vibrations acting axially on the mounting tend to move the end member 10 relative to the end member 66, and a transfer of fluid between the first and second chambers 80 and 81 takes place, the relative movement of the end members being damped by the throttling effect of the restricted passageway 82 and resisted by the (relatively low) stiffness of the second diaphragm 51 which bulges towards the end plate 60. Very little resistance is offered by the rolling-lobe first diaphragm 15 and since sufficient flow of fluid through the passageway 82 can take place to accommodate movement of the piston 11 at low frequencies the intermediate diaphragm 47 does not need to move substantially and its stiffness therefore does not have any marked effect.Thus at low frequencies the mounting has high damping, low stiffness, characteristics which are particularly advantageous.
Excessive movement of the piston towards the end plate 60 is cushioned by engagement of the piston with the metal block 48 and transmission of the resulting shock through the rubber layer 53 to the boss 52, this arrangement constituting a bump stop.
At higher frequencies, greater than 200
Hertz, the rate of flow through the restricted passageway 82 is insufficiently fast to accommodate the piston movement, and the central portion of the intermediate diaphragm 47 is caused to move axially, providing shear and tension stiffness characteristics which increase the effective stiffness of the mounting. The effect of the rolling-lobe first diaphragm on the characteristics of the mounting is very small since it offers little resistance to axial movement of the piston and its reinforcement prevents it from bulging and thereby yielding to increases in fluid pressure in the first chamber.
The reinforced rolling-lobe first diaphragm thus enables the characteristics of the mounting to include a very low stiffness at low frequencies and a readily controllable (by design features of the intermediate and second diaphragms) stiffness at higher frequencies. The use of a reinforced rolling-lobe diaphragm instead of a rubber spring member reduces any tendency of the mounting to 'creep', that is, settle to a more reduced (or extended) axial length under prolonged exposure to axial load.
In the arrangement illustrated in Fig. 1 the bump stop provided by the metal block 48 and boss 52 is effective, but its provision tends to increase the overall axial length of the mounting. In order to provide a mounting suitable for use in applications where the mounting needs to be installed in a confined space the embodiment illustrated in Fig. 2 may be employed.
The mounting shown in Fig. 2 comprises a first end member 110 which comprises a piston 111 and a piston rod 112 having a screw thread 113 for attachment to a suitable bracket on an engine or chassis member. The piston 111 has a suitably curved side profile to engage a rolling-lobe annular first diaphragm 115 having an impermeable inner lining 116 and inner and outer annular bead wires 117 and 118 respectively around which the edges of a ply of reinforcement fabric (not shown) are secured. The reinforcement fabric, which is of conventional form for the reinforcement of rubber articles, extends between the bead wires 117 and 118 around the whole diaphragm area to render the rolling lobe 115 substantially inextensible.
The inner bead region 126 of the diaphragm 115 is secured to the piston 111, an annular shoulder 127 of the diaphragm being pressfitted into an undercut annular recess 128 of the piston. The outer bead region 129 is held in fluid-tight engagement with an annular shoulder 132 of an annular casing 133 by axial pressure transmitted through a cylindrical sleeve 135 which is a close fit within the casing 133 and is held under axial pressure by a turned-over annular flange 136 of the casing
133.
A cylindrical recess 137 within the sleeve
135 houses a rigid support ring 140, bonded to an intermediate unreinforced rubber diaphragm 141, which is a sliding fit within the recess 137.
A second rigid support ring 150, which is also a sliding fit within the recess 136 has bonded within it a second unreinforced diaphragm 151, the ring 150 having an inwardly extending annular flange 152 which assists in stiffening the diaphragm 151. An annular sealing lip 133 is formed as an extension of the rubber of the diaphragm 151 to provide a seal against the casing 133. The arrangement of the diaphragm is such that a first chamber
160 is formed between the first diaphragm
115 and the intermediate diaphragm 141, and a second chamber 161 is formed between the intermediate diaphragm 141 and the second diaphragm 151.
The chambers 160 and 161 are liquid-filled and communicate with one another through an annular restricted passageway 162 having a port 163 at one point of its circumference
leading into the chamber 160 and a second port 164 at a diametrically opposite point leading into the chamber 161, the arrange
ment being such that flow through the passageway 162 between the two chambers has to pass circumferentially around the ring 140.
A suitable fluid charging passage 166 is provided through the sleeve 135 and an aligned hole in the casing 133, to be closed by a welded rivet after charging.
An end wall 170 of shallow dished form is located at its periphery by the flange 136 of the casing and a screw-threaded bolt 171 passes through and is welded to its central region for attachment to a suitable bracket on the engine or chassis member, the casing 133, end wall 170 and bolt 171 constituting parts of a second end member 176. A vent 180 connects the space between the end wall 170 and the second diaphragm 151 to atmosphere, and a location peg 181 is provided to assist in securing the mounting to the associated bracket.
The casing 133, at the end adjacent the piston 111, extends inwardly to provide an annular seating flange 183 for a rebound stop in the form of a rubber grommet 184 for engagement by the rear face 185 of the piston 111 whenever the mounting is subjected to excessive tension loads which might otherwise over-extend it.
The action of the mounting described above is as follows:
Relatively low-frequency vibrations acting axially on the mounting tend to move the first end member 110 relative to the second end member 176, and a transfer of fluid between the first and second chambers 160 and 161 takes place, the relative movement of the end members being damped by the throttling effect of the restricted passageway 162 and resisted by the (relatively low) stiffness of the second diaphragm 151 which bulges towards the end wall 170. Very little resistance is offered by the rolling-lobe first diaphragm 115, and since sufficient flow of fluid through the passageway 162 can take place to accommodate movement of the piston 111 at low frequencies the intermediate diaphragm 141 does not need to move substantially and its stiffness therefore does not have any marked effect.Thus at low frequencies the mounting has high damping, low stiffness, characteristics which are particularly advantageous.
At high frequencies, greater than 200 Hertz, the rate of flow through the restricted passageway 162 is insufficiently fast to accommodate the piston movement, and the central portion of the intermediate diaphragm 141 is caused to move axially, providing shear and tension stiffness characteristics which increase the effective stiffness of the mounting. The effect of the rolling-lobe first diaphragm 115 on the characteristics of the mounting is very small since it offers little resistance to axial movement of the piston and its reinforcement prevents it from bulging and thereby yielding to increases in fluid pressure in the first chamber 160.
The reinforced rolling-lobe first diaphragm thus enables the characteristics of the mounting to include a very low stiffness at low frequencies and a readily controllable (by design features of the intermediate and second diaphragms) stiffness at higher frequencies. The use of a reinforced rolling-lobe diaphragm instead of a rubber spring member reduces any tendency of the mounting to 'creep', that is, settle to a more reduced (or extended) axial length under prolonged exposure to axial load.
Excessive movement of the piston 111 towards the end wall 170 causes the second diaphragm to bulge until it contacts the end wall 170 and is thus prevented from further movement. When no further movement of the second diaphragm is possible the incompressible fluid within the chambers 160 and 161 constitutes a 'hydraulic lock' which acts to resist any substantial further movement of the piston 111 towards the end wall 170, thus providing a 'bump stop'.
The bump stop provided by the system illustrated in Fig. 2 above requires no additional parts, and thus provides effective cushioning at minimum expense. It also enables the overall axial length of the mounting, for a given stroke, to be kept to a minimum.
Fig. 3 shows an alternative form of the mounting shown in Fig. 2, and only the features in which it differs from that shown in
Fig. 2 will be described.
The mounting 200 is provided with a "second diaphragm" 210 which is of greater thickness than the corresponding diaphragm 151 of Fig. 2, thus providing a greater stiffness.
The support ring 211 for the second diaphragm 210 is fitted directly into the casing 213 and a seal is effected by a lip 214 formed as an extension of the rubber of the diaphragm 210.
A sleeve 215, into which a support ring 218 of an intermediate diaphragm 219 is fitted, is fitted directly into the casing, and a metal clamping washer 220 is provided to transmit axial clamping loads to the ring 218 and sleeve 215.
A rivet 225 is shown in a position to be pressed into the casing and welded, after charging with hydraulic fluid.
Fig. 3 also shows in dotted lines the position of the diaphragm 210 in operation when the mounting is under normal load and also subjected to a transient "bump" load which causes the second diaphragm 210 to be deflected into contact with the end wall 230 of the casing. As soon as this occurs, the effect of such contact modifies the stiffness characteristics of the second diaphragm, increasing its effective stiffness.
By suitable design of the profile of the end wall 230, for example by providing a domed head to the fixing bolt 231 in place of the flat head 232 illustrated, the stiffness characteristics of the second diaphragm can be designed to suit particular requirements.
Claims (11)
1. A vibration absorbing mounting comprising a pair of end members, an annular reinforced rolling-lobe first diaphragm secured at one peripheral edge to a piston member forming part of a first end member and at the other peripheral edge to a casing member forming part of a second end member, a rubber intermediate diaphragm of substantial thickness constituting a rubber spring member secured to the casing member and defining with the first diaphragm a first liquid-filled chamber and an annular rubber second diaphragm also of substantial thickness constituting a rubber spring member secured to the casing member at its outer periphery and defining a second liquid-filled chamber between one side of the second diaphragm and the intermediate diaphragm, a restricted passageway being provided between the two liquidfilled chambers and a space on the other side of the second diaphragm being vented to atmosphere.
2. A vibration absorbing mounting according to Claim 1 wherein the annular rubber second diaphragm is secured to a central support.
3. A vibration absorbing mounting according to Claim 2 wherein the intermediate diaphragm comprises a central rigid block to form part of a bump stop constituted by the rigid block, the central support, and an end wall of the casing member.
4. A vibration absorbing mounting according to any of Claims 1-3 wherein the second diaphragm is of thinner construction than the intermediate diaphragm.
5. A vibration absorbing mounting according to any of Claims 1-3 wherein the second diaphragm is of thicker construction than the intermediate diaphragm.
6. A vibration absorbing mounting according to Claim 1 wherein the second end member comprises an end wall located in a position to restrain excessive bulging of the second diaphragm.
7. A vibration absorbing mounting according to Claim 6 wherein the end wall is located in a position such that the second diaphragm contacts the end wall when subjected to normal load and a transient bump load, the stiffness characteristics of the second diaphragm being modified by contact with the end wall.
8. A vibration absorbing mounting according to Claim 6 or Claim 7 wherein contact between the second diaphragm and the end wall may create a hydraulic lock to limit movement of the first end member towards the second end member and thus provide a bump stop.
9. A vibration absorbing mounting substantially as described herein with reference to Fig.
1 of the drawings.
10. A vibration absorbing mounting sub stantially as described herein with reference to
Fig. 2 of the drawings.
11. A vibration absorbing mounting substantially as described herein with reference to
Fig. 3 of the drawings.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| GB08604115A GB2172083A (en) | 1985-03-06 | 1986-02-19 | Vibration absorbing mounting |
Applications Claiming Priority (3)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| GB858505741A GB8505741D0 (en) | 1985-03-06 | 1985-03-06 | Vibration absorbing mountings |
| GB858508394A GB8508394D0 (en) | 1985-03-30 | 1985-03-30 | Vibration absorbing mountings |
| GB08604115A GB2172083A (en) | 1985-03-06 | 1986-02-19 | Vibration absorbing mounting |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| GB8604115D0 GB8604115D0 (en) | 1986-03-26 |
| GB2172083A true GB2172083A (en) | 1986-09-10 |
Family
ID=27262605
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| GB08604115A Withdrawn GB2172083A (en) | 1985-03-06 | 1986-02-19 | Vibration absorbing mounting |
Country Status (1)
| Country | Link |
|---|---|
| GB (1) | GB2172083A (en) |
Cited By (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US5102105A (en) * | 1989-12-02 | 1992-04-07 | Firma Carl Freudenberg | Hydraulically damped engine mount |
| RU2484330C2 (en) * | 2011-08-19 | 2013-06-10 | Олег Савельевич Кочетов | Fluid-operated antivibration mount of power unit |
| RU2503862C2 (en) * | 2011-08-19 | 2014-01-10 | Олег Савельевич Кочетов | Hydraulic vibration support |
| RU2503861C2 (en) * | 2011-08-19 | 2014-01-10 | Олег Савельевич Кочетов | Hydraulic vibration insulating support |
Citations (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| GB2149880A (en) * | 1983-11-12 | 1985-06-19 | Dunlop Ltd | Vibration absorbing mountings |
-
1986
- 1986-02-19 GB GB08604115A patent/GB2172083A/en not_active Withdrawn
Patent Citations (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| GB2149880A (en) * | 1983-11-12 | 1985-06-19 | Dunlop Ltd | Vibration absorbing mountings |
Cited By (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US5102105A (en) * | 1989-12-02 | 1992-04-07 | Firma Carl Freudenberg | Hydraulically damped engine mount |
| RU2484330C2 (en) * | 2011-08-19 | 2013-06-10 | Олег Савельевич Кочетов | Fluid-operated antivibration mount of power unit |
| RU2503862C2 (en) * | 2011-08-19 | 2014-01-10 | Олег Савельевич Кочетов | Hydraulic vibration support |
| RU2503861C2 (en) * | 2011-08-19 | 2014-01-10 | Олег Савельевич Кочетов | Hydraulic vibration insulating support |
Also Published As
| Publication number | Publication date |
|---|---|
| GB8604115D0 (en) | 1986-03-26 |
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Legal Events
| Date | Code | Title | Description |
|---|---|---|---|
| WAP | Application withdrawn, taken to be withdrawn or refused ** after publication under section 16(1) |