GB2189751A - Vehicle suspension systems - Google Patents
Vehicle suspension systems Download PDFInfo
- Publication number
- GB2189751A GB2189751A GB08709272A GB8709272A GB2189751A GB 2189751 A GB2189751 A GB 2189751A GB 08709272 A GB08709272 A GB 08709272A GB 8709272 A GB8709272 A GB 8709272A GB 2189751 A GB2189751 A GB 2189751A
- Authority
- GB
- United Kingdom
- Prior art keywords
- vehicle
- resistance
- torsion bar
- chassis
- roll
- 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- Withdrawn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
-
- B—PERFORMING OPERATIONS; TRANSPORTING
- B60—VEHICLES IN GENERAL
- B60G—VEHICLE SUSPENSION ARRANGEMENTS
- B60G17/00—Resilient suspensions having means for adjusting the spring or vibration-damper characteristics, for regulating the distance between a supporting surface and a sprung part of vehicle or for locking suspension during use to meet varying vehicular or surface conditions, e.g. due to speed or load
- B60G17/015—Resilient suspensions having means for adjusting the spring or vibration-damper characteristics, for regulating the distance between a supporting surface and a sprung part of vehicle or for locking suspension during use to meet varying vehicular or surface conditions, e.g. due to speed or load the regulating means comprising electric or electronic elements
- B60G17/0152—Resilient suspensions having means for adjusting the spring or vibration-damper characteristics, for regulating the distance between a supporting surface and a sprung part of vehicle or for locking suspension during use to meet varying vehicular or surface conditions, e.g. due to speed or load the regulating means comprising electric or electronic elements characterised by the action on a particular type of suspension unit
-
- B—PERFORMING OPERATIONS; TRANSPORTING
- B60—VEHICLES IN GENERAL
- B60G—VEHICLE SUSPENSION ARRANGEMENTS
- B60G21/00—Interconnection systems for two or more resiliently-suspended wheels, e.g. for stabilising a vehicle body with respect to acceleration, deceleration or centrifugal forces
- B60G21/02—Interconnection systems for two or more resiliently-suspended wheels, e.g. for stabilising a vehicle body with respect to acceleration, deceleration or centrifugal forces permanently interconnected
- B60G21/04—Interconnection systems for two or more resiliently-suspended wheels, e.g. for stabilising a vehicle body with respect to acceleration, deceleration or centrifugal forces permanently interconnected mechanically
- B60G21/05—Interconnection systems for two or more resiliently-suspended wheels, e.g. for stabilising a vehicle body with respect to acceleration, deceleration or centrifugal forces permanently interconnected mechanically between wheels on the same axle but on different sides of the vehicle, i.e. the left and right wheel suspensions being interconnected
- B60G21/055—Stabiliser bars
Landscapes
- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- Vehicle Body Suspensions (AREA)
Abstract
A vehicle suspension system employs a torsion bar spring 15 which may be considered as a conventional "anti-roll bar". The torsion bar can be adjustably preloaded when the vehicle is in motion in order to limit roll angle during cornering manoeuvres. Pitch resistance may also or alternatively be controlled. Both aspects of the suspension are controlled by a servo arrangement which modifies suspension spring forces according to the demands of an acceleration-sensing control unit 27 (not shown). <IMAGE>
Description
SPECiFICATION
Vehicle suspension systems
This invention relates to vehicle suspension systems and more particularly, but not excl usiveiy, to the active control of vehicle suspension springs.
The prior art includes G.B. 1075481 (Mumford), and amongst other disclosures there have been proposals for the loading of individual suspension springs to be modified by servo-systems controlled buy a unit responsive to horizontal acceleration forces and to suspension feedback signals.
Such systems provide a degree of control overthe roll and pitch attitudes of a vehicle chassis. However, there is a need for improvements in these previous systems, including the need to simplify the task of the servo-system and its control unit, and an aim of the present invention is to provide improvements in one or more of these respects, or generally.
According to the invention there are provided vehicle suspension systems as defined in the accompanying claims.
The invention also provides a vehicle suspension system possessing any advantage ortechnical feature disclosed herein and further comprising any novel feature or novel combination offeatures disclosed herein.
In this specification and the claims thereof, references to changes in the loading ofthetorsion bar produced by loading means orthe like, are intended to refer to such changes in the torsional loading ofthe bar produced by such loading means as distinctfrom any changes arising, for example, from rolling ofthevehicleoritstendencytoroll.
Likewise, references to the provision of meansfor controlling the resilient resistance provided by resilient means of a suspension unit in a vehicle suspension system, are intended to referto changes in such resilient resistance caused by the control system as distinct from any such changes which may be caused, for example, merely by compression of the resilient means.
In an embodiment described below there is provided a vehicle suspension system in which the vehicle suspension springing means is divided into two parts. One part primarily supports the vehicle weight and provides pitch resistance, and the other
part provides only roll resistance. Either one or both ofthese parts of the vehicle suspension system are controlled buy a servo arrangementwhich modifies the suspension spring forces according to the demand of a control unit. in this way, the task of the servo system and its control unit is simplified.
Likewise, in the embodiment described below, a vehicle suspension system includes wheel axles connected to a chassis th rough articu lated links and resilient suspension units which support the weight ofthe vehicle and provide pitch resistance, and may or may not provide some roll resistance. Torsion bar springs are adjustably mounted on the chassis and connect transverse pairs ofwheel axles such that the torsional loading of the bars or bar is changed when the wheels are differentially displaced about their articulating connections with the chassis. The adjustable mounts of the torsion bar springs are controlled by a servo arrangement such that the torsional loading of the bar may be changed according to the demands of a control unit.By means of a furtherservo servo arrangementthe control unit may also change the loading oftransverse pairs of resilient suspension units to modify the pitch attitude of the chassis.
Embodiments ofthe invention will nowbe described by way of example with reference to the accompanying drawings in which:
Figure lisa diagrammatic front elevation of a wishbone suspension system for a transverse pair of wheel axles.
Figure2 is a plan view ofthe arrangement shown in figure 1.
Figure 3 is a schematic diagram ofthemain components of a suitable servo-system forthe control of chassis roll.
Figure 4 is a schematic diagram of the main components of a suitable servo-system forthe control of both roll and pitch attitude.
Figure 5is a diagrammaticfront elevation of a wishbone suspension system for a pair oftransverse wheel axles similarto figure 1 but substituting in place of coil springs coupled hydro-pneumatic springs of adjustable force for the purpose of controiling pitch attitude.
In the first embodiment illustrated in Figures 1,2 and 3 a vehicle comprises a chassis 10 having two pairs of wheel axles 11 each connected to itthrough a form ofwishbone linkage comprising a pair of normally horizontal wishbones 12, 13 one above the other. The upperwishbone 12 supports the chassis 10 through a spring 14. All the wishbones are pivotally connected to both their respective wheel axles and to the chassis.
Atorsion barspring 15, cranked at each endto form levers pivotally connected through rigid links 16 to the upperwishbones 12, is fitted in bearings 17 affording rotational freedom attached to an adjustable mounting plate 18. The adjustable mounting plate is connected at one end to the chassis by means of a pivot 19, and atthe other end a chassis mounted double acting hydraulic ram 20 controlsthe angular position ofthe mounting plate relative to the chassis. Normally the mounting plate is maintained in an horizontal position relative to the chassis such that no torsional load exists in the bar 15.
With referencetofigure 3 an hydraulic pump 23 receives fluid from a reservoir 24 and delivers it at higher pressure into an accumulator 25 which connects with a servo valve 26. Control unit 27 is proportionally sensitive to transverse accelerations of the vehicle and by means of servo valve 26will proportionally control the pressure in hydraulic lines 28 and 29.
By way of example, iffigure 1 is considered to be a rear elevation of a vehicle which is cornering to the right, the vehicle will tend to roll to the left due to centrifugal force acting through it's centre of gravity which is normally above the vehicle's roll axis. The transverse acceleration is sensed by the control unit 27 which in turn operatesthe servo valve 26 changing the pressures existing in the hydraulic lines 28 and 29 so thatthe hydraulic ram 20 is caused to extend altering the angle of the mounting plate 18, together with torsion bar bearings 17, relative to the chassis 10. This establishes a torsional load in the ba r 1 5 which is reacted i nto the chassis th roug h pivots 19 and 30 causing a reduction in the roll angle which would otherwise have been obtained.
Similarly should the vehicle corner in the opposite direction the control unit 27 would cause the hydraulic ram to retract and load the torsion bar in the opposite sense.
In essencethetorsion bar spring 15 maybe considered as a conventional "anti-roll bar" which is capable of being adjustably preloaded when the vehicle is in motion in order to limit roll angle during cornering manoeuvres.
The second embodiment illustrated in figures 4 and Sis similar to thefirstwith two exceptions.
Firstly the chassis is supported by single acting hydraulic rams 21 instead of metal coil springs 14.
Transverse pairs of rams 21 are connected to a common gas charged pressure accumulator 22 or32 which acts as a resilient suspension spring.
Secondly, with reference to figure 4 which represents a schematic layout suitable for a vehicle having two pairs of transverse wheels, an additional servo valve 31, connected to accumulator 25 and proportionally controlled by a longitudinal acceleration sensor in control unit 27, is used to hydraulically modify the pressures in accumulators 22 and 32 in order to alterthe pitch attitude ofthe vehicle under acceleration or braking.
By way of example, and with reference to figure 4, if, with the vehicle at rest, the pressure in accumulator 32 is considered to be sufficientto support the weight of the front of the vehicle by means of the connected pair of rams 21, and similarly the pressure in accumulator 22 is sufficient to supportthe rear of the vehicle, when accelerating or decelerating weight transferred from front to rear or rear to front pairs of wheels respectively, due to the centre of gravity being above the road surface, will induce an angular pitching movement.
Longitudinal acceleration forces sensed bythe control unit 27 proportionally increases the pressure in accumulator 22 by means of the servo valve 31 and similarly decreases that in accumulator 32 to compensate forweighttransfer and thus reduce or eliminate pitch attitude changes.
Similarly deceleration forces are reacted to in the same way but in the opposite sense.
Amongst other advantages and features of the embodiments described above are the following, namely limitation of roll and pitch, and more constant ride height Moreover, the equipment can be designed as a factory fitted option without requiring major structural differences with respect to conventional layouts. Servicing is simple and the apparatus has certain fail safe characteristics.
Operation does not depend on displacement errors of the suspension. Because the car is suspended by "conventional " springs the control circuit responses becomefarsimplerto quantify.
Claims (13)
1. Avehicle suspension system comprising an anti-roll torsion barcharacterised by loading means forthetorsion bar responsiveto vehicle motionto change the loading of the barandtherebyto reduce vehicle roll.
2. Avehiclesuspension system comprising wheel axles connected to a chassis through resilient suspension units to supportthe weight ofthe vehicle and provide pitch resistance, and a torsion bar connecting a transverse pair of wheel axles to provide roll resistance, characterised by means to adjust the torsional loading of the torsion bar in response to sensed aspects of vehicle motion.
3. Avehicle suspension system comprising wheel axles connectedto a chassisthrough articulated links and resilient suspension units which supportthe weight of the vehicle and provide pitch resistance and may or may not provide some roll resistance, and atorsion bar spring adjustably mounted on the chassis and connecting a transverse pair of wheel axles so that the torsional loading of the bar is changed when the wheels are differentially displaced abouttheirarticulating connections with the chassis.
4. A system according to claim 1 or claim 2 wherein said means for adjusting the loading of the torsion bar comprises a torque generating mechanism connected to the torsion bar between the ends of the torsion bar.
5. Asystem according to claim 4wherein said torque generating mechanism acts between the chassis and the torsion bar.
6. A system according to claim 4 or claim 5 wherein said torque generating mechanism comprises a hydraulic or pneumatic ram.
7. A system according to claim 6 wherein said ram actuates a mechanism to convert linear movement into rotary movement.
8. A system according to claim 7 wherein said mechanism comprises lever means.
9. A system according to claim 8 wherein said lever means comprises a pair of spaced bearings for said torsion bar and carried on a common mounting which is pivotally connected to the vehicle chassis and connected also to said ram for pivotal movement aboutthe axis of said pivotal connection to the chassis.
10. Asystem according to claim Swhereinsaid torsion bar extends generally horizontally between opposed wheel axles of said vehicle and said pivot axes of said ram and said common mounting extend generally horizontally in the travel direction of the vehicle.
11. A system according to any one ofthe preceding claims characterised in that said suspension units comprise spring units providing a controllable degree of resilient resistance to vehicle pitching, and means is provided to vary said degree of resilient resistance in accordance with sensed aspects of vehicle motion tending to cause pitching.
12. Avehicle suspension system comprising first resilient means primarily supporting vehicle weight and providing pitch resistance, and second resilient means providing substantially only roll resistance, characterised in that at least one of said resilient means is adapted to provide controlled resistance to its loads, and control means responsive to aspects of vehicle movement is connected to said resilient means to control said pitch and/or roll ofthevehicle.
13. A vehicle suspension system substantially as described herein with reference to Figures 1 to 3, or
Figures 1 to 3 as modified by Figure 4 or by Figure 5, ofthe accompanying drawings.
Applications Claiming Priority (1)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
GB868609198A GB8609198D0 (en) | 1986-04-15 | 1986-04-15 | Vehicle suspension system |
Publications (2)
Publication Number | Publication Date |
---|---|
GB8709272D0 GB8709272D0 (en) | 1987-05-20 |
GB2189751A true GB2189751A (en) | 1987-11-04 |
Family
ID=10596237
Family Applications (2)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
GB868609198A Pending GB8609198D0 (en) | 1986-04-15 | 1986-04-15 | Vehicle suspension system |
GB08709272A Withdrawn GB2189751A (en) | 1986-04-15 | 1987-04-15 | Vehicle suspension systems |
Family Applications Before (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
GB868609198A Pending GB8609198D0 (en) | 1986-04-15 | 1986-04-15 | Vehicle suspension system |
Country Status (1)
Country | Link |
---|---|
GB (2) | GB8609198D0 (en) |
Cited By (8)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
GB2223718A (en) * | 1988-09-22 | 1990-04-18 | Speechbond Limited | Suspension with active roll control |
GB2235168A (en) * | 1989-08-24 | 1991-02-27 | Gkn Technology Ltd | A vehicle suspension system having an adjustable anti-roll bar |
US5076605A (en) * | 1989-04-17 | 1991-12-31 | Trw Steering & Industrial Products (Japan) Co., Ltd. | Stabilizer and method of controlling stabilizer |
US5178406A (en) * | 1989-03-17 | 1993-01-12 | Gkn Technology Limited | Torsion bar suspension |
EP0844935A1 (en) * | 1995-08-21 | 1998-06-03 | Kinetic Limited | Improvements to roll stabilisation mechanisms in vehicular suspension systems |
EP0952929A1 (en) * | 1996-12-24 | 1999-11-03 | Kinetic Limited | Passive vehicular suspension system including a roll control mechanism |
CN101428543B (en) * | 2007-11-06 | 2013-01-09 | 韩新生 | Full-floating automatic balancing suspension fork of automobile |
CN105059083A (en) * | 2015-08-06 | 2015-11-18 | 湖南大学 | Transverse stabilizer bar for adjusting vehicle roll angle with lateral acceleration |
Citations (6)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
GB933581A (en) * | 1959-10-31 | 1963-08-08 | Daimler Benz Ag | Improvements relating to torsion bar stabilizers for motor vehicles |
GB1037312A (en) * | 1962-03-15 | 1966-07-27 | Citroen Sa Andre | Improvements in or relating to anti-roll devices for automobile vehicles |
GB1067711A (en) * | 1964-02-03 | 1967-05-03 | Woodhead Mfg Company Ltd | Vehicle suspension system |
GB1319673A (en) * | 1969-10-24 | 1973-06-06 | Renault | Vehicle trim-correcting devices |
GB1562487A (en) * | 1976-11-19 | 1980-03-12 | Houghton A | Vehicle suspension means |
EP0152914A1 (en) * | 1984-02-14 | 1985-08-28 | Nissan Motor Co., Ltd. | Stabilizer for an automotive vehicle |
-
1986
- 1986-04-15 GB GB868609198A patent/GB8609198D0/en active Pending
-
1987
- 1987-04-15 GB GB08709272A patent/GB2189751A/en not_active Withdrawn
Patent Citations (6)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
GB933581A (en) * | 1959-10-31 | 1963-08-08 | Daimler Benz Ag | Improvements relating to torsion bar stabilizers for motor vehicles |
GB1037312A (en) * | 1962-03-15 | 1966-07-27 | Citroen Sa Andre | Improvements in or relating to anti-roll devices for automobile vehicles |
GB1067711A (en) * | 1964-02-03 | 1967-05-03 | Woodhead Mfg Company Ltd | Vehicle suspension system |
GB1319673A (en) * | 1969-10-24 | 1973-06-06 | Renault | Vehicle trim-correcting devices |
GB1562487A (en) * | 1976-11-19 | 1980-03-12 | Houghton A | Vehicle suspension means |
EP0152914A1 (en) * | 1984-02-14 | 1985-08-28 | Nissan Motor Co., Ltd. | Stabilizer for an automotive vehicle |
Cited By (13)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
GB2223718A (en) * | 1988-09-22 | 1990-04-18 | Speechbond Limited | Suspension with active roll control |
GB2223718B (en) * | 1988-09-22 | 1992-08-26 | Speechbond Limited | Control arrangement |
US5230529A (en) * | 1988-09-22 | 1993-07-27 | Harvey-Bailey Engineering Ltd. | Control arrangement |
US5178406A (en) * | 1989-03-17 | 1993-01-12 | Gkn Technology Limited | Torsion bar suspension |
US5076605A (en) * | 1989-04-17 | 1991-12-31 | Trw Steering & Industrial Products (Japan) Co., Ltd. | Stabilizer and method of controlling stabilizer |
GB2235168A (en) * | 1989-08-24 | 1991-02-27 | Gkn Technology Ltd | A vehicle suspension system having an adjustable anti-roll bar |
EP0844935A1 (en) * | 1995-08-21 | 1998-06-03 | Kinetic Limited | Improvements to roll stabilisation mechanisms in vehicular suspension systems |
US6302417B1 (en) | 1995-08-21 | 2001-10-16 | Kinetic Limited | Roll stabilization mechanisms in vehicular suspension systems |
EP0844935B1 (en) * | 1995-08-21 | 2006-08-23 | Kinetic Limited | Improvements to roll stabilisation mechanisms in vehicular suspension systems |
EP0952929A1 (en) * | 1996-12-24 | 1999-11-03 | Kinetic Limited | Passive vehicular suspension system including a roll control mechanism |
EP0952929A4 (en) * | 1996-12-24 | 2004-07-28 | Kinetic Ltd | Passive vehicular suspension system including a roll control mechanism |
CN101428543B (en) * | 2007-11-06 | 2013-01-09 | 韩新生 | Full-floating automatic balancing suspension fork of automobile |
CN105059083A (en) * | 2015-08-06 | 2015-11-18 | 湖南大学 | Transverse stabilizer bar for adjusting vehicle roll angle with lateral acceleration |
Also Published As
Publication number | Publication date |
---|---|
GB8609198D0 (en) | 1986-05-21 |
GB8709272D0 (en) | 1987-05-20 |
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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) |