WO1985001919A1 - Vehicle suspension arrangements - Google Patents
Vehicle suspension arrangements Download PDFInfo
- Publication number
- WO1985001919A1 WO1985001919A1 PCT/GB1984/000358 GB8400358W WO8501919A1 WO 1985001919 A1 WO1985001919 A1 WO 1985001919A1 GB 8400358 W GB8400358 W GB 8400358W WO 8501919 A1 WO8501919 A1 WO 8501919A1
- Authority
- WO
- WIPO (PCT)
- Prior art keywords
- wheel suspension
- piston
- load
- vehicle wheel
- suspension device
- Prior art date
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
- 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
- B60G17/02—Spring characteristics, e.g. mechanical springs and mechanical adjusting means
- B60G17/04—Spring characteristics, e.g. mechanical springs and mechanical adjusting means fluid spring characteristics
- B60G17/048—Spring characteristics, e.g. mechanical springs and mechanical adjusting means fluid spring characteristics with the regulating means inside the fluid springs
-
- B—PERFORMING OPERATIONS; TRANSPORTING
- B60—VEHICLES IN GENERAL
- B60G—VEHICLE SUSPENSION ARRANGEMENTS
- B60G2202/00—Indexing codes relating to the type of spring, damper or actuator
- B60G2202/10—Type of spring
- B60G2202/15—Fluid spring
-
- B—PERFORMING OPERATIONS; TRANSPORTING
- B60—VEHICLES IN GENERAL
- B60G—VEHICLE SUSPENSION ARRANGEMENTS
- B60G2202/00—Indexing codes relating to the type of spring, damper or actuator
- B60G2202/40—Type of actuator
- B60G2202/41—Fluid actuator
- B60G2202/413—Hydraulic actuator
-
- B—PERFORMING OPERATIONS; TRANSPORTING
- B60—VEHICLES IN GENERAL
- B60G—VEHICLE SUSPENSION ARRANGEMENTS
- B60G2400/00—Indexing codes relating to detected, measured or calculated conditions or factors
- B60G2400/10—Acceleration; Deceleration
- B60G2400/102—Acceleration; Deceleration vertical
-
- B—PERFORMING OPERATIONS; TRANSPORTING
- B60—VEHICLES IN GENERAL
- B60G—VEHICLE SUSPENSION ARRANGEMENTS
- B60G2400/00—Indexing codes relating to detected, measured or calculated conditions or factors
- B60G2400/20—Speed
- B60G2400/202—Piston speed; Relative velocity between vehicle body and wheel
-
- B—PERFORMING OPERATIONS; TRANSPORTING
- B60—VEHICLES IN GENERAL
- B60G—VEHICLE SUSPENSION ARRANGEMENTS
- B60G2400/00—Indexing codes relating to detected, measured or calculated conditions or factors
- B60G2400/25—Stroke; Height; Displacement
- B60G2400/252—Stroke; Height; Displacement vertical
-
- B—PERFORMING OPERATIONS; TRANSPORTING
- B60—VEHICLES IN GENERAL
- B60G—VEHICLE SUSPENSION ARRANGEMENTS
- B60G2400/00—Indexing codes relating to detected, measured or calculated conditions or factors
- B60G2400/50—Pressure
Definitions
- the invention relates to vehicle suspension arrangements.
- European Patent Application 84 300 370.8 and in International Patent Application PCT/GB84/00014, both of which claim priority from UK Patent Application 83 01 741 there is disclosed a vehicle suspension system comprising wheel suspension devices the displacement of which can be varied, and means responsive to the loading of the suspension devices to feed back to the devices electric signals effecting a predetermined displacement.
- Such a vehicle suspension system permits control of the ride of the vehicle and its attitude to be achieved substantially independently.
- the system can be rendered capable of keeping the vehicle substantially stable in all planes of movement, irrespective of external forces.
- the present invention is concerned with the provisions of an improved wheel suspension device for use in such a system or in other systems serving a similar purpose.
- the present invention accordingly provides a wheel suspension device comprising an hydraulic actuator of which the piston position is adjustable in response to forces acting thereon and/or to a selected
- OMPI control input and a load bearing strut responsive to the actuator piston experience to minimise the load carried by the actuator.
- the present invention thus also provides a wheel suspension device comprising a double acting hydraulic actuator and a strut of which the pre-load and load deflection characteristics are adjustable, the actuator " and the strut being arranged to share the suspension load, and means for adjusting the pre-load and load deflection characteristics of the strut in response to the pressure differential experienced by the piston of the hydraulic actuator so as to minimise the share of the suspension load carried by the actuator.
- the present invention also provides a vehicle wheel suspension device comprising an inner end member slidable into and out of an outer end member, the members enclosing between them a fluid body of which the volume is selectively adjustable, the inner end member also having a piston portion slidably engaging the outer member interior, the ends of the piston portion being exposed to respective fluid pressures to effect the relative sliding movement of the end members.
- the fluid body can comprise a body of a suitable hydraulic fluid, but can instead comprise a body of air or other gas of which the volume is adjustable by alteration of the volume of a body of liquid in contact with the body of gas either directly or by way of a free piston, so as to vary the spring rate of the strut.
- the double acting hydraulic actuator is substantially irreversible within a range of load determined by its cross-sectional area and fluid differential supply pressure.
- a demand load will effect a displacement, which can remain unaltered in spite of a change in load.
- the actuator can incorporate sensing means responsive to at least one of piston position, piston velocity and piston acceleration, for supplying signals to electrical control circuitry included in the system in which the suspension device of the invention is incorporated, which circuitry provides outputs controlling the device.
- the pre-load and load deflection characteristics of the load bearing strut are conveniently adjustable by variation of the hydraulic fluid quantity present in the strut by way of a servo-valve.
- the movement of *> the hydraulic fluid can be employed to damp the movement
- the wheel suspension device of the invention in an electric system, when transducers measuring load, pressure, velocity and/or displacement can be included, the device
- the device 15 can be controlled mechanically, as by way of a mechanical linkage between the device and the vehicle. Although primarily applicable to road vehicles, the usefulness of the device of the invention is not so limited.
- the invention which can be embodied in a variety of ways, will be understood to provide a wheel suspension device for an active suspension system in which the load on the hydraulic actuator is substantially reduced, if not eliminated, so that a considerable size
- Figures 1A and 1B together are a sectional front view of a vehicle wheel suspension device embodying the invention, shown in an extended position;
- Figure 2 is a partial side view of the device of Figure 1 ;
- Figure 3 schematically shows the suspension device of Figures 1 and 2 incorporated in a vehicle wheel suspension system
- Figure 4 schematically shows a modified form of suspension device in accordance with the invention, incorporated in a second vehicle wheel suspension system.
- the vehicle wheel suspension device 1 illustrated in Figures 1-3 comprises a lower end fitting 2 formed with a loop 4 for connection of the device to a vehicle axle assembly (not shown) .
- the fitting 2 has a recess accommodating a load cell 6 operative between the fitting and a headmember 8.
- the head member 8 mounts two opposed servo valves 10 and 12 and has a stepped recess formed in its upper side within which are received three spaced concentric tubes, each sealed to the head member by * an external O-ring or like seal.
- the innermost tube 14 communicates through a passage 16 in the had member 8 with the servo-valve 10 for the introduction into the tube interior, and for the withdrawal therefrom, of an oil or other suitable hydraulic fluid from an external source 11.
- the space 20 between the inner tube 14 and the intermediate tube 22 communicates through a passage 24 in the head member 8 with the servo valve 12, and the outer annular space 26 between the intermediate tube 22 and the stainless steel outer tube 28 communicates with the valve 12 through a passage 30.
- the assembly comprising the tubes 14,22,28 is secured to the head member 8 by means of a steel split collar 32.
- the • inner tube 14 is sealingly secured to an extension portion 34 of the tube 28, of which the upper end is sealed by a plug 35, provided with a pinhole 36.
- a ring 38 makes a sliding seal to the exterior of the extension portion 34 by means of sealing rings 39 and is secured to the lower tubular end portion 40 of an upper end fitting 42.
- the fitting 42 is closed by
- OMPI a reduced diameter portion 44 at its upper end, the portion 44 being tapped to receive a threaded end element 45 for connection of the device to a vehicle chassis.
- the end portion 40 surrounds the extension portion ' 34 with sufficient clearance for the spaced reception therebetween of a sleeve 46 having its lower end sealingly clamped between the ring 36 and a downwardly facing internal step in the end portion 40.
- the upper end of the sleeve 46 is closed except for a pinhole 47.
- An outer ring 54 is secured around the lower end of the end portion 40 by means of a screw threaded connection. Secured within the lower end of the ring 54 is a sleeve 56, the upper end of which abuts the end portion 40 and the ring 38.
- the sleeve 56 is thus a downward extension of the end fitting 42 and at its lower end it makes a sliding seal on the exterior of the outer tube 28 by means of sealing elements 58 held by an end ring 60 secured to the sleeve end by an outer ring 62.
- the outer tube 28 has, below the extension tube
- a larger diameter portion 64 which makes a sliding seal, with the sleeve 56 by means of sealing elements 66, and which functions as a piston.
- Ports 68 at the lower end of the portion 64 communicate the space 26, between the tubes 22 and 28, with the space 70 between the tube 28 and the sleeve 56.
- ports 72 at the upper end of the portion 64 communicate the space 20 between the tubes 14 and 22 with the space 74 " between the extension tube 34 and the sleeve 56.
- the device can function as a double acting hydraulic actuator.
- Pressure fluid introduced into the space 70 from the source 11, by way of the servo- valve 12, passage 30, annular space 26 and ports 68, will, act on the end faces of the space 70 to shorten the device.
- Pressure fluid supplied to the space 74 through the servo-valve 12, passage 24, annular space 20 and ports 72 will act within the space 74 to lengthen the device.
- the pressure fluid supply controlled by the servo-valve 12 need not be from the source 11 connected to- the servo-valve 10 but can be from a separate source.
- the device 1 can also function as a gas spring in that a compression load will be accommodated by compression of air or other gas in the chamber 76 between the tube extension portion 34 and the sleeve 46.
- the volume 78 comprising the upper part of the interior of the tube 14 above the meniscus of the hydraulic fluid therein, and the interior of the extension portion 34, closed by the plug 35, constitutes a first gas reservoir for the gas spring chamber, with which it communicates through the pinhole 36.
- the volume 80 between the sleeve 46 and the portion 40 of the upper end fitting 42 constitutes a second gas reservoir for the gas spring chamber, through the pinhole 47, and this second reservoir can be charged with gas through a charging portion 82 in the end fitting 42.
- the condition of the device 1 is sensed not only by the load cell 6 but also by a linear variable displacement transformer 90.
- the transformer stator portion is received in a housing 91 secured to the fitting 2 and to the head member 8 by connectors 92, the movable core or yoke of the transformer being secured to the sleeve 56 by a connector 94.
- the transformer output is thus dependent on the length and length variations of the device as represented by the position and movement of the piston portion 64 in the sleeve 56.
- the transformer 90 thus supplies signals indicative of at least one of the velocity, acceleration and position of the piston portion.
- the outputs of the load cell 6 and of the linear variable displacement transformer 90 are supplied to control circuitry 95 arranged to generate control signals which are supplied in turn to the servo valves 10 and 12.
- the control circuitry 95 can be generally of the kind described in European Patent Application 84 300 370.8 and International Patent Application PCT/GB84/00014, the contents of which are incorporated herein by reference.
- the device 1, in its function as a hydraulic actuator, is arranged to be substantially irreversible and its effective length, as well as its velocity and/or acceleration can be governed by control signals fed to the servo-valve 12.
- the volume of the hydraulic fluid in the tube 14 can be varied so as to alter the spring characteristics of the device 1 in its function as a load bearing strut. .
- the modified vehicle wheel suspension device 101 shown schematically in Figure 4 corresponds to the device 1 of Figures 1 and 2, except for internal modifications appropriate to the replacement of the gas volume in spaces 76,78 and 80 by a body of hydraulic fluid, the volume of which is selectively adjustable to alter the load deflection characteristics of the device.
- Parts in Figure 4 corresponding to parts shown in Figures 1-3 are indicated by the same reference numerals.
- the sleeve 46 is omitted in the suspension device 101 and the plug 35 is either omitted, or replaced by a plug without the pin hole 36, so as to seal off the interior of the tube 14 from the interior of the end fitting 42, which forms a working chamber 102 to which hydraulic fluid is supplied under pressure.
- the servo valve 12 again controls the supply of pressure fluid from a source 104 into and out of the passages 24,30 in the head member 8, but the servo valve ' 10 is omitted. Instead, a servo valve 105 controls a supply of hydraulic fluid into the working chamber 102 through the port 82 from a second pressure source 106 by way of an hydraulic accumulator 107.
- the outputs of the load cell 6 and the linear variable displacement transformer 90 of the suspension device 101 are connected into control circuitry 109, with control outputs supplied to the servo-valves 12 and 105, the function of which generally resembles that of the control circuitry 95.
Abstract
A vehicle wheel suspension system includes a suspension device (1) having a double acting hydraulic actuator, of which the piston (64) position is adjustable in response to forces acting on the piston (64) and/or to a selective control input, and a load bearing strut operable in response to the actuator piston experience to minimize the actuator load. The device comprises an inner member having a portion (64) slidable within an outer member (56), with the piston (64) on the inner member and slidably engaging the outer member (56), and a fluid body operative between the members, the volume of which is selectively adjustable to alter the strut pre-load and load deflection characteristics. The fluid body may be a body of oil or of gas, when the volume adjustment, which alters the spring rate, can be effected by alteration of the volume of a liquid directly in contact with the gas body or separated therefrom by a free piston.
Description
VEHICLE SUSPENSION ARRANGEMENTS DESCRIPTION
The invention relates to vehicle suspension arrangements. In European Patent Application 84 300 370.8 and in International Patent Application PCT/GB84/00014, both of which claim priority from UK Patent Application 83 01 741, there is disclosed a vehicle suspension system comprising wheel suspension devices the displacement of which can be varied, and means responsive to the loading of the suspension devices to feed back to the devices electric signals effecting a predetermined displacement.'
Such a vehicle suspension system permits control of the ride of the vehicle and its attitude to be achieved substantially independently. The system can be rendered capable of keeping the vehicle substantially stable in all planes of movement, irrespective of external forces. The present invention is concerned with the provisions of an improved wheel suspension device for use in such a system or in other systems serving a similar purpose.
The present invention accordingly provides a wheel suspension device comprising an hydraulic actuator of which the piston position is adjustable in response to forces acting thereon and/or to a selected
OMPI
control input, and a load bearing strut responsive to the actuator piston experience to minimise the load carried by the actuator.
The present invention thus also provides a wheel suspension device comprising a double acting hydraulic actuator and a strut of which the pre-load and load deflection characteristics are adjustable, the actuator " and the strut being arranged to share the suspension load, and means for adjusting the pre-load and load deflection characteristics of the strut in response to the pressure differential experienced by the piston of the hydraulic actuator so as to minimise the share of the suspension load carried by the actuator.
The present invention also provides a vehicle wheel suspension device comprising an inner end member slidable into and out of an outer end member, the members enclosing between them a fluid body of which the volume is selectively adjustable, the inner end member also having a piston portion slidably engaging the outer member interior, the ends of the piston portion being exposed to respective fluid pressures to effect the relative sliding movement of the end members. The fluid body can comprise a body of a suitable hydraulic fluid, but can instead comprise a body of air or other gas of which the volume is adjustable by alteration of the volume of a body of liquid in contact with the body of gas either directly or by way of a free piston, so as to vary the spring rate of the strut.
Typically, the double acting hydraulic actuator is substantially irreversible within a range of load determined by its cross-sectional area and fluid differential supply pressure. Thus, a demand load will effect a displacement, which can remain unaltered in spite of a change in load. The actuator can incorporate sensing means responsive to at least one of piston position, piston velocity and piston
acceleration, for supplying signals to electrical control circuitry included in the system in which the suspension device of the invention is incorporated, which circuitry provides outputs controlling the device.
5 The pre-load and load deflection characteristics of the load bearing strut are conveniently adjustable by variation of the hydraulic fluid quantity present in the strut by way of a servo-valve. The movement of *> the hydraulic fluid can be employed to damp the movement
10 of the actuator.
Although it is convenient to incorporate the wheel suspension device of the invention in an electric system, when transducers measuring load, pressure, velocity and/or displacement can be included, the device
15 can be controlled mechanically, as by way of a mechanical linkage between the device and the vehicle. Although primarily applicable to road vehicles, the usefulness of the device of the invention is not so limited.
20 The invention, which can be embodied in a variety of ways, will be understood to provide a wheel suspension device for an active suspension system in which the load on the hydraulic actuator is substantially reduced, if not eliminated, so that a considerable size
25 reduction is possible, together with a reduced power consumption.
The invention will be more readily understood from the following illustrative description and the accompanying drawings, in which:
30 Figures 1A and 1B together are a sectional front view of a vehicle wheel suspension device embodying the invention, shown in an extended position;
Figure 2 is a partial side view of the device of Figure 1 ;
35 Figure 3 schematically shows the suspension device of Figures 1 and 2 incorporated in a vehicle wheel
suspension system; and
Figure 4 schematically shows a modified form of suspension device in accordance with the invention, incorporated in a second vehicle wheel suspension system.
The vehicle wheel suspension device 1 illustrated in Figures 1-3 comprises a lower end fitting 2 formed with a loop 4 for connection of the device to a vehicle axle assembly (not shown) . At its upper side, the fitting 2 has a recess accommodating a load cell 6 operative between the fitting and a headmember 8. The head member 8 mounts two opposed servo valves 10 and 12 and has a stepped recess formed in its upper side within which are received three spaced concentric tubes, each sealed to the head member by* an external O-ring or like seal.
The innermost tube 14 communicates through a passage 16 in the had member 8 with the servo-valve 10 for the introduction into the tube interior, and for the withdrawal therefrom, of an oil or other suitable hydraulic fluid from an external source 11. The space 20 between the inner tube 14 and the intermediate tube 22 communicates through a passage 24 in the head member 8 with the servo valve 12, and the outer annular space 26 between the intermediate tube 22 and the stainless steel outer tube 28 communicates with the valve 12 through a passage 30. The assembly comprising the tubes 14,22,28 is secured to the head member 8 by means of a steel split collar 32. At its upper end, the • inner tube 14 is sealingly secured to an extension portion 34 of the tube 28, of which the upper end is sealed by a plug 35, provided with a pinhole 36.
A ring 38 makes a sliding seal to the exterior of the extension portion 34 by means of sealing rings 39 and is secured to the lower tubular end portion 40 of an upper end fitting 42. The fitting 42 is closed by
OMPI
a reduced diameter portion 44 at its upper end, the portion 44 being tapped to receive a threaded end element 45 for connection of the device to a vehicle chassis.
The end portion 40 surrounds the extension portion ' 34 with sufficient clearance for the spaced reception therebetween of a sleeve 46 having its lower end sealingly clamped between the ring 36 and a downwardly facing internal step in the end portion 40. The upper end of the sleeve 46 is closed except for a pinhole 47. An outer ring 54 is secured around the lower end of the end portion 40 by means of a screw threaded connection. Secured within the lower end of the ring 54 is a sleeve 56, the upper end of which abuts the end portion 40 and the ring 38. The sleeve 56 is thus a downward extension of the end fitting 42 and at its lower end it makes a sliding seal on the exterior of the outer tube 28 by means of sealing elements 58 held by an end ring 60 secured to the sleeve end by an outer ring 62. The outer tube 28 has, below the extension tube
34, a larger diameter portion 64, which makes a sliding seal, with the sleeve 56 by means of sealing elements 66, and which functions as a piston. Ports 68 at the lower end of the portion 64 communicate the space 26, between the tubes 22 and 28, with the space 70 between the tube 28 and the sleeve 56.
Also, ports 72 at the upper end of the portion 64 communicate the space 20 between the tubes 14 and 22 with the space 74 "between the extension tube 34 and the sleeve 56.
It will be evident from the foregoing description that the device can function as a double acting hydraulic actuator. Pressure fluid introduced into the space 70 from the source 11, by way of the servo- valve 12, passage 30, annular space 26 and ports 68, will, act on the end faces of the space 70 to shorten
the device. Pressure fluid supplied to the space 74 through the servo-valve 12, passage 24, annular space 20 and ports 72 will act within the space 74 to lengthen the device. The pressure fluid supply controlled by the servo-valve 12 need not be from the source 11 connected to- the servo-valve 10 but can be from a separate source.
The device 1 can also function as a gas spring in that a compression load will be accommodated by compression of air or other gas in the chamber 76 between the tube extension portion 34 and the sleeve 46. The volume 78, comprising the upper part of the interior of the tube 14 above the meniscus of the hydraulic fluid therein, and the interior of the extension portion 34, closed by the plug 35, constitutes a first gas reservoir for the gas spring chamber, with which it communicates through the pinhole 36. The volume 80, between the sleeve 46 and the portion 40 of the upper end fitting 42 constitutes a second gas reservoir for the gas spring chamber, through the pinhole 47, and this second reservoir can be charged with gas through a charging portion 82 in the end fitting 42.
The condition of the device 1 is sensed not only by the load cell 6 but also by a linear variable displacement transformer 90. The transformer stator portion is received in a housing 91 secured to the fitting 2 and to the head member 8 by connectors 92, the movable core or yoke of the transformer being secured to the sleeve 56 by a connector 94. The transformer output is thus dependent on the length and length variations of the device as represented by the position and movement of the piston portion 64 in the sleeve 56. The transformer 90 thus supplies signals indicative of at least one of the velocity, acceleration and position of the piston portion.
In use of the device 1 , the outputs of the load cell 6 and of the linear variable displacement transformer 90 are supplied to control circuitry 95 arranged to generate control signals which are supplied in turn to the servo valves 10 and 12. The control circuitry 95 can be generally of the kind described in European Patent Application 84 300 370.8 and International Patent Application PCT/GB84/00014, the contents of which are incorporated herein by reference. The device 1, in its function as a hydraulic actuator, is arranged to be substantially irreversible and its effective length, as well as its velocity and/or acceleration can be governed by control signals fed to the servo-valve 12. Moreover, by means of the control signals supplied to the servo-valve 10, the volume of the hydraulic fluid in the tube 14 can be varied so as to alter the spring characteristics of the device 1 in its function as a load bearing strut. .
The modified vehicle wheel suspension device 101 shown schematically in Figure 4, corresponds to the device 1 of Figures 1 and 2, except for internal modifications appropriate to the replacement of the gas volume in spaces 76,78 and 80 by a body of hydraulic fluid, the volume of which is selectively adjustable to alter the load deflection characteristics of the device. Parts in Figure 4 corresponding to parts shown in Figures 1-3 are indicated by the same reference numerals.
The sleeve 46 is omitted in the suspension device 101 and the plug 35 is either omitted, or replaced by a plug without the pin hole 36, so as to seal off the interior of the tube 14 from the interior of the end fitting 42, which forms a working chamber 102 to which hydraulic fluid is supplied under pressure. The servo valve 12 again controls the supply of pressure fluid from a source 104 into and out of the
passages 24,30 in the head member 8, but the servo valve '10 is omitted. Instead, a servo valve 105 controls a supply of hydraulic fluid into the working chamber 102 through the port 82 from a second pressure source 106 by way of an hydraulic accumulator 107. The outputs of the load cell 6 and the linear variable displacement transformer 90 of the suspension device 101 are connected into control circuitry 109, with control outputs supplied to the servo-valves 12 and 105, the function of which generally resembles that of the control circuitry 95.
It will be evident that the invention can be embodied in a variety of ways other than as specifically described.
Claims
1. A method of operating a vehicle wheel suspension device comprising an hydraulic actuator and a load bearing strut, the method having the steps of adjusting the hydraulic actuator piston position in response to forces acting thereon and/or to a control input, and operating the load bearing strut in response to the actuator piston experience so as to minimise the load carried by the actuator.
2. A vehicle wheel suspension system comprising a wheel suspension device, the wheel suspension device having an hydraulic actuator and load bearing strut, means for adjusting the hydraulic actuator piston position in response to forces acting thereon and/or to a control input, and means for operating the load bearing strut in response to the experience of the actuator piston to thereby minimise the actuator load.
3. A vehicle wheel suspension system as claimed in claim 2 wherein the hydraulic actuator is a double acting actuator which shares the suspension load with the strut of which the pre-load and load deflection characteristics are adjustable in response to the pressure differential experienced by the actuator piston.
4. A vehicle wheel suspension system as claimed in claim 3 wherein the strut incorporates a gas spring and the load deflection characteristics are adjustable by adjustment of the spring rate.
5. A vehicle wheel suspension device capable of use in the system of claim 2 or 3, the device comprising an inner member having an end connectable to one of the vehicle axle assembly and the vehicle chassis, an outer member having the inner member slidably received therein and having an end connectable to the other of the vehicle axle assembly and the vehicle chassis, a body of fluid received between the
OMPI inner and outer members, the. volume of which is selectively adjustable, and a piston within a working chamber formed between the inner and outer members, the sides of the piston being exposed to respective fluid pressures to effect the relatively sliding movement of the inner and outer members.
6. A vehicle wheel suspension device as claimed in claim 5 wherein the fluid body comprises a liquid body.
7. A vehicle wheel suspension device as claimed in claim 5 wherein the fluid body comprises a body of gas, the device including a body of liquid of which the volume is selectively adjustable to adjust the volume of the gas body.
8. A vehicle wheel suspension device as claimed in claim 7 wherein the liquid body is received in the interior of the inner member, which interior communicates with the gas body through a restricted orifice at the upper end of the inner member within the outer member.
9. A vehicle wheel suspension device as claimed in claim 8 wherein the bodies of gas and liquid are separated by a free piston in the inner member interior.
10. A vehicle wheel suspension device as claimed in claim 7, 8 or 9 wherein the outer member contains a gas reservoir in communication with the gas body through a restricted orifice, the reservoir being chargeable from outside the device through the outer member wall.
11. A vehicle wheel suspension device as claimed in any one of claims 4 to 10 wherein the inner member comprises an end fitting from which extend three spaced concentric tubes defining passages therebetween for communicating pressure fluid between a servo-valve carried by the end fitting and respective ends of the working chamber.
12. A vehicle wheel suspension device as claimed in any one of claims 4 to 11 having sensing means responsive to at least one of piston position, piston velocity and piston acceleration.
Applications Claiming Priority (2)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
GB8328373 | 1983-10-24 | ||
GB838328373A GB8328373D0 (en) | 1983-10-24 | 1983-10-24 | Vehicle suspension device |
Publications (1)
Publication Number | Publication Date |
---|---|
WO1985001919A1 true WO1985001919A1 (en) | 1985-05-09 |
Family
ID=10550650
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
PCT/GB1984/000358 WO1985001919A1 (en) | 1983-10-24 | 1984-10-23 | Vehicle suspension arrangements |
Country Status (8)
Country | Link |
---|---|
US (1) | US4830398A (en) |
EP (1) | EP0142947B2 (en) |
JP (1) | JPH064370B2 (en) |
AT (1) | ATE33593T1 (en) |
CA (1) | CA1240713A (en) |
DE (2) | DE3470490D1 (en) |
GB (1) | GB8328373D0 (en) |
WO (1) | WO1985001919A1 (en) |
Cited By (2)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
WO1990015726A1 (en) * | 1989-06-15 | 1990-12-27 | Group Lotus Plc | Vehicle suspension device |
WO1994023222A1 (en) * | 1993-03-30 | 1994-10-13 | Meyer, Richard, J. | Liquid spring vehicular suspension system |
Families Citing this family (24)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
CA1256131A (en) * | 1985-02-08 | 1989-06-20 | David A. Williams | Vehicle suspension arrangements |
DE3684801D1 (en) * | 1985-02-25 | 1992-05-21 | Nissan Motor | POSITIVELY REGULATED VEHICLE SUSPENSION SYSTEM. |
GB8526970D0 (en) | 1985-11-01 | 1985-12-04 | Lotus Group Plc | Torque splitting system |
JP2681772B2 (en) * | 1985-11-07 | 1997-11-26 | 株式会社豊田中央研究所 | Vibration control device |
US4890822A (en) * | 1986-02-13 | 1990-01-02 | Nhk Spring Co., Ltd. | Car suspension system |
JPH0696363B2 (en) * | 1986-06-10 | 1994-11-30 | 日産自動車株式会社 | Active suspension |
JPH0780409B2 (en) * | 1986-06-12 | 1995-08-30 | 日産自動車株式会社 | Active suspension |
US5144558A (en) * | 1986-06-13 | 1992-09-01 | Nissan Motor Company, Limited | Actively controlled automotive suspension system with adjustable rolling-stability and/or pitching-stability |
JPH0780411B2 (en) * | 1986-07-31 | 1995-08-30 | トヨタ自動車株式会社 | Active suspension for vehicles |
DE3783557T2 (en) * | 1986-10-24 | 1993-05-13 | Mazda Motor | VEHICLE SUSPENSION SYSTEM WITH VARIABLE SUSPENSION CHARACTERISTICS. |
JPH01103512A (en) * | 1987-10-15 | 1989-04-20 | Mitsubishi Motors Corp | Active suspension controller for vehicle |
JPH069845Y2 (en) * | 1987-11-05 | 1994-03-16 | 三菱自動車工業株式会社 | Active suspension controller |
JPH069846Y2 (en) * | 1987-11-05 | 1994-03-16 | 三菱自動車工業株式会社 | Active suspension controller |
GB2220624B (en) * | 1988-05-31 | 1992-04-08 | Atsugi Motor Parts Co Ltd | Hydraulic shock absorber |
JPH02142942A (en) * | 1988-11-25 | 1990-06-01 | Atsugi Unisia Corp | Hydraulic shock absorber |
DE3931857A1 (en) * | 1989-09-23 | 1991-04-04 | Bosch Gmbh Robert | DAMPING SYSTEM |
FR2653732B1 (en) * | 1989-10-31 | 1994-12-09 | Alsthom Cge Alcatel | INTERVENTION VEHICLE WITH VARIABLE CONFIGURATION FOR DIFFICULT FLOORS. |
FR2654992B1 (en) * | 1989-11-28 | 1992-03-06 | Renault | VEHICLE SUSPENSION. |
US5242190A (en) * | 1990-12-24 | 1993-09-07 | Ford Motor Company | Unitary sensor assembly for automotive vehicles |
US5396973A (en) * | 1991-11-15 | 1995-03-14 | Lord Corporation | Variable shock absorber with integrated controller, actuator and sensors |
US5855363A (en) * | 1996-10-04 | 1999-01-05 | Svendsen; Mark G. | Spring and rebound support for bicycle seat |
DE10030079A1 (en) * | 2000-06-19 | 2002-01-24 | Schenck Ag Carl | Cylinder piston arrangement based on electro- and magneto-rheological liquids, has second volume-changing chamber that produces bias force against admission direction of pressure medium in first working chamber |
US8434771B2 (en) * | 2011-06-14 | 2013-05-07 | Honda Motor Co., Ltd. | Piston-type actuator and static fluid damper and vehicles including same |
JP6345724B2 (en) * | 2016-03-16 | 2018-06-20 | 本田技研工業株式会社 | Vehicle suspension system |
Citations (12)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US3029089A (en) * | 1959-05-07 | 1962-04-10 | Itt | Vehicle suspension and stabilizing system |
US3035853A (en) * | 1958-12-10 | 1962-05-22 | Itt | Vehicle suspension and stabilizing system |
US3502347A (en) * | 1967-11-06 | 1970-03-24 | Itt | Apparatus for vehicle suspension control |
DE2043526A1 (en) * | 1970-09-02 | 1972-03-09 | Daimler-Benz Ag, 7000 Stuttgart | Hydropneumatic suspension |
GB1287140A (en) * | 1968-11-13 | 1972-08-31 | Const Mecaniques Panhard And L | Vehicles having hydropneumatic suspension systems |
FR2386427A1 (en) * | 1977-04-09 | 1978-11-03 | Messerschmitt Boelkow Blohm | ELASTIC LEG, IN PARTICULAR FOR AIRCRAFT LANDING GEAR |
FR2401037A1 (en) * | 1977-08-26 | 1979-03-23 | Daimler Benz Ag | METHOD AND DEVICE FOR ACTIVE DAMPERING OF VEHICLE WHEEL OSCILLATIONS |
EP0027869A2 (en) * | 1979-10-27 | 1981-05-06 | Messerschmitt-Bölkow-Blohm Gesellschaft mit beschränkter Haftung | Shock and vibration damping arrangement for vehicles |
US4273303A (en) * | 1979-03-16 | 1981-06-16 | The Boeing Company | Adaptive airplane landing gear |
FR2489458A1 (en) * | 1980-08-29 | 1982-03-05 | Messier Hispano Sa | Hydraulic shock absorber e.g. for aeroplane - with absorption characteristic adapted in accordance with force to be absorbed |
US4333668A (en) * | 1979-12-17 | 1982-06-08 | The Bendix Corporation | Electronic adaptive ride control system |
EP0114757A1 (en) * | 1983-01-21 | 1984-08-01 | Group Lotus Plc | Vehicle suspension system |
Family Cites Families (10)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
FR429567A (en) * | 1911-05-10 | 1911-09-26 | Octave Fromond | Air suspension for vehicles |
US3011777A (en) * | 1957-11-06 | 1961-12-05 | Bendix Corp | Retractable strut |
US3141659A (en) * | 1959-12-07 | 1964-07-21 | Jr John K Lyon | Adjustable shock absorber system for vehicles |
US3290038A (en) * | 1965-01-14 | 1966-12-06 | Bendix Corp | Extensible shock absorber |
GB1450898A (en) * | 1972-12-02 | 1976-09-29 | Girling Ltd | Suspension means for vehicles |
FR2447820A1 (en) * | 1979-02-02 | 1980-08-29 | Citroen Sa | OLEOPNEUMATIC SUSPENSION WITH TELESCOPIC LEG FOR VEHICLE |
DE3004307C2 (en) * | 1980-02-06 | 1984-06-07 | Boge Gmbh, 5208 Eitorf | Self-pumping hydropneumatic telescopic spring-damper element with internal level control |
FR2497896A1 (en) * | 1980-08-29 | 1982-07-16 | Messier Hispano Sa | DAMPER |
GB2101266B (en) * | 1981-07-09 | 1985-08-21 | Lucas Industries Ltd | Self-pumping struts for vehicle suspension systems |
JPS58112819A (en) * | 1981-12-28 | 1983-07-05 | Nippon Denso Co Ltd | Method of controlling shock absorbers |
-
1983
- 1983-10-24 GB GB838328373A patent/GB8328373D0/en active Pending
-
1984
- 1984-10-23 EP EP84307288A patent/EP0142947B2/en not_active Expired - Lifetime
- 1984-10-23 US US06/747,130 patent/US4830398A/en not_active Expired - Lifetime
- 1984-10-23 DE DE8484307288T patent/DE3470490D1/en not_active Expired
- 1984-10-23 DE DE198484307288T patent/DE142947T1/en active Pending
- 1984-10-23 JP JP59504030A patent/JPH064370B2/en not_active Expired - Lifetime
- 1984-10-23 WO PCT/GB1984/000358 patent/WO1985001919A1/en unknown
- 1984-10-23 AT AT84307288T patent/ATE33593T1/en active
- 1984-10-24 CA CA000466250A patent/CA1240713A/en not_active Expired
Patent Citations (12)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US3035853A (en) * | 1958-12-10 | 1962-05-22 | Itt | Vehicle suspension and stabilizing system |
US3029089A (en) * | 1959-05-07 | 1962-04-10 | Itt | Vehicle suspension and stabilizing system |
US3502347A (en) * | 1967-11-06 | 1970-03-24 | Itt | Apparatus for vehicle suspension control |
GB1287140A (en) * | 1968-11-13 | 1972-08-31 | Const Mecaniques Panhard And L | Vehicles having hydropneumatic suspension systems |
DE2043526A1 (en) * | 1970-09-02 | 1972-03-09 | Daimler-Benz Ag, 7000 Stuttgart | Hydropneumatic suspension |
FR2386427A1 (en) * | 1977-04-09 | 1978-11-03 | Messerschmitt Boelkow Blohm | ELASTIC LEG, IN PARTICULAR FOR AIRCRAFT LANDING GEAR |
FR2401037A1 (en) * | 1977-08-26 | 1979-03-23 | Daimler Benz Ag | METHOD AND DEVICE FOR ACTIVE DAMPERING OF VEHICLE WHEEL OSCILLATIONS |
US4273303A (en) * | 1979-03-16 | 1981-06-16 | The Boeing Company | Adaptive airplane landing gear |
EP0027869A2 (en) * | 1979-10-27 | 1981-05-06 | Messerschmitt-Bölkow-Blohm Gesellschaft mit beschränkter Haftung | Shock and vibration damping arrangement for vehicles |
US4333668A (en) * | 1979-12-17 | 1982-06-08 | The Bendix Corporation | Electronic adaptive ride control system |
FR2489458A1 (en) * | 1980-08-29 | 1982-03-05 | Messier Hispano Sa | Hydraulic shock absorber e.g. for aeroplane - with absorption characteristic adapted in accordance with force to be absorbed |
EP0114757A1 (en) * | 1983-01-21 | 1984-08-01 | Group Lotus Plc | Vehicle suspension system |
Non-Patent Citations (1)
Title |
---|
Design Engineering, July 1984 (London, GB) "Vehicle active suspension system", pages 36, 37 * |
Cited By (3)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
WO1990015726A1 (en) * | 1989-06-15 | 1990-12-27 | Group Lotus Plc | Vehicle suspension device |
US5590898A (en) * | 1989-06-15 | 1997-01-07 | Group Lotus Plc | Vehicle suspension system |
WO1994023222A1 (en) * | 1993-03-30 | 1994-10-13 | Meyer, Richard, J. | Liquid spring vehicular suspension system |
Also Published As
Publication number | Publication date |
---|---|
JPH064370B2 (en) | 1994-01-19 |
US4830398A (en) | 1989-05-16 |
ATE33593T1 (en) | 1988-05-15 |
EP0142947B2 (en) | 1991-10-23 |
EP0142947B1 (en) | 1988-04-20 |
DE142947T1 (en) | 1985-11-07 |
CA1240713A (en) | 1988-08-16 |
JPS61500957A (en) | 1986-05-15 |
GB8328373D0 (en) | 1983-11-23 |
DE3470490D1 (en) | 1988-05-26 |
EP0142947A1 (en) | 1985-05-29 |
Similar Documents
Publication | Publication Date | Title |
---|---|---|
EP0142947B1 (en) | Vehicle suspension arrangements | |
US4753328A (en) | Vehicle suspension systems and damping arrangements therefor | |
US5749596A (en) | Latchable stabilizer bar actuator | |
US4639013A (en) | Vehicle suspension arrangements | |
US5299488A (en) | Active suspension system | |
US5285878A (en) | Cylinder including a piston with a valve control | |
EP0219209A1 (en) | Vehicle suspension damper with remote control | |
GB2154700A (en) | Control of dampers for vehicle suspension | |
US20100109276A1 (en) | Controllable vehicle suspension system with magneto-rheological fluid device | |
US4613116A (en) | Air suspension | |
US6817597B1 (en) | Spring-and-shock absorber system having differential roll bellows | |
EP2150457A1 (en) | Controllable vehicle suspension system with magneto-rheological fluid device | |
US4293139A (en) | Power steering pump powered load leveler | |
CA1059103A (en) | Electrically responsive static-pressure regulating valve | |
CN212564196U (en) | Pneumatic adjustable damping shock absorber for vehicle | |
EP0347921B1 (en) | A fluid spring | |
JP2905481B2 (en) | Suspension unit | |
EP0331213B1 (en) | Piston movement damping arrangements | |
EP0289364A2 (en) | Vehicle suspension systems | |
Dunwoody | Digital active suspension | |
JPS6328754A (en) | Brake liquid pressure control valve | |
KR940009287B1 (en) | Electronic proportional dissipating pressure valve for a hydraulic shock absorber | |
JPH07501285A (en) | double piston strut | |
JPS61125906A (en) | Suspension of vehicle | |
JPS61125905A (en) | Suspension of vehicle |
Legal Events
Date | Code | Title | Description |
---|---|---|---|
AK | Designated states |
Designated state(s): JP US |