CN101443204A - Vehicle roll control system with self-centering actuator - Google Patents

Vehicle roll control system with self-centering actuator Download PDF

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Publication number
CN101443204A
CN101443204A CNA2005800501201A CN200580050120A CN101443204A CN 101443204 A CN101443204 A CN 101443204A CN A2005800501201 A CNA2005800501201 A CN A2005800501201A CN 200580050120 A CN200580050120 A CN 200580050120A CN 101443204 A CN101443204 A CN 101443204A
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CN
China
Prior art keywords
cylinder
actuator
spring
vehicle
port
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Pending
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CNA2005800501201A
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Chinese (zh)
Inventor
R·J·巴伦
B·J·甘泽尔
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Kelsey Hayes Co
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Kelsey Hayes Co
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Publication of CN101443204A publication Critical patent/CN101443204A/en
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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B15/00—Fluid-actuated devices for displacing a member from one position to another; Gearing associated therewith
    • F15B15/08—Characterised by the construction of the motor unit
    • F15B15/14—Characterised by the construction of the motor unit of the straight-cylinder type
    • F15B15/1423—Component parts; Constructional details
    • F15B15/1476—Special return means
    • 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
    • B60G17/016—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 their responsiveness, when the vehicle is travelling, to specific motion, a specific condition, or driver input
    • B60G17/0162—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 their responsiveness, when the vehicle is travelling, to specific motion, a specific condition, or driver input mainly during a motion involving steering operation, e.g. cornering, overtaking
    • 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
    • B60G21/0551—Mounting means therefor
    • B60G21/0553—Mounting means therefor adjustable
    • B60G21/0555—Mounting means therefor adjustable including an actuator inducing vehicle roll
    • 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
    • B60G2202/13—Torsion spring
    • B60G2202/135—Stabiliser bar and/or tube
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B60—VEHICLES IN GENERAL
    • B60G—VEHICLE SUSPENSION ARRANGEMENTS
    • B60G2204/00—Indexing codes related to suspensions per se or to auxiliary parts
    • B60G2204/10—Mounting of suspension elements
    • B60G2204/12—Mounting of springs or dampers
    • B60G2204/122—Mounting of torsion springs
    • B60G2204/1224—End mounts of stabiliser on wheel suspension
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B60—VEHICLES IN GENERAL
    • B60G—VEHICLE SUSPENSION ARRANGEMENTS
    • B60G2204/00—Indexing codes related to suspensions per se or to auxiliary parts
    • B60G2204/80—Interactive suspensions; arrangement affecting more than one suspension unit
    • B60G2204/82—Interactive suspensions; arrangement affecting more than one suspension unit left and right unit on same axle
    • 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
    • B60G2400/104—Acceleration; Deceleration lateral or transversal with regard to vehicle
    • 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
    • B60G2400/204—Vehicle speed
    • 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
    • B60G2400/40—Steering conditions
    • B60G2400/41—Steering angle

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Physics & Mathematics (AREA)
  • Fluid Mechanics (AREA)
  • General Engineering & Computer Science (AREA)
  • Vehicle Body Suspensions (AREA)

Abstract

A system is disclosed for controlling the roll of a motor vehicle. The system comprises a hydraulic cylinder arrangement connected between an unsprung portion of the vehicle and a sprung portion of the vehicle. Various seals and ports are arranged within the hydraulic cylinder arrangement, and a volume of hydraulic fluid is disposed in the bore of the cylinder. By selectively preventing hydraulic fluid flow out of the ports, a piston within the cylinder can only move in a direction toward a neutral position within the cylinder, thus providing a self centering action of the suspension.

Description

Vehicle roll control system with self-centering actuator
Background technology
The present invention relates generally to the power actuated vehicle roll control system, particularly a kind of self-centering actuator that is used for roll control system, and a kind of roll control system that comprises self-centering actuator.
Become known for the suspension of power actuated vehicle, it makes the irregular isolation in the landform that car load and vehicle travel thereon.Half activity suspension for example generally includes spring, and is connected vehicle and props up on the spring and do not prop up shock absorber between the part on the spring.Half activity suspension generally is self-contained, and only the load that puts on it is reacted.On the contrary, in the activity suspension, the reaction of the load that applied is typically provided by the hydraulic pressure or the pneumatic actuator of electric control with being determined.
Except vehicle being propped up part on the spring and road are isolated, and when quickening, slowing down or turning with high relatively speed, also wish stablize vehicle, stop vehicle to prop up and do not prop up the part inclination on spring or the trend of inclination with respect to it in the part on the spring.Therefore, the suggestion suspension remains on basic level attitude with vehicle, and the power source of this position of not considering to manage to overturn.For example, the U.S. Patent No. 5630623 of Ganzel discloses a kind of half activity system that is used for the inclination of controlling machine motor vehicle, it comprises that being connected vehicle does not prop up at the partial sum vehicle on the spring and prop up actuator between the part on the spring, merges as a reference in this content with this patent disclosure.The known control system of U.S. Patent No. 5630623 is the antiroll bar of the locking and unlocking vehicle not only, and regulate the deflection up or down of any one wheel in four wheels of vehicle, and do not consider whether affected vehicle is positioned at the inboard or the outside of rotation, as described in greater detail.
Referring now to accompanying drawing, attached Fig. 1 and 2 represents the half movable no pumping system 10 that is used for the inclination of controlling machine motor vehicle according to the prior art of U.S. Patent No. 5630623.Hydraulic circuit 11a and back hydraulic circuit 11b before system 10 comprises.Actuator 12, the first and second pressure controls or pressure relief valve 14 and 16 before preceding hydraulic circuit 11a comprises, and first and second boiler check valve 18 and 20.Back hydraulic circuit 11b comprises the second back actuator 21, and the similar assembly of other following public and preceding hydraulic circuit 11a.
Respectively each axis around basic horizontal in the wheel 22,24,26 and 28 of vehicle rotatably is installed to element such as cantilever 30,32,34 and 36, these cantilevers form vehicle and do not prop up the parts of the part on spring.Vehicle do not prop up the part on the spring successively by actuator 12 and 21 and anti-roll or anti-Panhard rod 38 and 40 be connected to vehicle and prop up part on spring.
In the actuator 12 and 21 each comprises cylinder, and the piston of back and forth arranging in corresponding cylinder 42 44.One of the cylinder 42 of each actuator 12,21 or piston 44 can be connected on one that is associated in antiroll bar 38,40 or the cantilever 30,32,43,36 drivingly, and another right assembly of each cylinder/piston can be connected on another that is associated in antiroll bar 38,40 or the cantilever 30,32,43,36 drivingly.Shown in attached Fig. 1 and 2, for example, a free end of antiroll bar 38 before the cylinder 42 of preceding actuator 12 is connected to, and piston rod is connected to right front cantilever 30 from the part that cylinder roughly extends downwards.Similarly, back antiroll bar 40 is connected to the cylinder 42 of right rear actuators 21, and the piston 44 of actuator 21 is connected to cantilever 32.
Each actuator 12 and 21 has a pair of port 46,48 and 50,52 respectively, can alternately provide working medium such as hydraulic fluid by this port, and perhaps the end of the cylinder 42 from the either side that is arranged in the piston 44 that is positioned at is wherein extracted this working medium out.Height on the spring that in the actuator 12 and 21 each is used to keep vehicle body to be positioned at the part leave the road surface on its wheel that is associated is more fully described as following.
First pressure-gradient control valve 14 is ratio safety valves, and it is communicated with first port 46 of actuator 12 by hydraulic power line 54.Valve 14 passing ratios are solenoid-operated, and have position of opening and the position of closing.Reality or anticipated load in response to actuator 12, this screw actuator with the effect that applies the proportional power of electric signal thereon under towards this off position excitation valve 14, this has stoped outflow first port 46, in chamber on cylinder 42, produce predetermined pressure to overcome this solenoid force, more fully describe as following.First boiler check valve 18 is arranged in the hydraulic circuit parallel with first pressure-gradient control valve 14, and is only allowing on the direction of first port 46 of actuator 12 by flowing wherein.
Second pressure-gradient control valve 16 also is the ratio safety valve, and is communicated with second port 48 of actuator 12 by hydraulic power line 56.Also passing ratio screw actuator control of valve 16, and can between the position that opens and closes, move by this screw actuator, flow out second port 48 so that stop, in following chamber, produce predetermined pressure at cylinder 42.Second boiler check valve 20 is arranged in the hydraulic circuit parallel with second pressure-gradient control valve 16, and is only allowing on the direction of second port 48 of actuator 12 by flowing wherein.
The back hydraulic circuit 11b of the back actuator 21 hydraulic circuit 11a with preceding actuator 12 basically is identical.Thereby, first port 50 of proportional pressure control valve 58 peace row boiler check valve 60 with back actuator 21 provided communicatively, and second port 52 of another proportional pressure control valve 62 peace row boiler check valve 64 with back actuator 21 provided communicatively.
In operation, electronic control unit (ECU) 70 processing are from the input of one or more vehicle-wheel speed sensors 72, transverse acceleration meter 74 and steering angle sensor 76.Given these inputs, ECU70 predicts the seriousness of inclination on the horizon, and to suitable valve 14 and 58 or 16 and 62 issue control commands.For example, power actuated vehicle may begin to rotate relative to high-revolving left-hand.When not having the compensation of system 10, the part that this rotation can cause vehicle not prop up on spring trends towards around the roughly clockwise direction ground inclination of its longitudinal axis.
In the beginning of this maneuver, sensor 72,74 and 76 sends to ECU70 with the transient conditions signal.ECU70 calculates again or obtains the net pressure P that need produce the chamber from look-up table on the cylinder 42 of one or two actuator 12 and 21, so that the counteracting vehicle roll, and the screw actuator of activation pressure control cock 14 and 58 produce enough preventions flow through these valves, up to the size of pressure P.
In order to offset the vehicle roll of expection in the opposite direction, for example as experience during rotating in dextrad, ECU70 repeats this program, and the screw actuator of excitation valve 16 and 62, so that allow pressure boost in the following chamber of two actuators 12 and 21.In either case, when sensor 72,74 and 76 was indicated the minimizing of offsetting the required instantaneous or expection of vehicle rolls or increased, ECU70 sent a signal to suitable pressure-gradient control valve, so that correspondingly reduce or increase its pressure by boundary.
If on one of actuator, force unexpected load,, then can in a chamber of affected actuator, produce the pressure that increases as what occur during inclination on the projection of a wheel in road.For example, if off front wheel 22 runs into projection and upward deflects during left-hand rotates, then piston 44 in cylinder 42 to top offset, and the increase of the pressure in the last chamber of actuator 12.Even valve 14 is excited to cut out (stoping the inclination of expection) at this moment, the pressure of this increase also can overcome solenoidal power, thereby allows to hang compression, and keeps ride quality., begin to move down and after valve 14 cut out once more, boiler check valve 18 allowed pistons 44 and cantilever 30 to retreat downwards, and can not receive any resistance from roll control system subsequently by this protruding top at wheel 22.This process spends the limited amount time, and in the meantime, because left-hand rotates, vehicle body inclination to the right to a certain degree.Because the last chamber that fluid shifts out actuator 12, so the pressure on actuator 12 in the chamber is got back to before its level of overturning in advance, piston 44 and cantilever 30 are unlikely got back to its initial position fully, and actuator 12 can remain on the state that a little more compresses than before the wheel bump projection, thereby allows the inclination to the right more than hope during left-hand rotates.
Moreover, in view of left-hand rotates, rise and under the situation that valve 14 is excited to cut out at the near front wheel 28 suddenly, cantilever 36 moves up, the antiroll bar 38 of actuator 12 tops is moved upwards up to new raised position with respect to Control arm 30, thereby have an effect, and the pressure in the last chamber of minimizing actuator 12 with extension in the cylinder 42.If the pressure in the last chamber is reduced under the pressure in the pre-loaded holder 78, then boiler check valve 18 allows to flow in the last chamber of actuators 12, so that 12 extension does not have resistance basically from actuator 12 to actuator.New extended position can be near the initial position or can be to exceed initial position promptly more to many position of extension than this initial position, and this depends on the quantity in the last chamber that allows to flow into actuator 12.
Moreover, in view of left-hand rotates, if antiroll bar 38 is positioned at center or center position at first, and for example, when antiroll bar 38 extends to new location, leave initial position excitation valve 14 by antiroll bar 38, then this new location can be near initial position, or crosses this initial position and promptly cross this center or center position to than this initial position multiple pressure position of contracting more.Thereby, we can say that actuator 12 can surpass center position on both direction, promptly actuator 12 can finish in such position, that is and, actuator 12 more manys extension or the multiple pressure position of contracting more than its state at the center position place.
Holder 78 is arranged in each front and back hydraulic circuit that is communicated with pressure- gradient control valve 14,16 and 58,62.By the fluid in the hydraulic circuit is remained under certain pressure, holder 78 plays the effect that stops the cavitation (cavitation) in the system 10 when the wheel deflection of vehicle, and is also any by reservoir this system loss, that leak the fluid of the dynamic sealing of crossing as replenishing.All valve that is used for each front and back hydraulic circuit 11a and 11b and holder are packaged in the unit of installing 80 and 82 near antiroll bar 38 and 40.Front and back hydraulic circuit 11a keeps separating with 11b, so that the valve in each loop is controlled by corresponding antiroll bar, this has eliminated the needs to the flexible hydraulic hose of the costliness of extending from vehicle body to the front and back antiroll bar.
Summary of the invention
The present invention includes a kind of hydraulically operated actuator that is used for the inclination of controlling machine motor vehicle.This actuator is connected vehicle and does not prop up at the partial sum vehicle on the spring and prop up between the part on the spring, is connected to vehicle in the part on the spring and does not prop up part on spring so that optionally vehicle is propped up.This actuator comprises that being fixed to vehicle props up at the partial sum vehicle on the spring and do not prop up piston in the part on spring one, and is fixed to vehicle and props up at the partial sum vehicle on the spring and do not prop up cylinder in the part on spring another.This cylinder has the inside face of limiting hole, and at least the first and second ports.This piston is arranged in the hole of the cylinder between first and second ports, and engages the inside face of this cylinder hermetically.This first and second port connects by fluid conduit systems.This piston a certain amount of hydraulic fluid is arranged in the hole of this cylinder, so that when stoping hydraulic fluid between first and second ports by this fluid conduit systems mobile, only can move on the direction of the center position in this cylinder.
Therefore, the purpose of this invention is to provide a kind of half movable roll control system that comprises above-mentioned actuator, when this roll control system operation, when applying unexpected load thereon, the vehicle hanging element is allowed to get back to its center position.
When reading with reference to the accompanying drawings, to detailed description of the preferred embodiment, various objectives of the present invention and advantage will be readily apparent to persons skilled in the art by following.
Description of drawings
Accompanying drawing 1 is the scheme drawing that is used for the known system of controlling machine motor vehicle inclination.
Accompanying drawing 2 is another scheme drawings of the roll control system of expression in the accompanying drawing 1.
Accompanying drawing 3 is the scheme drawings according to first embodiment of roll control system of the present invention.
Accompanying drawing 3A is another scheme drawing of the roll control system of expression in the accompanying drawing 3.
Accompanying drawing 4 is the scheme drawings according to second embodiment of roll control system of the present invention.
Accompanying drawing 5 is the scheme drawings according to the 3rd embodiment of roll control system of the present invention.
Accompanying drawing 6 is section drawings of check valve apparatus of expression in accompanying drawing 5 schematically.
Accompanying drawing 7 is the scheme drawings according to the 4th embodiment of roll control system of the present invention.
Accompanying drawing 8 is the scheme drawings according to the 5th embodiment of roll control system of the present invention.
Accompanying drawing 9 is the scheme drawings according to the 6th embodiment of roll control system of the present invention.
The specific embodiment
At first, it should be noted that: bearing mark such as upper and lower, top, bottom, top, below, on and under be to use with respect to the orientation of the accompanying drawing of on paper, discussing, and be not orientation for the structure that limits the actual use of the present invention.
Refer again to accompanying drawing, accompanying drawing 3 and 3A represent according to the roll control systems with 110 indications of the present invention, general.With shown in attached Fig. 1 and 2 with the vehicle of being discussed in the similar assembly represented come mark by identical numeral.Roll control system 110 comprises actuator, check valve apparatus 114 and the holder 178 by 112 indications.Preferably check valve apparatus 114 and holder 178 are packaged in the unit 180.Unit 180 is preferably mounted near the spring element 138a.Yet unit 180 also can be installed near the actuator 112 or any other suitable position.The present invention will describe single actuator 112 and related hydraulic circuit.Yet, be appreciated that as above in the face of the roll control system of prior art and describe, the second back actuator and corresponding hydraulic circuit preferably can also be provided.In other words, can provide roll control system 110, the roll control system of its expression and the prior art described in attached Fig. 1 and 2 for the front and back antiroll bar of vehicle.It is also understood that if only provide one, then can be suitably provide at the front or rear face of vehicle according to roll control system of the present invention.And it it must be understood that, can provide first and second actuators at the front or rear face of vehicle, perhaps provides first and second actuators in the front of vehicle, provides third and fourth actuator in the back of vehicle.
The actuator 12 and 21 that actuator 112 is similar to prior art described above is provided use.Actuator 112 comprises cylinder 118, and partly is arranged in the bar 120 in the cylinder 118.With to the similar mode of roll control system of the top prior art of describing with respect to accompanying drawing 1, with the cylinder 118 of actuator 112 or of being connected to drivingly in spring element 138a and the cantilever 30 in the bar 120, and another of this cylinder 118/ bar 120 centerings is connected in spring element 138a and the cantilever 30 another drivingly.
Spring 138a can be the antiroll bar similar to antiroll bar 38, Panhard rod, perhaps any other vehicle can be propped up on the spring and do not prop up part spring connected to one another on spring.
It should be noted that, front or rear face at vehicle provides under the situation of a pair of first and second actuators, a pair of first and second actuators perhaps are provided in the front of vehicle and provide in the back of vehicle under the situation of a pair of third and fourth actuator, this can replace spring element 138a to work to actuator, and spring element 138 (or antiroll bar 38) is not included in the vehicle in this case.
Bar 120 has the first terminal 120a, and this first end provides the structure that bar 120 is connected to spring element 138a or cantilever 30.Bar 120 has the second terminal 120b.The flange 121 of circumferential extension is formed on the bar 120, is positioned at bar 120 endways on the part in the middle of 120a and the 120b.Preferably, flange 121 integrally forms with bar 120.Yet, should be appreciated that this flange can form in any suitable manner.
Cylinder 118 comprises the first end wall 118a and the second end wall 118b.It is the hole that cylinder 118 limits hollow interior 113.Inside 113 is divided into chamber 146, centre chamber 150 and following chamber 148, discusses as following.Cylinder 118 comprises connection structure 118d, and this connection structure is suitable for cylinder 118 being connected to vehicle at the second end wall 118b and props up on the part on the spring or vehicle do not prop up in the part on spring one.Cylinder 118 comprises the port one 52 that is communicated with last chamber 146 fluids.Cylinder 118 comprises the port one 56 that is communicated with centre chamber 150 fluids.Cylinder 118 comprises the port one 54 that is communicated with following chamber 148 fluids.To discuss the purpose of port one 52,156 and 154 below.Cylinder 118 comprises first opening 122 among the first end wall 118a.Cylinder 118 comprises second opening 124 among the second end wall 118b.To discuss the purpose of first and second openings 122 and 124 below.Cylinder 118 comprises the annular lip 130 that extends inward in inner 113, preferably in the centre chamber 150 of cylinder 118.
The first terminal 120a of bar 120 extends by first opening 122 of cylinder 118.The second terminal 120b of bar 120 extends by second opening 124 of cylinder 118.First sealing member 126 is arranged in first opening 122, and between the bar 120 and the first end wall 118a, provides fluid not saturating slipper seal.Similarly, second sealing member 128 is arranged in second opening 124, and between the bar 120 and the second end wall 118b, provides fluid not saturating slipper seal.
The flange 121 of bar 120 has the outer dia less than the inside diameter of annular lip 130, so as bar 120 can be in cylinder 118 crank motion, and flange 121 does not contact annular lip 130.
In a side of annular lip 130, first annular piston 134 is arranged in the cylinder 118.Piston 134 is arranged in bar 120 the first terminal 120a around.Opposite side away from the annular lip 130 of piston 134 is arranged in second annular piston 136 in the cylinder 118.Piston 136 is arranged in around the second terminal 120b of bar 120.In first and second pistons 134 and 136 each comprises sealing elements therein 138,140 respectively, thereby provides fluid not saturating slipper seal between one of association in bar 120 and the first piston 134 and second piston 136.Similarly, on the excircle of the first piston 134 and second piston 136, provide outer seal component 142 and 144 respectively, so that in first and second pistons 134 and 136, provide fluid not saturating slipper seal between the inner wall surface of related and cylinder 118.134,136 cooperations of first and second pistons are divided into chamber 146 between the second end wall 118b of cylinder 118 and second piston 136 with the inside 113 of cylinder 118, in first end wall 118a of cylinder 118 and the following chamber 148 between the first piston 134, and the centre chamber 150 between the first piston 134 and second piston 136.The flange 130 of cylinder 118 and the flange 121 of bar 120 are arranged in inner 113.
Last chamber 146 has the spring 147 that is arranged in wherein.Spring 147 promotes piston 134 to annular lip 130.Following chamber 148 comprises the spring 149 that is arranged in wherein.Spring 149 promotes piston 136 to annular lip 130.
When piston 134 and 136 adjacent flange 130 location, piston 134 and 136 is positioned at its corresponding neutral or " " center " position, and actuator 112 is positioned at its neutral or " " center " position.Notice, in the description of this embodiment of the present invention, and in the embodiment that describes below, use term " " center " generally but be not necessarily to mean the structure of roll control system 110, actuator 112, the accurate mid point of cylinder 118, so bar 120 is with respect to the mid point of cylinder 118 stroke range." " center " only means that expression is not in the position of bar 120 with respect to the end of cylinder 118 strokes in use.Should be appreciated that neutrality be for be described in vehicle general smoothly advance during preferred or normal position.Thereby this center position is the center typically, yet should be appreciated that this center position can be any suitable optimum position.
When piston 134 moves away flange 130 by bar 120, actuator 112 elongations.When piston 136 by bar 120 when flange 130 leaves, actuator 112 compressions.When flange 121 was aimed at (coplane) with the flange 130 of cylinder 118, bar 120 was positioned at its center position.
The last chamber 146 of cylinder 118 is connected with port one 52,, can provides or discharge working medium such as hydraulic fluid from the last chamber 146 that cylinder 118 is associated by this port.The following chamber 148 of cylinder 118 is connected with port one 54, by this port, can provide or discharge working medium such as hydraulic fluid from the following chamber 148 that cylinder 118 is associated.The centre chamber of cylinder 118 is connected with port one 56, by this port, can provide or discharge working medium such as hydraulic fluid from the centre chamber 150 that cylinder 118 is associated.Check valve apparatus 114 is communicated with the port one 56 of actuator 112 by hydraulic power line 158, and is communicated with port one 52,154 by hydraulic power line 160.Holder 178 is communicated with hydraulic power line 158 fluids between check valve apparatus 114 and the port one 56.
Check valve apparatus 114 passes through solenoid-operated, and has the position and the non-return position of opening.When dead check valve apparatus 114, it is in the non-return position, the non-return element of this check valve apparatus 114 is in that the direction of (promptly from port one 56 to port one 52 and/or 154) allows to flow through check valve apparatus 114 from hydraulic power line 158 to hydraulic power line 160, and stops fluid to flow through check valve apparatus 114 on the opposite sense that flows.Thereby, when the screw actuator of dead check valve apparatus 114, stop by check valve apparatus 114 and hydraulic pressure unit 158 to enter flowing of centre chamber 150 via port one 56.
Except when wish inclination when control (except when along straight relatively path operations vehicle time), the screw actuator of excitation check valve apparatus 114, the while vehicle is in the operation.When excitation, check valve apparatus 114 is in the position of opening, so that check valve apparatus 114 allows on either direction by flowing wherein, and this fluid can be mobile in the direction from port one 52,154 towards port one 56.For example, when check valve apparatus 114 is in the position of opening, and actuator 112 is during by elongation, and bar 120 moves freely, so that flange 121 towards first end wall 118a move, and again towards the first end wall 118a mobile piston 134.Similarly, for example, when check valve apparatus 114 was in the position of opening and compressive activation device 112, bar 120 moved freely, so that flange 121 towards second end wall 118b move, and again towards the second end wall 118b mobile piston 136.Bar 120 and piston 134 can move in corresponding chamber 148, this be because when piston with fluid from the chamber during 148 discharges, the fluid of discharge can enter centre chamber 150.Similarly, bar 120 and piston 136 can move in chamber 146, this be because when piston 136 with fluid from the chamber 146 whens discharges, fluid can enter centre chamber 150.On the contrary, when piston 134 when flange 130 moves, the fluid of discharging from centre chamber 150 is by check valve apparatus 114, and inlet chamber 148.
The reality of responsive actuation device 12 or anticipated load, screw actuator is not energized, so that check valve apparatus 14 is got back to the non-return position.When dead check valve apparatus 114, can be from centre chamber's 150 release fluids, but fluid can not be from the chamber 146,148 be provided to centre chamber 150, as mentioned above.For example, when actuator 12 is positioned at center position, or when under the load that trends towards compressive activation device 112, slightly being compressed, stop bar 120 to move away the center of cylinder 118, because move away the center of cylinder 118, bar 120 must be towards the second end wall 118b driven plunger 136, so that the fluid of going up in the chamber must outflow port 152.Yet, if boiler check valve 114 is positioned at the non-return position, flow for this, there is not the flow channel of inlet chamber 150.Fluid can't flow in the chamber 148, and this is because piston 136 against flange 130, and can not move volume with propagation chamber 148.Yet, even the screw actuator of dead check valve apparatus 114 also allows to leave flowing of chamber 150.Thereby piston 136 freely moves towards its center position, no matter actuator when extend (that is to say, when the flange on the bar 120 121 from compression position when center position moves).When the flange on the bar 120 121 when center position moves, spring 148 promotes pistons 136 and follows, fluid is discharged from retract chamber 150 and is left port, by check valve apparatus 114, to port one 52, and enters expansion chambers 146 by pipeline 160.
If actuator 112 is subjected to trending towards the power of extension actuator 112, bar 120 attempts from the center that (or from initial extended position) moves away, and has stoped fluid to flow equally and has left chamber 148.Yet bar 120 and piston 134 always freely move towards its center position, no matter the screw actuator of check valve apparatus 114 dead whether.When bar 120 when its center position moves, the spring 149 of green phase association is pushed piston 134 to its center position, and the fluid in the retract chamber 150 flows to the expansion chambers 148 of the opposite side of mobile piston 134 by check valve apparatus 114.Another piston 136 keeps taking one's seat with respect to annular lip 130, even contact with the flange 121 of bar 120, as long as check valve apparatus 114 is unperturbed, flows into chamber 150 thereby stop.Should be noted that and not expect flowing of from the chamber 148 inlet chambers 146 that if this is to leave center position because bar 120 promotes pistons 134, then piston 136 usually can adjacent flange 130; Chamber 146 can not further be expanded, to accept the fluid from chamber 148.In preferred embodiment, spring 147 and 149 spring force are enough with enough fast speed mobile piston 136 and 134 respectively, so that under normal operating conditions, when the position takes place to change fast, if flange 121 presses one in piston 136 and 134, bar 120 quick travel, and flange 121 presses in piston 136 and 134 another, then flange 121 through its center positions with before in contact piston 136 or 134 another, first in the piston 136 and 134 can must be got back to its center position.Yet, can expect, in other embodiments, under the rapid-varying situation of the position of flange 121, if flange 121 presses one in piston 136 and 134, bar 120 quick travel, and flange 121 presses in piston 136 and 134 another, then first in piston 136 and 134 got back to before its center position, and flange 121 can be got back to its center position, and flange 121 is understood some and moved out its center position slightly.
Can expect that check valve apparatus 114 can be made up of any valve gear that can carry out above-mentioned functions.Check valve apparatus 114 can comprise boiler check valve and bypass disc.Can determine the situation of bypass disc by any suitable method.A kind of such method is a. g. of inductively measuring via the driving circuit performance, as what describe in the U.S. Patent No. 6577133 of Barron, at this its disclosed content is merged as a reference.
The roll control system that is different from prior art, when the screw actuator of dead check valve apparatus 114, roll control system 110 allows bar 120 to move towards center position, stops bar 120 further to leave center position simultaneously.Therefore, the spring element 138a of association is locked in the appropriate position,, still can gets back to center or center position on the direction of leaving center or center position so that related spring element 138a can not move.Thereby, if at first spring element 138a is locked onto the position that makes the undesirable quantity of vehicle roll, run into when making wheel move the uneven road surface of (trending towards alternately compressing and extension actuator 112) up and down at relevant wheel, actuator 112 can be got back to corresponding center position hardy with relevant spring element 138a.
Be to be understood that, front or rear face at vehicle provides under the situation of a pair of first and second actuators, a pair of first and second actuators perhaps are provided in the front of vehicle, provide under the situation of a pair of third and fourth actuator in the back of vehicle, spring element 138 is not included in the vehicle, and this to actuator optionally the locking and unlocking vehicle prop up on the spring and do not prop up part on spring.In release, this will serve as spring element to actuator, and make vehicle ' steady.
Holder 178 is communicatively connected to hydraulic power line 158 between port one 56 and the check valve apparatus 114.Provide holder 178 with compensation at any amount of fluid that leaks out system of the life period of holder 178, and explanation is because the variable density that causes of temperature traverse.Holder 178 is preferably with the low-voltage memory of about 2 crust to about 5 bar pressures operation.
Referring now to accompanying drawing 4, shown is according to second embodiment by 210 roll control systems of indicating of the present invention, general.Roll control system 210 is similar to roll control system 110, and wherein similar element uses the corresponding digital of increase by 100 to be numbered.Those are different from the element of roll control system 100 described elements only to describe roll control system 210.Single actuator 212 of the present invention and hydraulic circuit are described.Yet, should be appreciated that as mentioned above, the second back actuator and the corresponding hydraulic circuit of the hydraulic circuit that is similar to single actuator 212 and is associated preferably also is provided.
Actuator 212 comprises cylinder 218.Cylinder 218 has the first end wall 218a and the second end wall 218b.Bar 220 extends through the opening 222 among the first end wall 218a of cylinder 218, and enters the chamber of cylinder 218.Bar 220 is mounted to crank motion in the chamber of cylinder 218.Sealing member 226 is arranged in the opening 222, so that between bar 220 and cylinder 218, provide fluid not saturating slipper seal.Be different from the bar 120 at preceding embodiment, bar 220 does not extend through second opening in the cylinder 218.Thereby required outer seal reduces to one in the cylinder 218, and promptly sealing member 226.
On the other end of the bar 220 in being arranged at cylinder 218, bar 220 comprises the flange 221 of circumferential extension, and this flange extends outwardly into the inside 113 of cylinder 218, so as bar 220 can be in cylinder 218 crank motion, and flange 221 can not contact annular lip 230.First annular piston 234 is arranged in the cylinder 218 of a side of annular lip 230 and flange 221.Second piston 236 is arranged in the cylinder 218 of the opposite side of the flange 221 of annular lip 230 and bar 220.Second piston 236 is not the ring-type element the same with first piston 136, and bar 220 is not to extend by second piston 236.Second piston 236 can be included in the outer seal component 242 that the not saturating slipper seal of fluid is provided between the inwall of second piston 236 and cylinder 218.First piston 234 is similar to first piston 134.First and second pistons 234 and 236 cooperations are divided into chamber 246, time chamber 248 and centre chamber 250 generally to be similar to system's 110 described modes with the inside of cylinder 218.
Because the change section branch of bar 220 extends in the cylinder 218, so the volume change that occupies by bar 220 in the cylinder 218.Therefore, the variation of the fluid pressure that the temperature traverse by system 210 that must not only compensate holder 278 causes, and the fluid volume that causes owing to the loss from system's 210 leak fluid changes, but also will compensate in the remainder of this system 210, because the part of bar 220 moves into and leaves the variation of the potential fluid volume that the cylinder 218 of system 210 causes.
System 210 comprises the fluid conduit systems 260 that connects last chamber 246 and following chamber 248.Fluid conduit systems 260 is also via check valve apparatus 214 communication chamber 250.Check valve apparatus 214 comprises screw actuator 214a, makes check valve apparatus 214 be positioned at " opening " position at that time when encouraging, and in this position, fluid can be crossed the check valve apparatus 214 between fluid conduit systems 260 and the chamber 250 at the either direction upper reaches.When dead screw actuator 214a, check valve apparatus 214 is positioned at " non-return " position, and in this position, fluid can be from the chamber 250 enters fluid conduit systems 260, but fluid impassabitity check valve apparatus 214 is from fluid conduit systems 260 inlet chambers 250.
System 210 further comprises holder 278, and it is communicated with chamber 250 continuous fluids.
For example, when the screw actuator 214a of excitation check valve apparatus 214 so that check valve apparatus 214 is positioned at the position of opening, and the external force compression is on actuator 212 time, bar 220 and piston 236 freely move towards the second end wall 218b.Yet, when the screw actuator 214a of dead boiler check valve 214 so that check valve apparatus 214 is positioned at the non-return position, piston 236 and bar 220 are limited to leave center position or flange 230.
For example, when the screw actuator 214a of excitation check valve apparatus 214 so that check valve apparatus 214 is positioned at open position, and force-extension is when acting on the actuator 212, bar 220 and piston 234 freely move towards the first end wall 218a.Yet, when the screw actuator 214a of dead boiler check valve 214 so that check valve apparatus 214 is positioned at the non-return position, piston 234 and bar 220 are limited to leave center position or flange 230.
Further for example, under the situation that check valve apparatus 214 is normally opened, when dead check valve apparatus 214 and actuator 212 were compressed, bar 220 and piston 236 freely moved towards the second end 218b.In addition, when dead check valve apparatus 214 and actuator 212 elongations, bar 220 and piston 234 freely move towards the first end 218a.
Similarly, further for example, under the situation that check valve apparatus 214 is normally opened, when excitation check valve apparatus 214, piston 236 and bar 220 are limited to leave center position or flange 230.In addition, when excitation check valve apparatus 214, limited piston 234 and bar 220 leave center position or flange 230.
Referring now to accompanying drawing 5, shown is according to the 3rd embodiment by 310 roll control systems of indicating of the present invention, general.Roll control system 310 generally is similar to aforesaid roll control system 110.Those and roll control system 110 described different elements of roll control system 310 are only described.Single actuator of the present invention and hydraulic circuit will be described.Yet, should be appreciated that as mentioned above, also for vehicle provides second actuator and corresponding hydraulic circuit, so that provide roll control system in the front and back of vehicle.Can be on vehicle, to use roll control system 310 with the similar mode of above-mentioned first embodiment.
Actuator 312 comprises cylinder 318.Cylinder 318 has the first end wall 318a, the second end wall 318b, and the cylindrical wall 318c that extends between the first end wall 318a and the second end wall 318b.Cylindrical wall 318c has the inside face of limiting hole 313.Form axially open 322 by the first end wall 318a.The second end wall 318b preferably be suitable for being connected to vehicle on the partial sum on the spring does not prop up in the part on spring one.
Cylinder 318 has first radial port 354.First port 354 passes the first end wall 318a and radially forms.Cylinder 318 has second radial port 356.The cylindrical wall 318c that second port 356 passes the contiguous first end wall 318a radially forms.Cylinder 318 has the 4th radial port 352.The cylindrical wall 318c that the 4th port 352 passes the contiguous second end wall 318b radially forms.The 4th port 352 is the vent windows that lead to atmosphere.Cylinder 318 has the 3rd radial port 353.The cylindrical wall 318c that the 3rd port 352 passes between second radial port 356 and the 4th radial port 352 radially forms.Further describe the purpose of port 352,353,354 and 356 below.
Cylinder 318 has the first groove 326a, and this groove is formed on the inside face that is adjacent to the axially open 322 among the cylinder 318 exterior end wall 318a, to receive first sealing member 326.Cylinder 318 has the second groove 343a, and this second groove is formed on the inside face that is adjacent to the axially open 322 among the cylinder 318 in-to-in end wall 318a, so that receive second sealing member 343.
Cylinder 318 has the 3rd groove 341a, and the 3rd groove forms on the inside face of the cylindrical wall 318c between the first end wall 318a and the second end wall 318b, so that receive the 3rd sealing member 341.Cylinder 318 has the 4th groove 351a, the 4th groove with the vertically slight position at interval of the 3rd groove 341a, on the inside face of the cylindrical wall 318c between the 3rd groove 341a and the second end wall 318b, form, so that receive the 4th sealing member 351.
Cup piston 335 is arranged in the cylinder 318.This piston has the first terminal 335a and the second terminal 335b.The first terminal 355a of piston 355 is the ends that open wide, and towards the first terminal 318a of cylinder 318.The second terminal 355b of piston 355 is the ends of closing, and towards the second terminal 318b of cylinder 318.Piston 335 comprises the annular lip 337 near the first terminal 335a.Flange 337 extends radially inwardly.The purpose of flange 337 is described below.
Bar 320 extends to the inside of cylinder 318 by the axially open in the cylinder 318 322, and extends through the first terminal 335a that opens wide of piston 335.Bar 320 is installed on the cylinder 318, so that crank motion therewith.The sealing member 326 that is arranged in the axially open 322 provides the fluid of slip not seal thoroughly between bar 320 and cylinder 318.Notice, be different from the bar 120 of first embodiment, bar 320 does not extend by second opening in the cylinder 318; Therefore need some differences (describing below) in the operation.
The other end in bar 320 is arranged in piston 335, bar 320 comprise the flange 321 of circumferential extension, and this flange extends outwardly into the inside of piston 335.Bar 320 has the circumferential groove 321a that arranges near flange 321.Preferably between annular lip 337 and flange 321, provide ring liner, although under the condition of the diameter of the flange on this bar greater than the internal diameter of the opening among the piston 335 first terminal 335a that limited by annular lip 337, this not necessarily.Most preferably, liner 339 is arranged in the groove 321a.Ring liner 339 most preferably is the Bellville packing ring.The annular lip 337 of piston 335 and ring liner cooperation remain on the flange 321 of bar 320 in the piston 335.Should be appreciated that similar ring liner can be suitable in officely what using in its embodiment described here, though this liner is not illustrated.
First sealing member 326 and second sealing member 343 are cooperated to limit annular first fluid chamber 354a in cylinder 318 with cylinder 318 and bar 320.First fluid chamber 354a is communicated with first port, 354 fluids.Second sealing member 343, the 3rd sealing member 341, piston 335, bar 320 and cylinder 318 cooperations are limited in the cylinder 318 with second fluid chamber 345 with variable-volume.Second fluid chamber 345 is communicated with second port, 356 fluids.Second fluid chamber 345 also with the internal fluid communication of piston 335 because liner 339 forms the not saturating sealing of fluid between bar 320 and piston 335.The 3rd sealing member 341 and the 4th sealing member 351 are cooperated so that annular the 3rd 353a of fluid chamber is limited in the cylinder 318 with piston 335 and cylinder 318.The 3rd 353a of fluid chamber is communicated with the 3rd port 353 fluids.The 4th sealing member 351 and the second end wall 318b and piston 335 and cylinder 318 cooperations are limited in the cylinder 318 with the 4th 352a of fluid chamber with variable-volume.The 4th 352a of fluid chamber leads to atmosphere via the 4th port 352.
Roll control system 310 comprises holder 378.As directed, holder 378 most preferably is traditional low pressing spring holder, although this not necessarily.Holder 378 comprises the first port 378a.Holder comprises the second port 378b.The second port 378b is as the vent window to atmosphere.Should be appreciated that any holder that is suitable for using described here, and can in arbitrary embodiment of the present invention, use at any holder of this expression or description.
First port 354 of cylinder 318 is connected to the first port 378a of holder 378 via hydraulic power line 347, and it has such effect, that is, the fluid between sealing member 326 and 343 is kept the pressure same with holder 378.Thereby the fluid between the sealing member 326 and 343 for example can not experience because the increase of the destructive pressure that variation of temperature causes.Similarly, the 3rd port 353 of cylinder 318 is connected to the first port 378a of holder 378 via hydraulic power line 347, and equally the fluid between sealing member 341 and 351 is kept the pressure same with holder 378.
Roll control system 310 comprises check valve apparatus 314.Check valve apparatus 314 comprises the first little opening valve 314a, and second largest opening valve 314b, and its purpose is described below.Shown check valve apparatus 314 is positioned at unperturbed " non-return " position of each valve 314a and 314b, thereby only allows to enter the flowing of cylinder 318 by check valve apparatus 314 via port 356 from hydraulic power line 347.When excitation valve 314a and 314b, described check valve apparatus 314 be known as be positioned at excitation, circulation or aperture position, wherein fluid not only can be from check valve apparatus 314 entry ports 356, and can outflow port 356 enter hydraulic power line 347 by check valve apparatus 314.
The embodiment of expression check valve apparatus 314 in accompanying drawing 6.Check valve apparatus 314 is representative type secondary screw actuator boiler check valve preferably.Yet, should be appreciated that and can use any suitable valve gear.Check valve apparatus 314 has the first little opening valve 314a, and this opening valve is opened the differential pressure that strides across valve with minimizing.In case pressure reduces, so that be applied to pressure on this valve less than the electromagnetic force that is applied on the check valve apparatus 314, then second largest opening valve 314b opens.Like this, controllably discharge differential pressure.
Check valve apparatus 314 is carried out the function roughly the same with check valve apparatus 114.Yet, when with check valve apparatus 314 when dead switches to foment, check valve apparatus 314 also provides the may command of pressure to discharge in addition.When the excitation first little opening valve 314a, because the first little opening valve 314a partly opens, fluid can be crossed check valve apparatus 314 with low relatively velocity flow, and the first little opening valve 314a can not open second largest opening valve 314b, up to acting on till pressure on the second largest opening valve 314b descends fully, so that the power that the first little opening valve 314a acts on the second largest opening valve 314b can overcome the pressure that acts on the second largest opening valve 314b.
Port 356 is connected second Room 345 communicatively with check valve apparatus 314, and is connected to holder 378 via check valve apparatus 314 and hydraulic power line 347.
Roll control system 310 comprises load port 390.Load port 390 is connected to hydraulic power line 347.The load port 390 of closing usually is manual unlocking suitably, so that make system's discharging and loading as required, for example is used for periodical maintenance, or is used for mainly loading between manufacturing or installation period.Fluid in the actuator 312 is remained under certain pressure by holder 378.More particularly, pressure and the difference between the bar pressure in the chamber 345 act on piston 335, so that promote piston 335 towards the second end wall 318b.During operation, as described below, actuator 312 can be subjected to enough pulling force, because the power of this differential pressure generating, and bar 320 can leave end wall 318b with piston 335 pullings to overcome.
As shown in Figure 5, bar 320 and piston 335 are in the center position with respect to cylinder 318.When excitation during check valve apparatus 314, bar 320 and piston 335 be crank motion in cylinder 318 freely as required.When bar 320 moves to the inside of cylinder 318 more, the sport that bar 320 and piston 335 enter compression position makes fluid discharge from second Room 345.Can be in holder 378 with the fluid storage of discharging.On the contrary, when actuator 312 elongation and bar 320 less are arranged in the cylinder 318, will be from the fluid of holder 378 by in the check valve apparatus 314 suction cylinders of opening 318, up to the center position of bar 320 shown in moving to, the flange 337 of ring liner 339 contact pistons 335, and begin to make piston 335 to move away from the second end wall 318b to move.In case this generation, fluid will be transferred to (diameter of piston 335 is greater than the diameter of 345 bars of recalling 320 from the chamber) the holder 378 from second Room 345.
When dead check valve apparatus 314, for example, roll control system 310 in use, fluid impassabitity second port 356 leaves cylinder 318, thereby bar 320 and piston 335 be with respect to cylinder 318 lockings, so that bar 320 can not further extend in the piston 335.By the same token, piston 335 can not be moved down in second Room 345.Yet, if the fluid pressure in the holder 378 (generally can be like this greater than the fluid pressure in second Room 345, do not prop up the momentary duty that produces between the part on the spring except propping up at the partial sum on the spring at vehicle), fluid can enter second Room 345 from holder 378.Thereby, if any one in bar 320 and the piston 335 is not in center position when dead check valve apparatus 314, then allow bar 320 and piston 335 to get back to center position.
Be similar to second above-described operation of embodiment, because the variable part of bar 320 can extend in the cylinder 318, so the volume change that occupies by bar 320 in the cylinder 318.Therefore, holder 378 not only must compensate because the variation of the fluid pressure that the fluid loss of revealing from system 310 causes, and must compensate the potential variation of the system that shutdown system caused 310 inner volumes that a part owing to bar 320 moved into and left the cylinder 318 of system 310.
As mentioned above, if the pressure in the holder 378 is higher than the pressure in second Room 345, then the fluid from holder 378 can flow into second Room 345 by check valve apparatus 314, even when dead check valve apparatus 314.Spring is included in the volume of having adjusted in the holder 378 in the holder 378, thereby holder 378 makes system 310 keep pressurization, thereby continuously piston 335 is pushed in the center position, and check valve apparatus 314 is in the position of opening.Yet, it must be understood that, can use any suitable holder.
When 310 vehicles thereon of system were advanced, the actuator 312 of roll control system 310 was subjected to trending towards the power of compressive activation device 312 once in a while, and is subjected to trending towards the power of extension actuator 312.By the check valve apparatus 314 of excitation, fluid freely flows on either direction by check valve apparatus 314, thereby can freely flow into and flow out cylinder 318.This means that actuator 312 relatively freely extends and compresses, travel to provide more stably thereby the suspension of permission vehicle absorbs these power.This is normally along the situation of the road straight-line travelling of relatively flat.Yet, when having the situation of wishing raising inclination control, can not encourage check valve apparatus 314.
If dead check valve apparatus 314 when actuator 312 is in its center position (in as accompanying drawing 5 expression) then hydraulically is locked in bar 320 and cylinder 318 position relative to each other, and can not leaves center position.If actuator 312 is compressed power during this situation that " is locked in neutrality ", then stop the fluid in second Room 345 to flow out second port 356, this is because check valve apparatus 314 blocks this flowing.Piston 335 is against the second end wall 318b of cylinder 318.Thereby bar 320 can not move from the center position with respect to cylinder 318, to allow actuator 312 compressions.Similarly, if during this situation that " is locked in neutrality ", actuator 312 is subjected to trending towards the power of extension actuator 312, then stops the fluid in second Room 345 to flow out second port 356, and this is because check valve apparatus 314 blocks this flowing.Thereby bar 320 can not move from the center position with respect to cylinder 318, to allow actuator 312 elongations.
If dead check valve apparatus 314 when actuator 312 is in its compression position then will stop actuator 312 to move (if additional compression force is on actuator 312) towards the position that it more compresses.As situation about discussing in the paragraph in front, if the compressive force that actuator 312 is added when being in the situation of this " compression locking " then stops the fluids in second Room 345 to flow out second port 356, this is because check valve apparatus 314 blocks this flowing.Thereby bar 320 can not move towards the position that actuator 312 more compresses from the compression position with respect to cylinder 318 that exists when check valve apparatus 314 is closed.
Yet when actuator 312 was in this compression position and is subjected to trending towards the power of extension actuator 312, actuator 312 freely moved towards its center position.When under the effect of bar 320 at these extending forces when mobile, the increase in volume of second Room 345, thus reduced the pressure of this volume inner fluid.Reach center position (perhaps encouraging check valve apparatus 314 again) up to actuator 312, fluid via hydraulic power line 347, flows freely into second Room 345 via second port 356 and check valve apparatus 314 from holder 378, so that fill second Room 345 of expansion.Yet, in case bar 320 moves to center position, further moving the second end wall 318b that will make piston 335 leave cylinder 318, this will trend towards fluid is discharged from second Room 345, as mentioned above.Thereby, trend towards making actuator 312 to move to the further motion of expanded position by check valve apparatus 314 preventions, as mentioned above.
Similarly, if when actuator 312 is positioned at its extended position dead check valve apparatus 314, then stop actuator 312 to move (if additional tension on actuator 312) towards the position that it more extends.As mentioned above, if the pulling force that actuator 312 is added when being in " elongation locking " situation then stops the fluid in second Room 345 to flow out second port 356, this is because check valve apparatus 314 blocks this flowing.Thereby bar 320 can not move towards the position that actuator 312 more extends from the extended position with respect to cylinder 318 that exists when check valve apparatus 314 is closed.
Yet when actuator 312 was in the position of elongation and is subjected to trending towards the power of compressive activation device 312, actuator 312 freely moved towards its center position.When bar 320 and piston 335 under the effect at these compressive forces when mobile, the increase in volume of second Room 345, thus reduced the pressure of this volume inner fluid.Reach center position (perhaps check valve apparatus 314 encourages again) up to actuator 312, fluid freely flows out second Room 345, via second port 356 and check valve apparatus 314, and via hydraulic power line 347 inflow holders 378.Yet, in case bar 320 moves to center position, bar 320 is no longer advanced with piston 335, therefore as mentioned above, stoped by check valve apparatus 314 and to have made actuator 312 move to the further motion of compression position, this is because the further compression movement of bar 320 needs fluid to flow out second Room 345 via port 356, and by unperturbed check valve apparatus 314.
Referring now to accompanying drawing 7, shown is according to of the present invention, general the 4th embodiment by 410 roll control systems of indicating.Roll control system 410 generally is similar to aforesaid roll control system 310.Those that only describe roll control system 410 are different from the element of roll control system 310 described elements.Single actuator 412 of the present invention and hydraulic circuit will be described.Yet, should be appreciated that as mentioned above, can also provide second actuator and corresponding hydraulic circuit for vehicle, so that provide roll control system in the front and back of vehicle.Roll control system 410 can be to use on vehicle with the similar mode of above-mentioned first embodiment.
Actuator 412 comprises cylinder 418.Cylinder 318 comprises the first end wall 418a, the second end wall 418b, and the cylindrical wall 418c that extends between the first end wall 318a and the second end wall 318b.Cylindrical wall 418c has the inside face of limiting hole 413.Pass the first end wall 418a and form axially open 422.The second end wall 418b preferably be suitable for being connected to vehicle at spring on partial sum does not prop up in the part on spring one.
Cylinder 418 has radial port 456.Pass the cylindrical wall 418c that is adjacent to the first end wall 418a and radially form radial port 456.Cylinder 418 has out-of-position axial port 452.The second end wall 418b axial offset ground that out-of-position axial port 452 is passed cylinder 418 forms.Below further discuss the purpose of port 452 and 456.
Cylinder 418 has the first groove 426a, forms on the inside face of the axially open 422 of this first groove in being adjacent to cylinder 418 exterior end wall 418a, so that receive first sealing member 426.Cylinder 418 has the second groove 443a, forms on the inside face of the axially open 422 of this second groove in being adjacent to cylinder 418 in-to-in end wall 418a, so that receive second sealing member 443.
Cylinder 418 has the 3rd groove 441a, and the 3rd groove forms on the inside face of the cylindrical wall 418c between the first end wall 418a and the second end wall 418b, so that receive the 3rd sealing member 441.Cylinder 418 has the 4th groove 494a, and the 4th groove forms on the inside face of the cylindrical wall 418c between the 3rd groove 441a and the second end wall 418b in the position that is adjacent to the second end wall 418b, so that receive piston packing 494.
Cup piston 435 is arranged in the cylinder 418.This piston has the first terminal 435a and the second terminal 435b.The first terminal 435a of piston 435 is the ends that open wide, and towards the first terminal 418a of cylinder 418.The second terminal 435b of piston 435 is the ends of closing, and towards the second terminal 418b of cylinder 418.Piston 435 comprises the annular lip 437 near the first terminal 435a.Flange 437 extends radially inwardly.Discuss the purpose of flange 437 below.
The axially open 422 that bar 420 passes in the cylinder 418 extends into the inside of cylinder 418, and passes through the first terminal 435a that opens wide of piston 435.Bar 420 is installed on the cylinder 418, so that crank motion therewith.Be arranged in sealing members 426 and 443 in the axially open 422 the not saturating sealing of fluid of slip is provided between bar 420 and cylinder 418.Notice that be similar to the bar 320 of the 3rd embodiment and be different from the bar 120 of first embodiment, bar 420 does not extend by second opening in the cylinder 418; Therefore compare with first embodiment, need some differences (discussing below) in operation.
On the end in bar 420 is arranged in piston 435, bar 420 comprises the flange 421 of circumferential extension, and this flange extends outwardly into the inside of piston 435.Bar 420 has the circumferential groove 421a that arranges near flange 421.Preferably between annular lip 437 and flange 421, provide ring liner 439, although the diameter of the flange on bar 421 is greater than this is not necessarily under the situation of the internal diameter of the opening among, the piston 435 first terminal 435a 437 that limit by annular lip.Most preferably, liner 439 is arranged in the groove 421a.Ring liner 439 most preferably is the Bellville packing ring.The annular lip 437 of piston 435 and ring liner 439 cooperations remain on the flange 421 of bar 420 in the piston 435.This liner should be appreciated that similar ring liner is suitable for using in what other embodiment described here in office, although can not illustrate.
Second sealing member 443, the 3rd sealing member 441, piston 435, bar 420 and cylinder 418 cooperations are limited in the cylinder 418 with the fluid chamber 345 with first variable-volume.First fluid chamber 445 is communicated with first port, 456 fluids.First fluid chamber 445 also with the internal fluid communication of piston 435 because liner 439 forms the not saturating sealing of fluid between bar 420 and piston 435.The 3rd sealing member 441, piston 435 and cylinder 418 cooperations are limited to the 452a of fluid chamber of second variable-volume in the cylinder 318.Second 452a of fluid chamber is communicated with second port, 452 fluids.
Roll control system 410 comprises holder 478.As directed, holder 478 most preferably is traditional low pressing spring holder, although not necessarily.Holder 478 comprises the first port 478a.Holder comprises the second port 478b.The second port 478b ventilates with out-of-position axial port 452 collaboratively.Should be appreciated that any holder that is suitable for using described here, and any holder in this expression or description can use in arbitrary embodiment of the present invention.
Roll control system 410 comprises check valve apparatus 414.Check valve apparatus 414 comprises the first little opening valve 414a, and second largest opening valve 414b, discusses its purpose below.Check valve apparatus 414 further comprises independently boiler check valve 492.Independently boiler check valve 492 only allows flowing on from the first port 478a of holder 478 to the direction of first port 456 of cylinder 418.Shown check valve apparatus 414 is in unperturbed " non-return " position that each valve 314a and 314b close, and does not allow any flowing by it.Thereby check valve apparatus 314 only allows to enter the flowing of cylinder 418 by check valve apparatus 414 via port 456 from holder 478.When excitation valve 414a and 414b, described check valve apparatus 414 is known as and is in position excitation, that circulate or open, wherein fluid not only can flow into port 456 from check valve apparatus 414, and can outflow port 456 enter holder 478 by check valve apparatus 414.
The first little opening valve 414a and the second largest opening valve 414b of check valve apparatus 414 preferably form representative type secondary solenoid valve.Yet, should be appreciated that and can use any suitable valve gear.Check valve apparatus 414 has the first little opening valve 414a, and this little opening valve is opened the differential pressure that strides across this valve with minimizing.In case pressure decay, thus at applied pressure on the valve less than the electromagnetic force that on check valve apparatus 414, applies, then second largest opening valve 414b opens.Like this, controllably discharge differential pressure.
Check valve apparatus 414 is carried out the function roughly the same with check valve apparatus 414.Yet, be similar to check valve apparatus 314, when check valve apparatus 414 when dead switches to foment, check valve apparatus 414 provides the controlled release of pressure in addition.When the excitation first little opening valve 414a, fluid is crossed check valve apparatus 414 with relatively low velocity flow, this is because the first little opening valve 414a partly opens, and the first little opening valve 414a can not open second largest opening valve 414b, the power that the first little opening valve 414a acts on the second largest opening valve 414b descends fully up to the pressure that acts on the second largest opening valve 414b, so that can overcome the pressure that acts on the second largest opening valve 414b.
Port 456 is connected first Room 445 communicatively with check valve apparatus 414, and is connected to holder 478 via check valve apparatus 414 and hydraulic power line 447.
Roll control system 410 comprises load port 490.Load port 490 is connected to hydraulic power line 447.The load port 490 of closing usually is suitable for manual unlocking, so that make the electric leakage of this system as required and load, for example is used for periodical maintenance, perhaps be used to make or installation period between main loading.Fluid in the actuator 412 is remained under certain pressure by holder 478.More particularly, the difference of the pressure among pressure in the chamber 445 and the chamber 452a acts on piston 435, so that promote piston 435 towards the second end wall 418b.During operation, as described below, actuator 412 can be subjected to enough pulling force, so that overcomes the power owing to this differential pressure generating, and bar 420 can leave end wall 418b with piston 435 pullings.
As shown in Figure 7, bar 420 and piston 435 are in the center position with respect to cylinder 418.When excitation during check valve apparatus 414, bar 420 and piston 435 can be as required crank motion in cylinder 418 freely.When bar 420 moved to the inside of cylinder 418 more, bar 420 and piston 435 entered the sport of compression position fluid are discharged first Room 445.With the fluid storage of discharging in holder 478.On the contrary, when actuator 412 elongations, and when bar still less 420 is arranged in the cylinder 418, to pass through check valve apparatus 414 suction cylinders 418 from the fluid of holder 478, up to the center position of bar 420 shown in moving to, and the flange 437 of ring liner 439 contact pistons 435, and begin to make piston 435 to move away the second end wall 418b.In case this generation, fluid will be transferred to (diameter of piston 435 is greater than the diameter of 445 bars of recalling 420 from the chamber) the holder 478 from first Room 445.
When dead check valve apparatus 414, for example roll control system 410 in use, fluid impassabitity first port 456 leaves cylinder 418, thereby bar 420 and piston 435 be with respect to cylinder 418 lockings, so that bar 420 can not further extend in the piston 435.Because identical, piston 435 can not be moved down in first Room 445.Yet, if the fluid pressure in the holder 478 (generally can be like this greater than the fluid pressure in first Room 445, except prop up at vehicle on the spring and do not prop up producing between the part on the spring the momentary duty), fluid can flow into first Room 445 from holder 478.Thereby, if any one in bar 420 and the piston 435 is not positioned at center position when dead check valve apparatus 414, allow bar 420 and piston 435 to get back to center position.
Above being similar to respect to the described operation of the second and the 3rd embodiment, because the variable part of bar 420 can extend in the cylinder 418, so the volume change that occupy by bar 420 in the cylinder 418.Therefore, holder 478 not only must compensate because the variation of the fluid pressure that the fluid loss of revealing from system 410 causes, and must compensate the potential variation of the system that shutdown system caused 410 inner volumes that a part owing to bar 420 moved into and left the cylinder 418 of system 410.
As mentioned above, if the pressure in the holder 478 greater than the pressure in first Room 445, can be fed in first Room 445 by check valve apparatus 414 from the fluid of holder 478, even when dead check valve apparatus 414.Spring is included in the volume of having adjusted in the holder 478 in the holder 478, so that holder 478 can maintenance system 410 pressurize, thereby continuously piston 435 is pushed to center position, and check valve apparatus 414 is in the position of opening.Yet, it must be understood that, can use any suitable holder.
When 410 vehicles thereon of system were advanced, the actuator of roll control system 410 was subjected to trending towards the power of compressive activation device 412 once in a while, and is subjected to trending towards the power of extension actuator 412.By the check valve apparatus 414 of excitation, fluid passes through check valve apparatus 414 free-flowing on either direction, thereby can freely flow into and flow out cylinder 418.This means that actuator 412 relatively freely extends and compresses, travel to provide more stably thereby the suspension of permission vehicle absorbs these power.This is normally along the situation of the road straight-line travelling of relatively flat.Yet, when having the situation of wishing raising inclination control, can not encourage check valve apparatus 414.
If when actuator 412 is in its center position dead check valve apparatus 414 when (as shown in Figure 7), then bar 420 and cylinder 418 hydraulically is locked in position relative to each other, and can move from center position.If actuator 412 is compressed power during this situation that " is locked in neutrality ", then stop the fluid in first Room 445 to flow out first port 456, this is because check valve apparatus 414 blocks this flowing.Piston 435 is against the second end wall 418b of cylinder 418.Thereby bar 420 can not move from the center position with respect to cylinder 418, to allow actuator 412 compressions.Similarly, if during this situation that " is locked in neutrality ", actuator 412 is subjected to trending towards the power of extension actuator 412, then stops the fluid in first Room 445 to flow out first port 456, and this is because check valve apparatus 414 blocks this flowing.Thereby bar 420 can not move from the center position with respect to cylinder 418, so that allow actuator 412 elongations.
If dead check valve apparatus 414 when actuator 412 is in its compression position then will stop actuator 412 to move (if additional compression force is in actuator 412) towards the position that it more compresses.As situation about discussing in the paragraph in front, if the compressive force that actuator 412 is added, be in the situation of this " locking when compression " simultaneously, then stop the fluid in first Room 445 to flow out first port, this is because check valve apparatus 414 blocks this flowing.Thereby bar 420 can not move towards the position that actuator 412 more compresses from the compression position with respect to cylinder 418 that exists when check valve apparatus 414 is closed.
Yet when actuator 412 was in this compression position and is subjected to trending towards the power of extension actuator 412, actuator 412 freely moved towards its center position.When the power of bar 420 by these elongations moves, the increase in volume of first Room 445, thus reduced the pressure of this volume inner fluid.Reach center position (perhaps encouraging check valve apparatus 414 again) up to actuator 412, fluid freely flows into first Room 445 from holder 478 via first port 456 and check valve apparatus 414 via hydraulic power line 447, so that fill first Room 445 of expansion.Yet in case bar 420 moves to center position, further sport makes piston 435 leave the second end wall 418b of cylinder 418, and this trends towards fluid is discharged from first Room 445, as mentioned above.Thereby, stoped by check valve apparatus 414 to trend towards making actuator 412 to move to the further motion of extended position, as mentioned above.
Similarly, if when actuator 412 is in its extended position dead check valve apparatus 414, then will stop actuator 412 to move (if additional tension in actuator 412) towards the position that it more extends.As mentioned above, if the pulling force that actuator 412 is added is in the situation that this " locks " simultaneously when elongation, then stop the fluids in first Room 445 to flow out first port 456, this is because check valve apparatus 414 blocks this flowing.Thereby bar 420 can not move towards the position that actuator 412 more extends from the extended position with respect to cylinder 418 that exists when check valve apparatus 414 is closed.
Yet when actuator 412 was in extended position and be subjected to tending to the power of compressive activation device 412, actuator 412 freely moved towards its center position.When bar 420 and piston 435 move by these compressive forces, the increase in volume of first Room 445, thus reduced pressure in this volume.Reach center position (perhaps encouraging check valve apparatus 414 again) up to actuator 412, fluid freely flows out first Room 445, via first port 456 and check valve apparatus 414, and enters holder 478 via hydraulic circuit 447.Yet, in case bar 420 moves to center position, then bar 420 is no longer advanced with piston 435, therefore as mentioned above, stoped by check valve apparatus 414 and to have made actuator move to the further motion of compression position, this is because the further motion of bar 420 needs fluid to flow out first Room 445 via port 456, and by unperturbed check valve apparatus 414.
Referring now to accompanying drawing 8, shown is according to the 5th embodiment by 510 roll control systems of indicating of the present invention, general.Roll control system 510 generally is similar to roll control system 410, and generally is similar to roll control system 210, as mentioned above.Those are different from the element of roll control system 410 and 210 described elements only to describe roll control system 510.Actuator 512 of the present invention and hydraulic circuit are described.Yet, should be appreciated that as mentioned above, also for vehicle provides second actuator and corresponding hydraulic circuit, so that provide roll control system in the front and back of vehicle.Can be on vehicle, to use roll control system 510 with the similar mode of above-mentioned first embodiment.
Actuator 512 has integrated holder 578.Holder 578 is the travellers (strut) with gas spring 549.Holder 578 is similarly operated with the low-voltage memory of describing in preceding embodiment.In addition, actuator 512 does not have any vent window to atmosphere.Actuator 512 has last chamber 585, and this upper chamber portion is filled with oil, and residual volume is filled with gas.
Actuator 512 comprises cylinder 518.Cylinder 518 has the first end wall 518a, the second end wall 518b, and the cylindrical wall 518c that extends between the first end wall 518a and the second end wall 518b.Cylindrical wall 518c has the inside face of limiting hole 513.Pass the first end wall 518a and form axially open 522.The second end wall 518b preferably is suitable for being connected to vehicle and props up on the partial sum on the spring does not prop up in the part on spring one.Cylinder 518 preferably promptly comprises the annular lip 530 that extends inward in inner 513 between the first end wall 518a and the second end wall 518b in the approximate centre of the cylindrical wall 518c of cylinder 518.
Cylinder 518 has first radial port 554.The cylindrical wall 518c that first port 554 passes the contiguous first end wall 518a radially forms.Cylinder 518 has second radial port 552.The cylindrical wall 518c that second port 552 passes adjacent flange 530 radially forms.Further describe the purpose of port 552 and 554 below.
First sealing member 526 is arranged in the opening 522.Second sealing member 541 is arranged in around the inside of the cylinder 518 of cylindrical wall 518c.
Cup piston 535 is arranged in the cylinder 518.Piston has the first terminal 535a and the second terminal 535b.The first terminal 535a of piston 535 is the ends that open wide, and towards the first terminal 518a of cylinder 518.The second terminal 535b of piston 535 is the ends of closing, and towards the second terminal 518b of cylinder 518.Piston 535 comprises the annular lip 537 near the first terminal 535a.Flange 538 inwardly radially extends.Discuss the purpose of flange 538 below.Second sealing member 541 is arranged between cylindrical wall 518c and the piston 535, and between the first Room 554a and the second Room 552a, provides fluid not saturating slipper seal.
Bar 520 extends to the inside of cylinder 518 by the axially open in the cylinder 518 522, and extends through the first terminal 535a that opens wide of piston 535.Bar 520 is installed on the cylinder 518, so that crank motion therewith.The sealing member 526 that is arranged in the axially open 522 provides fluid not saturating slipper seal between bar 520 and cylinder 518.Notice, be similar to the bar 320 of the 3rd embodiment, be different from the bar 120 of first embodiment, bar 520 does not extend by second opening in the cylinder 518; Therefore compare with first embodiment, need the difference (describing) in the certain operations as following.
The end of the bar 520 in being arranged in piston 535, bar 520 comprise the flange 521 of circumferential extension, and this flange extends outwardly into the inside of piston 535.Flange 521 forms circumferential shelf 521a, and this circumferential shelf is arranged towards the terminal 535a that opens wide of piston 535.Preferably between annular lip 537 and flange 521, provide ring liner 539, although under the situation of the diameter of the flange on bar 521 greater than the internal diameter of the opening among, the piston 535 first terminal 535a 538 that limit by annular lip, this not necessarily.Most preferably, liner 539 is arranged on the frame 521a.Ring liner 539 is the Bellville packing ring most preferably.The annular lip 537 of piston 535 and ring liner 539 cooperations remain on the flange 521 of bar 520 in the piston 535.This liner should be appreciated that similar ring liner can be suitable for using in what other embodiment described here in office, although can not be illustrated.
First sealing member 526 and second sealing member 541 and cylinder 518, piston 535 and bar 520 cooperations are so that limit the first fluid chamber 554a of annular variable-volume in cylinder 518.First fluid chamber 554a is communicated with first port, 554 fluids.First fluid chamber 554a also with the internal fluid communication of piston 535, this is because liner 538 forms the not saturating sealing of fluid between bar 520 and piston 535.Second sealing member 541, piston 535 and cylinder 518 cooperations are so that limit second 552a of fluid chamber of variable-volume in cylinder 518.Second 552a of fluid chamber is communicated with second port, 552 fluids.
Roll control system 510 comprises integrated holder 578.As shown in the figure, holder 578 most preferably has the traveller spring holder of gas spring 549.Should be appreciated that any holder that is suitable for using described here, and can in any embodiment of the present invention, use at any holder of this expression and description.
Roll control system 510 comprises check valve apparatus 514.Check valve apparatus 514 is similar to the check valve apparatus 114 of first embodiment.First port 554 is communicated with check valve apparatus 514 fluids via first hydraulic power line 560.Second port 552 is communicated with check valve apparatus 514 fluids via second hydraulic power line 558.Shown check valve apparatus 514 is in unperturbed " non-return " position, thereby only allows to pass through check valve apparatus 514 from second port 552 via second hydraulic power line 558, via first hydraulic power line 560 flowing by first port, 554 inlet chamber 554a.During the position that is in excitation, circulates or opens when check valve apparatus 514 is known as, wherein fluid can not only enter first port 554 from check valve apparatus 514, but also outflow port 554 enters second port 552 by check valve apparatus 514.Check valve apparatus 514 is carried out the function roughly the same with check valve apparatus 114.
Port 554 is connected the first Room 554a communicatively with check valve apparatus 514, and will be connected to holder 578 via check valve apparatus 514.
By holder 578 fluid among the first Room 554a is remained under certain pressure.More particularly, the difference of the pressure among the pressure among the first Room 554a and the second Room 552a acts on piston 535, so that promote piston 535 towards flange 530.During operation, as described below, actuator 512 can be subjected to enough pulling force, because the power that causes of this differential pressure, and bar 520 can leave flange 530 with piston 535 pullings to overcome.
As shown in Figure 8, bar 520 and piston 535 are in the center position with respect to cylinder 518.When excitation during check valve apparatus 514, bar 520 and piston 535 can be as required crank motion in cylinder 518 freely.When bar 520 moved to the inside of cylinder 518 more, bar 520 and piston 535 entered the sport of compression position and discharge fluid from the first Room 554a.Is in the holder 578 with the fluid storage of discharging at the second Room 552a.On the contrary, in actuator 512 elongations, and when bar 520 less is arranged in the cylinder 518, will be from the check valve apparatus 514 suction cylinders 518 of fluid by opening of holder 578, up to the center position of bar 520 shown in moving to, and the flange 537 of ring liner 539 contact pistons 535, and begin to make piston 535 to move away flange 530.In case this generation, fluid will be transferred to (diameter of piston 535 is greater than the diameter of the bar of recalling from chamber 554a 520) the holder 578 from the first Room 554a.
When dead check valve apparatus 514, for example, roll control system 510 in use, fluid impassabitity second port 554 leaves the first Room 554a, thereby bar 520 and piston 535 be with respect to cylinder 518 lockings, so that bar 520 can not further extend in the piston 535.By the same token, piston 535 can not be moved down among the first Room 554a.Yet, if the fluid pressure in the holder 578 (generally can be like this greater than the fluid pressure in the first Room 554a, except prop up at vehicle on the spring and do not prop up producing between the part on the spring the momentary duty), fluid can flow into the first Room 554a from holder 578.Thereby, if any one in bar 520 and the piston 535 is not in center position when dead check valve apparatus 514, will allow bar 520 and piston 535 to get back to center position.
The operation of describing with respect to second embodiment above being similar to is because the variable part of bar 520 can extend in the cylinder 518, so the volume change that is occupied by bar 520 in the first Room 554a.Therefore, holder 578 not only must compensate because the variation of the fluid pressure that the fluid loss of revealing from system 510 causes, and must compensate the potential variation of the system that shutdown system caused 510 inner volumes that a part owing to bar 520 moved into and left the cylinder 518 of system 510.The volume of gas allows the variation of system's 510 this pressure of compensation and/or volume among the second Room 552a.
As mentioned above, if the pressure in the holder 578 is higher than the pressure in the first Room 554a, then the fluid from holder 578 can supply among the first Room 554a by check valve apparatus 514, even when dead check valve apparatus 514.Volume in the holder 578 that comprised setting of spring in traveller so that holder 578 makes system 510 keep pressurization, thereby continuously piston 535 is pushed in the center position, and check valve apparatus 514 is in the position of opening.Yet, it must be understood that, can use any suitable holder.
When 510 vehicles thereon of system were advanced, the actuator 512 of roll control system 510 was subjected to trending towards the power of compressive activation device 512 once in a while, and is subjected to trending towards the power of extension actuator 512.By the check valve apparatus 514 of excitation, fluid freely flows on either direction by check valve apparatus 514, thereby can freely flow into and flow out cylinder 518.This means that actuator 512 relatively freely extends and compresses, travel to provide more stably thereby the suspension of permission vehicle absorbs these power.This is normally along the situation of the road straight-line travelling of relatively flat.Yet, when having the situation of wishing raising inclination control, can not encourage check valve apparatus 514.
If dead check valve apparatus 514 when actuator 512 is in its center position (in as accompanying drawing 8 expression) then hydraulically is locked in bar 520 and cylinder 518 position relative to each other, and can not leaves center position.If actuator 512 is compressed power during this situation that " is locked in neutrality ", then stop the fluid in the first Room 554a to flow out first port 554, this is because check valve apparatus 514 blocks this flowing.Piston 535 has been resisted against on the flange 530 of cylinder 518.Thereby bar 520 can not move from the center position with respect to cylinder 518, to allow actuator 512 compressions.Similarly, if during this situation that " is locked in neutrality ", actuator 512 is subjected to trending towards the power of extension actuator 512, then stops the fluid in the first Room 554a to flow out first port 554, and this is because check valve apparatus 514 blocks this flowing.Thereby bar 520 can not move from the center position with respect to cylinder 518, to allow actuator 512 elongations.
If dead check valve apparatus 514 when actuator 512 is in its compression position then will stop actuator 512 to move (if additional compression force is on actuator 512) towards the position that it more compresses.As situation about discussing in the paragraph in front, if the compressive force that actuator 512 is added when being in the situation of this " compression locking ", then stop the fluid in the first Room 554a to flow out first port 554, this is because check valve apparatus 514 blocks this flowing.Thereby bar 520 can not move towards the position that actuator 512 more compresses from the compression position with respect to cylinder 518 that exists when check valve apparatus 514 is closed.
Yet when actuator 512 was in this compression position and is subjected to trending towards the power of extension actuator 512, actuator 512 freely moved towards its center position.When bar 520 moves by these extending forces, the increase in volume of the first Room 554a, thus reduced the pressure of this volume inner fluid.Reach center position (perhaps encouraging check valve apparatus 514 again) up to actuator 512, fluid from holder 578 via second hydraulic power line 558, freely flow into the first Room 554a via first port 554 and check valve apparatus 514, so that fill the first Room 554a of expansion.Yet, in case bar 520 moves to center position, further moving the flange 530 that will make piston 535 move away cylinder 518, this will trend towards discharging fluid from the first Room 554a, as mentioned above.Thereby, trend towards making actuator 512 to move to the further motion of expanded position by check valve apparatus 514 preventions, as mentioned above.
Similarly, if when actuator 512 is positioned at its extended position dead check valve apparatus 514, then stop actuator 512 to move (if additional tension on actuator 512) towards the position that it more extends.As mentioned above, if the pulling force that actuator 512 is added when being in " elongation locking " situation then stops the fluid in the first Room 554a to flow out first port 554, this is because check valve apparatus 514 blocks this flowing.Thereby bar 520 can not move towards the more position of elongation of actuator 512 from the extended position with respect to cylinder 518 that exists when check valve apparatus 514 is closed.
Yet when actuator 512 was in the position of elongation and is subjected to trending towards the power of compressive activation device 512, actuator 512 freely moved towards its center position.When bar 520 and piston 535 move by these compressive forces, the increase in volume of the first Room 554a, thus reduced the pressure of this volume inner fluid.Reach center position (perhaps encouraging check valve apparatus 514 again) up to actuator 512, fluid freely flows out the first Room 554a, via first port 554 and check valve apparatus 514, and enters holder 578 via second hydraulic power line 558.Yet, in case bar 520 moves to center position, bar 520 is no longer advanced with piston 535, therefore as mentioned above, stoped by check valve apparatus 514 and to have made actuator 512 move to the further motion of compression position, this is because the further compression movement of bar 520 needs fluid to flow out the first Room 554a via port 556, and by unperturbed check valve apparatus 514.
Referring now to accompanying drawing 9, shown is according to the 6th embodiment by 610 roll control systems of indicating of the present invention, general.Roll control system 610 generally is similar to the roll control system of above-mentioned embodiment.Those are different from the element of the described element of above-mentioned roll control system only to describe roll control system 610.Single actuator 612 of the present invention is described.Yet, should be appreciated that as mentioned above, also for vehicle provides second actuator and corresponding hydraulic circuit, so that provide roll control system in the front and back of vehicle.Can be on vehicle, to use roll control system 610 with the similar mode of above-mentioned first embodiment.
Actuator 612 has integrated holder 678, and this holder partly is filled with oil, and residual volume is filled with gas.Integrated check valve apparatus 614 provides with the form of cartridge type valve 614b and boiler check valve 614a, although this not necessarily.Check valve apparatus 614 and operation similarly as described in the embodiment early.Boiler check valve 614a opens so that allow fluid between the inside of cylinder 618 and integrated holder 678, to move, thereby make bar 620 and piston 635 get back to when dead check valve apparatus 614 shown in center position.
Actuator 612 comprises cylinder 618.Cylinder 618 has the first end wall 618a, the second end wall 618b, and the cylindrical wall 618c that extends between the first end wall 618a and the second end wall 618b.Cylindrical wall 618c has the inside face of limiting hole 613.Pass the first end wall 618a and form axially open 622.The second end wall 618b preferably is suitable for being connected to vehicle and props up on the partial sum on the spring does not prop up in the part on spring one.
Cylinder 618 has first radial port 654.The cylindrical wall 618c that first port 654 passes the contiguous first end wall 618a radially forms.Cylinder 618 has second radial port 652.The cylindrical wall 618c that second port 652 passes the contiguous first end wall 618a radially forms.Further describe the purpose of port 652 and 654 below.
Cylinder 618 has the first groove 626a, forms on the inside face of the axially open 622 of this first groove in contiguous cylinder 618 exterior end wall 618a, so that receive first sealing member 626.Cylinder 618 has the second groove 643a, forms on the inside face of the axially open 622 of this second groove in contiguous cylinder 618 in-to-in end wall 618a, so that receive second sealing member 643.
Cup piston 635 is arranged in the cylinder 618.This piston has the first terminal 635a and the second terminal 635b.The first terminal 635a of piston 635 is the ends that open wide, and towards the first terminal 618a of cylinder 618.The second terminal 635b of piston 635 is the ends of closing, and towards the second terminal 618b of cylinder 618.Piston 635 comprises the annular lip 637 near the first terminal 635a.Flange 637 extends radially inwardly.Will discuss the purpose of flange 637 below.Piston 635 engages with cylindrical wall 618c hermetically.
Bar 620 extends into the inside of cylinder 618 by the axially open in the cylinder 618 622, and extends through the first terminal 635a that opens wide of piston 635.Bar 620 is installed on the cylinder 618, so as with its crank motion.The sealing member 626 that is arranged in the axially open 622 provides fluid not saturating slipper seal between bar 620 and cylinder 618.Notice, be different from the bar 120 of first embodiment, bar 620 does not extend by second opening in the cylinder 618; Therefore need some differences (discussing below) in the operation.
On the end in bar 620 is arranged in piston 635, bar 620 comprises the flange 621 of circumferential extension, and this flange extends outwardly into the inside of piston 635.The annular lip 637 of piston 635 is cooperated to keep flange 621 and bar 620 in piston 635 with the flange of bar 620 621.
Second sealing member 643, flange 621, bar 620 and cylinder 618 cooperations are to limit the 654a of fluid chamber of first variable-volume in cylinder 618.First fluid chamber 654a is communicated with first port, 654 fluids.Be different from the 3rd, the 4th and the 5th embodiment, first fluid chamber 654a not with the internal fluid communication of piston 635, this is because flange 621 forms the not saturating sealing of fluid between bar 620 and piston 635.Piston 635, boiler check valve 614a, cylindrical wall 618c and second end wall 618b cooperation are to limit the 652a of fluid chamber of second variable-volume in cylinder 618.Second 652a of fluid chamber is communicated with holder port 678a fluid, will describe its purpose below.
Roll control system 610 comprises integrated holder 678.Holder 678 comprises the first port 678a.This holder comprises the second port 678b.Should be appreciated that any holder that is suitable for using described here, and any holder in this expression or description can use in arbitrary embodiment of the present invention.
First port 654 of cylinder 618 is communicated with hydraulic power line 660 fluids.Hydraulic power line 660 is communicated with second port, 652 fluids.Second port 652 of cylinder 618 optionally is communicated with the second port 678b of holder 678 via cartridge type valve 614b.The inside of piston 635 optionally is communicated with the first port 678a of holder 678 via boiler check valve 614a.
Though shown hydraulic circuit 660 is positioned at the outside of cylinder 618, yet, should be appreciated that hydraulic power line 660 also can be positioned at the inside of cylinder 618.For example, hydraulic power line 660 can form in cylindrical wall 618c.
Shown check valve apparatus 614 is positioned at unperturbed " non-return " position of each valve 614a and 614b, thereby only allows to flow from the in-to-in of holder 678 to first Room 654a and piston 635.When excitation valve 614a and 614b, described check valve apparatus 614 is known as and is in position excitation, that circulate or open, wherein fluid not only can flow into the inside of the first Room 654a and piston 635 from check valve apparatus 614, but also can flow out the inside of the first Room 654a and piston 635, flow into holders 678 by check valve apparatus 614.Check valve apparatus 614 is carried out the function roughly the same with check valve apparatus 114.
By holder 678 fluid in fluid among the first Room 654a and piston 635 inside is remained under certain pressure.The masterpiece of pressure among the 654a of chamber and spring 649 is used for piston 635, so that push piston 635 to second end wall 618b.The effect of pressure is pushed flange 621 to first end wall 618a in the piston 635.During operation, as described below, actuator 612 can be subjected to enough pulling force, because the power of this differential pressure generating, and bar 620 can leave the second end wall 618b with piston 635 pullings, perhaps flange 621 promoted to leave the first end wall 618a to overcome.
As shown in Figure 9, bar 620 and piston 635 are in the center position with respect to cylinder 618.When excitation during check valve apparatus 614, bar 620 and piston 635 can be as required crank motion in cylinder 618 freely.When piston 635 when the first end wall 618a of cylinder 618 moves, bar 620 and piston 635 enter the sport of compression position and discharge fluid from the first Room 654a.When bar 620 moved to the inside of piston 635 more, bar 620 and piston 635 entered the sport of compression position and discharge fluid from the inside of piston 635.With the fluid storage of discharging in holder 678.On the contrary, in actuator 612 elongations, and when bar 620 less is arranged in the inside of piston 635, to pass through the inside of check valve apparatus 614 suction pistons 635 from the fluid of holder 678, up to the center position of bar 620 shown in moving to, and the flange 637 of flange 621 contact pistons 635, and begin to make piston 635 to move away the second end wall 618b.In case this generation, fluid will be transferred to (diameter of piston 635 is greater than the diameter of the bar of recalling from chamber 654a 620) the holder 678 from the first Room 654a.
When dead check valve apparatus 614, for example, roll control system 610 in use, fluid impassabitity first port 654 leaves the first Room 654a, and fluid can not leave the inside of piston 635 via boiler check valve 614a, thereby bar 620 and piston 635 be with respect to cylinder 618 lockings, so that bar 620 can not further extend in the piston 635.By the same token, piston 635 can not be moved down among the first Room 654a.Yet, if the fluid pressure in the holder 678 greater than in the first Room 654a or piston 635 in-to-in fluid pressures (generally be like this, except prop up at vehicle on the spring and do not prop up producing between the part on the spring the momentary duty), fluid can enter the inside of the first Room 654a and piston 635 from holder 678.Thereby, if any one is not in center position in bar 620 and the piston 635 when dead check valve apparatus 614, then allow bar 620 and piston 635 to get back to center position.
The operation of describing with respect to second embodiment above being similar to is because the variable part of bar 620 can extend in the cylinder 618, so the volume change that is occupied by bar 620 in the cylinder 618.Therefore, holder 678 not only must compensate because the variation of the fluid pressure that the fluid loss of revealing from system 610 causes, and must compensate the potential variation of system's 610 inner volumes that shutdown system that a part owing to bar 620 moved into and left the cylinder 618 of system 610 causes.The volume of gas allows system's 610 this pressure of compensation and/or volume change in the holder 678.
As mentioned above, if the pressure in the holder 678 is higher than in the first Room 654a or piston 635 pressure inside, then can flow into the inside of the first Room 654a or piston 635 by check valve apparatus 614, even during dead check valve apparatus 614 from the fluid of holder 678.
When 610 vehicles thereon of system were advanced, the actuator 612 of roll control system 610 was subjected to trending towards the power of compressive activation device 612 once in a while, and is subjected to trending towards the power of extension actuator 612.By the check valve apparatus 614 of excitation, fluid freely flows on either direction by check valve apparatus 614, thereby can freely flow into and flow out the inside of the first Room 645a and piston 635.This means that actuator 612 relatively freely extends and is compressed, travel to provide more stably thereby allow the suspension of vehicle to absorb these power.This is normally along the situation of the road straight-line travelling of relatively flat.Yet, when having the condition of wishing raising inclination control, can not encourage check valve apparatus 614.
If dead check valve apparatus 614 when actuator 612 is in its center position (in as accompanying drawing 9 expression) then hydraulically is locked in bar 620 and cylinder 618 position relative to each other, and can not leaves center position.If actuator 612 is compressed power during this situation that " is locked in neutrality ", then stop the fluid in the first Room 654a to flow out first port 654, and stop piston 635 in-to-in fluids to flow out boiler check valve 614a, this is because check valve apparatus 614 blocks this flowing.Piston 635 has been resisted against on the second end wall 618b of cylinder 618.Thereby bar 620 can not move from the center position with respect to cylinder 618, to allow actuator 612 compressions.Similarly, if during this situation that " is locked in neutrality ", actuator 612 is subjected to trending towards the power of extension actuator 612, then stop the fluid in the first Room 654a to flow out first port 654, and stop piston 635 in-to-in fluids to flow out boiler check valve 614a, this is because check valve apparatus 614 blocks this flowing.Thereby bar 620 can not move from the center position with respect to cylinder 618, to allow actuator 612 elongations.
If dead check valve apparatus 614 when actuator 612 is in its compression position then will stop actuator 612 to move (if additional compression force is on actuator 612) towards the position that it more compresses.As situation about discussing in the paragraph in front, if the compressive force that actuator 612 is added when being in the situation of this " compression locking ", then stop the fluid in the first Room 654a to flow out first port 654, and stop piston 635 in-to-in fluids to flow out boiler check valve 614a, this is because check valve apparatus 614 blocks this flowing.Thereby bar 620 can not move towards the position that actuator 612 more compresses from the compression position with respect to cylinder 618 that exists when check valve apparatus 614 is closed.
Yet when actuator 612 was in this compression position and is subjected to trending towards the power of extension actuator 612, actuator 612 freely moved towards its center position.When bar 620 moves by these extending forces, piston 635 in-to-in increase in volumees, thus reduced the pressure of this volume inner fluid.Reach center position (perhaps encouraging check valve apparatus 614 again) up to actuator 612, fluid freely flows into the inside of piston 635 from holder 678 via the boiler check valve 614a of check valve apparatus 614, so that fill the inside of the expansion of piston 635.Yet in case bar 620 moves to center position, further moving will make piston 635 move away the second end wall 618b, and this trends towards discharging fluid from the first Room 654a, as mentioned above.Thereby, trend towards making actuator 612 to move to the further motion of expanded position by check valve apparatus 614 preventions, as mentioned above.
Similarly, if when actuator 612 is positioned at its extended position dead check valve apparatus 614, then stop actuator 612 to move (if additional tension on actuator 612) towards the position that it more extends.As mentioned above, if the pulling force that actuator 612 is added when being in " elongation locking " state, then stop the fluid in the first Room 654a to flow out first port 654, and stop piston 635 in-to-in fluids to flow out boiler check valve 614a, this is because check valve apparatus 614 blocks this flowing.Thereby bar 620 can not move towards the position that actuator 612 more extends from the extended position with respect to cylinder 618 that exists when check valve apparatus 614 is closed.
Yet when actuator 612 was in the position of elongation and is subjected to trending towards the power of compressive activation device 612, actuator 612 freely moved towards its center position.When bar 620 and piston 635 move by these compressive forces, the increase in volume of the first Room 654a, thus reduced the pressure of this volume inner fluid.Reach center position (perhaps encouraging check valve apparatus 614 again) up to actuator 612, fluid flows into the first Room 654a from holder 678 via first port 654 and check valve apparatus 614.Yet, when bar 620 moves, bar 620 will can further not advanced in piston 635, as mentioned above, therefore, stoped by check valve apparatus 614 to make actuator move to the further motion of compression position, as mentioned above, this is because the further compression movement of bar 620 needs fluid to flow out the inside of piston 635 via the boiler check valve 614a of unperturbed check valve apparatus 614.
Should be appreciated that corresponding piston is being connected in the suspension of vehicle drivingly, and when corresponding cylinder being connected on the antiroll bar of vehicle, the 3rd, the 4th, the 5th and the 6th embodiment is preferably operated.
Operating principle of the present invention and operation mode in preferred implementation of the present invention, have been explained and have illustrated.Yet, should be appreciated that except special explanation and explanation, can under the situation that does not break away from its spirit or scope, put into practice the present invention.

Claims (26)

1. hydraulically operated actuator that is used for the inclination of controlling machine motor vehicle, described actuator is connected vehicle and does not prop up at the partial sum vehicle on the spring and prop up between the part on the spring, be connected to vehicle in the part on the spring and do not prop up part on spring so that optionally vehicle is propped up, described actuator comprises:
Being suitable for being fixed to vehicle props up at the partial sum vehicle on the spring and does not prop up bar in the part on spring one;
The flange that on described bar, forms;
Being suitable for being fixed to vehicle props up at the partial sum vehicle on the spring and does not prop up cylinder in the part on spring another, wherein said cylinder has the inside face and at least the first and second ports of limiting hole, in the described hole of the described cylinder of wherein said flange arrangement between described first and second ports, and wherein said cylinder comprise with described first and second ports between at least one sealing member of engaging of the described inside face of described cylinder, wherein in described first and second ports at least one is connected to fluid conduit systems, described fluid conduit systems is with the outside that is arranged in described hole and pass wherein a kind of mode that described piston is defined and be provided with; And
A certain amount of hydraulic fluid, it is arranged in the described hole of described cylinder, so that when stoping described hydraulic fluid to flow out described first port and described second port, described flange only can move on the direction of the center position in described cylinder.
2. actuator as claimed in claim 1 is characterized in that, described cylinder is fixed to vehicle and does not prop up part on spring.
3. actuator as claimed in claim 1, it is characterized in that, described actuator further comprises check valve apparatus, when described check valve apparatus was in the position of opening, described check valve apparatus was suitable for allowing via at least one the bi-directional fluid flow in described first port and described second port.
4. actuator as claimed in claim 3 is characterized in that described check valve apparatus comprises screw actuator.
5. actuator as claimed in claim 4 is characterized in that described screw actuator is configured to, and when the described screw actuator of excitation, described check valve apparatus moves to the position of closing from the position of opening.
6. actuator as claimed in claim 4 is characterized in that described screw actuator is configured to, and when the described screw actuator of excitation, described check valve apparatus moves to the position of opening from the position of closing.
7. actuator as claimed in claim 1 is characterized in that described center position is the center.
8. half activity system that is used for the inclination of controlling machine motor vehicle, described system comprises:
Do not prop up at the partial sum vehicle on the spring at vehicle and to prop up bonded assembly hydraulically operated actuator between the part on the spring, described actuator comprises that being fixed to vehicle props up at the partial sum vehicle on the spring and do not prop up cylinder in the part on spring one, described actuator comprises that being fixed to vehicle props up at the partial sum vehicle on the spring and do not prop up bar in the part on spring another, the flange that on described bar, forms, wherein said cylinder has at least the first and second ports, and described flange arrangement is in described cylinder, between described first and second ports;
Be suitable for storing the holder of a certain amount of hydraulic fluid, described holder is communicated with at least one fluid in described first and second ports; And
Check valve apparatus with open position and non-return position, in first and second ports of described check valve apparatus and described holder and described cylinder at least one is communicated with, so that modulated pressure fluid flowing between described first port of described actuator and in described second port at least one, so that when described check valve apparatus is in the non-return position, described boiler check valve limits flowing between in described first port and second port at least one, and described flange only can move on the direction of the center position in described cylinder.
9. system as claimed in claim 8 is characterized in that, described cylinder is fixed to vehicle and does not prop up part on spring.
10. system as claimed in claim 8 is characterized in that, when described check valve apparatus was in the position of opening, described check valve apparatus allowed the bi-directional fluid flow between in described first port and described second port at least one.
11. system as claimed in claim 10 is characterized in that, described check valve apparatus comprises screw actuator.
12. system as claimed in claim 11 is characterized in that, described screw actuator with the effect that applies the proportional power of electric signal thereon under towards one of described open position and non-return position the excitation described check valve apparatus.
13. system as claimed in claim 8 further comprises:
Second holder;
Be connected vehicle and do not prop up at the partial sum vehicle on the spring and prop up bonded assembly second actuator between the part on the spring, described second actuator has first and second ports; And
With second check valve apparatus that described second holder is communicated with, at least one in described first and second ports of wherein said second actuator is communicated with via the described second check valve apparatus fluid.
14. system as claimed in claim 8, it is characterized in that, described system further comprises spring element, and described spring element is fixed to vehicle and props up part on spring, wherein said cylinder and be fixed to that vehicle props up in the described bar of the part on spring and be fixed to described spring element.
15. system as claimed in claim 12 is characterized in that, described spring element is a roll bar.
16. hydraulically operated actuator that is used for the inclination of controlling machine motor vehicle, wherein said actuator is connected vehicle and does not prop up at the partial sum vehicle on the spring and prop up between the part on the spring, be connected to vehicle in the part on the spring and do not prop up part on spring so that optionally vehicle is propped up, described actuator comprises:
Being suitable for being fixed to vehicle props up at the partial sum vehicle on the spring and does not prop up cylinder in the part on spring one, wherein said cylinder has first end wall, second end wall and cylindrical wall, described cylindrical wall forms between described first end wall and described second end wall, and wherein said cylinder has the annular lip that forms on the inside of the described cylindrical wall between described first end wall and described second end wall, and wherein said cylinder has first port, and described first port is to pass described first end wall and to form in wherein a kind of mode of passing in the described cylindrical wall near the described first end wall place; Second port, described second port pass described flange and form; And the 3rd port, described the 3rd port is to pass described second end wall and to form in wherein a kind of mode of passing in the described cylindrical wall near the described second end wall place;
Be arranged in the described flange of described cylinder and the in-to-in first piston of the described cylinder between described first end wall, described first piston engages the inside face of described cylinder hermetically;
Be arranged in second piston in the inside of the described flange of described cylinder and the described cylinder between described second end wall, the described second piston packing ground engages the inside face of described cylinder;
Be suitable for being fixed to vehicle and prop up at the partial sum vehicle on the spring and do not prop up bar in the part on spring another, wherein on described bar, form flange, and the described flange arrangement of wherein said bar is between described first piston and described second piston; And
A certain amount of hydraulic fluid, it is arranged in the inside of described cylinder, so that stop described hydraulic fluid from the inside of described cylinder by described first port and from the inside of described cylinder during by described the 3rd port mobile, the described flange of described bar only can move on the direction of the center position in described cylinder.
17. actuator as claimed in claim 16 is characterized in that, the described flange of described bar is an annular lip.
18. actuator as claimed in claim 16 is characterized in that, the described flange of described bar is a circumferential flange.
19. hydraulically operated actuator that is used for the inclination of controlling machine motor vehicle, wherein said actuator is connected vehicle and does not prop up at the partial sum vehicle on the spring and prop up between the part on the spring, be connected to vehicle in the part on the spring and do not prop up part on spring so that optionally vehicle is propped up, described actuator comprises:
Being suitable for being fixed to vehicle props up at the partial sum vehicle on the spring and does not prop up cylinder in the part on spring one, wherein said cylinder has first end wall, second end wall and cylindrical wall, between described first end wall and described second end wall, form described cylindrical wall, and wherein said cylinder has first port, and described first port is to pass described first end wall and to form in wherein a kind of mode of passing in the described cylindrical wall near the described first end wall place;
Be arranged in the cup piston in the inside of the described cylinder between described first end wall and described second end wall, described piston has first end and second end of closing that opens wide, wherein said unlimited terminal surface is to described first end wall, described terminal surface of closing is to described second end wall, and described piston has the flange that forms on described unlimited end, and described piston packing ground engages the inside face of described cylinder;
Being suitable for being fixed to vehicle props up at the partial sum vehicle on the spring and does not prop up bar in the part on spring another, on described bar, form flange, and the described flange of wherein said bar is arranged in the described piston between described unlimited terminal and described end of closing, and the described flange cooperation of the described flange of wherein said piston and described bar keeps the flange of described bar with the inside at described piston; And
A certain amount of hydraulic fluid, it is arranged in the inside of described cylinder, so that when stoping described hydraulic fluid from the inside of described cylinder during by described first port mobile, the described flange of described bar only can move on the direction of the center position in described cylinder.
20. actuator as claimed in claim 19 is characterized in that, described cylinder further comprises second port, and described second port is to pass described second end wall and to form in wherein a kind of mode of passing in the described cylindrical wall near the described second end wall place.
21. actuator as claimed in claim 20 is characterized in that, described second port is the vent window to atmosphere.
22. actuator as claimed in claim 19, it is characterized in that, the flange seal ground of described bar engages the inside of described piston, wherein said actuator further comprises check valve apparatus, described check valve apparatus is included in first valve that forms in the described cylinder, described first valve is communicated with the described first port fluid, and described first valve can be operated, optionally to stop inside flowing by described first port from described cylinder, and described check valve apparatus is included in second valve that forms in the described end of closing of described piston, the internal fluid communication of described second valve and described piston, and described second valve can be operated, and flows optionally to stop from the in-to-in of described piston.
23. hydraulically operated actuator that is used for the inclination of controlling machine motor vehicle, wherein said actuator is connected vehicle and does not prop up at the partial sum vehicle on the spring and prop up between the part on the spring, be connected in vehicle in the part on the spring and do not prop up part on spring so that optionally vehicle is propped up, described actuator comprises:
Being suitable for being fixed to vehicle props up at the partial sum vehicle on the spring and does not prop up cylinder in the part on spring one, wherein said cylinder has first end wall, second end wall and cylindrical wall, described cylindrical wall forms between described first end wall and described second end wall, and wherein said cylinder has the annular lip of the inside formation of the described cylindrical wall between described first end wall and second end wall, and wherein said cylinder has first port, and described first port is to pass described first end wall and to form in wherein a kind of mode of passing in the described cylindrical wall near the described first end wall place; Second port, described second port forms in wherein a kind of mode of passing described flange and pass in the described cylindrical wall near described flange place between described flange and described second end wall;
Be arranged in the cup piston in the inside of the described cylinder between described first end wall and the described flange, described piston has first end and second end of closing that opens wide, wherein said unlimited terminal surface is to described first end wall, and described terminal surface of closing is to described second end wall, and described piston has the flange that forms on described unlimited end, and described piston packing ground engages the inside face of described cylinder;
Being suitable for being fixed to vehicle props up at the partial sum vehicle on the spring and does not prop up bar in the part on spring another, wherein on described bar, form flange, and the described flange of wherein said bar is arranged in the described piston between described unlimited terminal and described end of closing, and the described flange cooperation of the described flange of wherein said piston and described bar keeps the flange of described bar with the inside at described piston; And
A certain amount of hydraulic fluid, it is arranged in the inside of described cylinder, so that when stoping described hydraulic fluid from the inside of described cylinder during by described first port mobile, the described flange of described bar only can move on the direction of the center position in described cylinder.
24. actuator as claimed in claim 22, it is characterized in that, described holder further comprises check valve apparatus, described check valve apparatus is communicated with described first port and the described second port fluid, and is suitable for optionally stoping the inside from described cylinder mobile by the fluid of described first port.
25. half activity system of controlling machine motor vehicle inclination, described system comprises:
Be connected to the spring element that vehicle props up the part on spring;
Be connected vehicle and do not prop up hydraulically operated actuator between the described spring element of the partial sum on the spring, described actuator comprises that being fixed to described spring element and vehicle does not prop up cylinder in the part on spring one, described actuator comprises that being fixed to described spring element and vehicle does not prop up bar in the part on spring another, the flange that on described bar, forms, wherein said cylinder has at least the first and second ports, and described flange is arranged in the described cylinder between described first port and second port;
Be suitable for storing the holder of a certain amount of hydraulic fluid, described holder is communicated with at least one fluid in described first and second ports; And
Check valve apparatus with open position and non-return position, in described first and second ports of described check valve apparatus and described holder and described cylinder at least one is communicated with, so that modulated pressure fluid flowing between described first port of described actuator and in described second port at least one, so that when described check valve apparatus is in the non-return position, described boiler check valve limits flowing between in described first port and second port at least one, and described flange only can move on the direction of the center position in described cylinder.
26. system as claimed in claim 25 is characterized in that, described spring element is a roll bar.
CNA2005800501201A 2005-05-04 2005-05-04 Vehicle roll control system with self-centering actuator Pending CN101443204A (en)

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Cited By (2)

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Publication number Priority date Publication date Assignee Title
CN111059096A (en) * 2019-11-28 2020-04-24 同济大学 Hydraulic centering locking actuating cylinder structure
US20230080108A1 (en) * 2020-02-07 2023-03-16 Timoney Dynamic Solutions Limited Motor Vehicle Suspension Gas Spring

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US20070278028A1 (en) 2006-06-05 2007-12-06 Wayne Robert Fought Anti-aeration system for a suspension actuator
DE102009023419A1 (en) * 2009-05-29 2010-12-02 Trw Automotive Gmbh Semi-active hydraulic chassis system for use in semi active hydraulic chassis stabilization system for vehicle, has reverse function realized in one hydraulic connection, and pressure relief valve provided in other hydraulic connection
DE102009032211A1 (en) * 2009-07-03 2011-01-05 Dr. Ing. H.C. F. Porsche Aktiengesellschaft Damper for hydraulic swing motor for stabilizer of chassis of two-track motor vehicle, has compensation devices coupled with hydraulic aggregate to cause pressure balance, and mounting device fixed in housing of hydraulic aggregate
GB201500553D0 (en) * 2015-01-14 2015-02-25 Bae Systems Plc Hydraulic Actuators

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US5630623A (en) * 1994-08-15 1997-05-20 Kelsey Hayes Vehicle roll control system
US6296235B1 (en) * 1999-10-15 2001-10-02 Adwait R. Dalal Automobile stabilization assembly

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN111059096A (en) * 2019-11-28 2020-04-24 同济大学 Hydraulic centering locking actuating cylinder structure
US20230080108A1 (en) * 2020-02-07 2023-03-16 Timoney Dynamic Solutions Limited Motor Vehicle Suspension Gas Spring

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