CN108778789A - The hydraulic suspension system of vehicle - Google Patents
The hydraulic suspension system of vehicle Download PDFInfo
- Publication number
- CN108778789A CN108778789A CN201780019608.0A CN201780019608A CN108778789A CN 108778789 A CN108778789 A CN 108778789A CN 201780019608 A CN201780019608 A CN 201780019608A CN 108778789 A CN108778789 A CN 108778789A
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- China
- Prior art keywords
- buffer
- vehicle
- piston
- stop part
- cylinder body
- Prior art date
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- Pending
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Classifications
-
- B—PERFORMING OPERATIONS; TRANSPORTING
- B60—VEHICLES IN GENERAL
- B60G—VEHICLE SUSPENSION ARRANGEMENTS
- B60G17/00—Resilient suspensions having means for adjusting the spring or vibration-damper characteristics, for regulating the distance between a supporting surface and a sprung part of vehicle or for locking suspension during use to meet varying vehicular or surface conditions, e.g. due to speed or load
- B60G17/02—Spring characteristics, e.g. mechanical springs and mechanical adjusting means
- B60G17/021—Spring characteristics, e.g. mechanical springs and mechanical adjusting means the mechanical spring being a coil spring
-
- B—PERFORMING OPERATIONS; TRANSPORTING
- B60—VEHICLES IN GENERAL
- B60G—VEHICLE SUSPENSION ARRANGEMENTS
- B60G11/00—Resilient suspensions characterised by arrangement, location or kind of springs
- B60G11/32—Resilient suspensions characterised by arrangement, location or kind of springs having springs of different kinds
- B60G11/48—Resilient suspensions characterised by arrangement, location or kind of springs having springs of different kinds not including leaf springs
- B60G11/52—Resilient suspensions characterised by arrangement, location or kind of springs having springs of different kinds not including leaf springs having helical, spiral or coil springs, and also rubber springs
- B60G11/54—Resilient suspensions characterised by arrangement, location or kind of springs having springs of different kinds not including leaf springs having helical, spiral or coil springs, and also rubber springs with rubber springs arranged within helical, spiral or coil springs
-
- B—PERFORMING OPERATIONS; TRANSPORTING
- B60—VEHICLES IN GENERAL
- B60G—VEHICLE SUSPENSION ARRANGEMENTS
- B60G15/00—Resilient suspensions characterised by arrangement, location or type of combined spring and vibration damper, e.g. telescopic type
- B60G15/02—Resilient suspensions characterised by arrangement, location or type of combined spring and vibration damper, e.g. telescopic type having mechanical spring
- B60G15/06—Resilient suspensions characterised by arrangement, location or type of combined spring and vibration damper, e.g. telescopic type having mechanical spring and fluid damper
- B60G15/062—Resilient suspensions characterised by arrangement, location or type of combined spring and vibration damper, e.g. telescopic type having mechanical spring and fluid damper the spring being arranged around the damper
- B60G15/066—Resilient suspensions characterised by arrangement, location or type of combined spring and vibration damper, e.g. telescopic type having mechanical spring and fluid damper the spring being arranged around the damper the spring being different from a coil spring
-
- 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
- B60G17/06—Characteristics of dampers, e.g. mechanical dampers
- B60G17/08—Characteristics of fluid dampers
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16F—SPRINGS; SHOCK-ABSORBERS; MEANS FOR DAMPING VIBRATION
- F16F9/00—Springs, vibration-dampers, shock-absorbers, or similarly-constructed movement-dampers using a fluid or the equivalent as damping medium
- F16F9/32—Details
- F16F9/48—Arrangements for providing different damping effects at different parts of the stroke
- F16F9/49—Stops limiting fluid passage, e.g. hydraulic stops or elastomeric elements inside the cylinder which contribute to changes in fluid damping
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16F—SPRINGS; SHOCK-ABSORBERS; MEANS FOR DAMPING VIBRATION
- F16F9/00—Springs, vibration-dampers, shock-absorbers, or similarly-constructed movement-dampers using a fluid or the equivalent as damping medium
- F16F9/32—Details
- F16F9/58—Stroke limiting stops, e.g. arranged on the piston rod outside the cylinder
-
- 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
- B60G2202/12—Wound spring
-
- B—PERFORMING OPERATIONS; TRANSPORTING
- B60—VEHICLES IN GENERAL
- B60G—VEHICLE SUSPENSION ARRANGEMENTS
- B60G2202/00—Indexing codes relating to the type of spring, damper or actuator
- B60G2202/10—Type of spring
- B60G2202/14—Plastic spring, e.g. rubber
- B60G2202/143—Plastic spring, e.g. rubber subjected to compression
-
- B—PERFORMING OPERATIONS; TRANSPORTING
- B60—VEHICLES IN GENERAL
- B60G—VEHICLE SUSPENSION ARRANGEMENTS
- B60G2206/00—Indexing codes related to the manufacturing of suspensions: constructional features, the materials used, procedures or tools
- B60G2206/01—Constructional features of suspension elements, e.g. arms, dampers, springs
- B60G2206/40—Constructional features of dampers and/or springs
- B60G2206/41—Dampers
-
- B—PERFORMING OPERATIONS; TRANSPORTING
- B60—VEHICLES IN GENERAL
- B60G—VEHICLE SUSPENSION ARRANGEMENTS
- B60G2500/00—Indexing codes relating to the regulated action or device
- B60G2500/10—Damping action or damper
-
- B—PERFORMING OPERATIONS; TRANSPORTING
- B60—VEHICLES IN GENERAL
- B60G—VEHICLE SUSPENSION ARRANGEMENTS
- B60G2500/00—Indexing codes relating to the regulated action or device
- B60G2500/10—Damping action or damper
- B60G2500/11—Damping valves
-
- B—PERFORMING OPERATIONS; TRANSPORTING
- B60—VEHICLES IN GENERAL
- B60G—VEHICLE SUSPENSION ARRANGEMENTS
- B60G2500/00—Indexing codes relating to the regulated action or device
- B60G2500/20—Spring action or springs
- B60G2500/22—Spring constant
Landscapes
- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Vehicle Body Suspensions (AREA)
- Fluid-Damping Devices (AREA)
Abstract
The present invention relates to a kind of vehicle, especially motor vehicles hydraulic suspension systems.The hydraulic suspension system includes：Hydraulic pressure attacks stop part (9b), and the piston and cylinder body of the hydraulic pressure attack stop part are used to be moved relative to each other by means of the piston of the buffer (1) when reaching the first attack stroke in cylinder body of the piston of buffer in the buffer；Machinery attack stop part (7b), the machinery attack stop part are used to compress between the cylinder body and the vehicle body of the vehicle of the buffer when reaching the second attack stroke (CA2) more than first stroke (CA1) in cylinder body of the piston of the buffer in the buffer；And bearing spring, the rigidity of the bearing spring make the resonant frequency of the vehicle body of the vehicle between 1Hz and 1.1Hz.The present invention is suitable for motor vehicle industry field.
Description
Technical field
The present invention relates to a kind of vehicle, especially motor vehicles hydraulic suspension systems.
Background technology
It is known per se, for each of the wheel of vehicle, the hydraulic suspension of the vehicle (especially motor vehicles)
System includes the buffer for having piston, and the piston is movable in corresponding cylinder body and is interposed in vehicle body and the vehicle
Between the axle journal frame (porte-fus é e) of wheel.The effect of the buffer is to encounter in wheel and is present in vehicle and travels
Road on unevenness or when barrier consumingly limit the oscillation being transferred to by wheel on the vehicle body of vehicle.
In order to limit and buffer buffer piston stroke, the buffer include compressible machinery (or optionally
Hydraulic pressure) attack stop part (but é e d'attaque) and optionally decompression stop part (but é e de d é tente).These backstops
The effect of part also reside in corresponding wheel due to accident or due to larger barrier (such as lambdoid deceleration strip or pit-hole) and
Occur protecting the chassis of the vehicle when stroke (d é battements) between larger wheel shaft trip.
Stop part especially is attacked from a kind of hydraulic pressure with piston known to file FR2995048, the piston is corresponding
It is movable in cylinder body, and the piston of hydraulic pressure attack stop part be used for when the piston of the buffer is close to end of travel by
The piston of the buffer moves.
However, since the larger stroke of the piston of the buffer is mainly accidental property, the comfort of the suspension
It is not top-priority for the mechanical integrity for keeping the vehicle.For this reason, the attack stop part and
The decompression stop part is typically very rigid, and generates discontinuous unexpected active force.In these cases, the vehicle
The comfort level of passenger thus can consumingly be damaged.
Invention content
It is an object of the invention to overcome the disadvantages mentioned above of the prior art.
In order to realize the purpose, described the present invention relates to a kind of vehicle, especially motor vehicles hydraulic suspension system
Hydraulic suspension system meets claim 1.
Other feature illustrates in the dependent claims.
The invention further relates to a kind of vehicle, the vehicle especially motor vehicles, and include this hydraulic suspension system.
Description of the drawings
By reading the detailed description being merely given as examples in specification and by reference to showing the prior art
With the attached drawing of two kinds of embodiment of the present invention, it is better understood with the present invention, other purposes, feature, details and advantage of the invention
It will be apparent from, in the drawing：
- Figure 1A and Figure 1B respectively illustrates the longitudinal sectional view of the buffer of the prior art and shows buffer composition member
The chart that the configuration of part changes with stroke of the piston of the buffer in the cylinder body of the buffer；
- Fig. 2A and Fig. 2 B respectively illustrates the buffer according to a first embodiment of the present invention when vehicle is in reference to stable state
Longitudinal sectional view and buffer corresponding with the position for the piston indicated on Fig. 2A element configuration chart；
It is more than first that-Fig. 3 A and Fig. 3 B, which respectively illustrate stroke of the piston when buffer in the cylinder body of the buffer,
The longitudinal sectional view of buffer according to a first embodiment of the present invention and the position with the piston indicated on Fig. 3 A when attacking stroke
Set the chart of the element configuration of corresponding buffer；
It is more than second that-Fig. 4 A and Fig. 4 B, which respectively illustrate stroke of the piston when buffer in the cylinder body of the buffer,
The longitudinal sectional view of buffer according to a first embodiment of the present invention and the position with the piston indicated on Fig. 4 A when attacking stroke
Set the chart of the element configuration of corresponding buffer；
- Fig. 5 A and Fig. 5 B respectively illustrate the buffer when vehicle is in reference to stable state according to a second embodiment of the present invention
Longitudinal sectional view and buffer corresponding with the position of piston indicated on Fig. 5 A element configuration chart；
It is more than first that-Fig. 6 A and Fig. 6 B, which respectively illustrate stroke of the piston when buffer in the cylinder body of the buffer,
The longitudinal sectional view of buffer when attack stroke according to a second embodiment of the present invention and the position with the piston indicated on Fig. 6 A
Set the chart of the element configuration of corresponding buffer；
It is more than second that-Fig. 7 A and Fig. 7 B, which respectively illustrate stroke of the piston when buffer in the cylinder body of the buffer,
The longitudinal sectional view of buffer when attack stroke according to a second embodiment of the present invention and the position with the piston indicated on Fig. 7 A
Set the chart of the element configuration of corresponding buffer；
It is more than third that-Fig. 8 A and Fig. 8 B, which respectively illustrate stroke of the piston when buffer in the cylinder body of the buffer,
The longitudinal sectional view of buffer when attack stroke according to a second embodiment of the present invention and the position with the piston indicated on Fig. 8 A
Set the chart of the element configuration of corresponding buffer.
Specific implementation mode
With reference to figure 1A, vehicle, especially motor vehicles hydraulic suspension systems will now be described.
For each wheel of the vehicle, the suspension of the vehicle includes hydraulic bjuffer 1, the hydraulic bjuffer packet
Include the ontology 2 of shape of block and movable piston 3 in cylinder body 2.The buffer 1 be interposed in the vehicle body 6 of the vehicle with it is right
Between the axle journal frame for answering wheel.Connect with the first end (the other end of the bar couples with the vehicle body 6 of the vehicle) of bar 14
Integral piston 3 distinguishes bound compression chamber and decompression chamber's two chambers 4,5 in cylinder body 2, as the piston exists
Movement in cylinder body 2, incompressible hydraulic fluid (oil) that cylinder body 2 includes is from 3 liang of sides of piston into described two chambers
Circulation.
The behavior of each hydraulic bjuffer 1 of the hydraulic suspension system of the vehicle can be described according to buffering rule,
In the buffering rule, the speed of stroke between the wheel shaft trip of corresponding wheel is depended on by the active force that buffer 1 applies.In other words
It says, piston 3 more rapidly moves in the cylinder body 2 of buffer, and the effect on the vehicle body 6 of the vehicle is applied to by buffer 1
Power is bigger.
For each wheel of the vehicle, the hydraulic suspension system further includes bearing spring 17, the bearing spring
It is assembled into and surrounds buffer 1, and the end of the bearing spring is resisted against the vehicle of the vehicle by means respectively of ware shape part 18
On body 6 and it is resisted against on the ware shape part 19 being connected with the cylinder body of buffer 2.Bearing spring 17 is stiffener, described
The behavior of stiffener can (according to the rule, the active force being applied on the vehicle body 6 of the vehicle by spring 17 takes by rule
Certainly between the wheel shaft trip of the corresponding wheel amplitude of stroke) it describes.In other words, bearing spring 17 more compresses, and is applied to described
Active force on the vehicle body 6 of vehicle is bigger.Bearing spring 17 can substantially carry described in the vehicle body 6 of the vehicle while permission
Stroke between wheel shaft trip.
For each wheel of the vehicle, the suspension system further includes that machinery attack stop part 7 and hydraulic pressure attack stop
15 two decompression stop parts of 9 two attack stop parts of block piece and machinery decompression stop part 16 and hydraulic pressure relief stop part.
Each Mechanical stops 7,16 are similar in terms of rigidity (raideur), and are therefore swum according to the wheel shaft of corresponding wheel
Between stroke apply active force on vehicle body 6.In the same manner as bearing spring 17, depressurized respectively by machinery attack stop part 7 and machinery
Stop part 16 is applied to the active force on the vehicle body 6 of the vehicle due to stroke and decompression wheel between the attack wheel shaft trip of corresponding wheel
Stroke is larger between axis trip and bigger.
Each hydraulic pressure attack stop part 9 and hydraulic pressure relief stop part 15 itself are similar to buffer, and therefore according to right
The speed of stroke applies active force on the vehicle body 6 of the vehicle between answering the wheel shaft of wheel to swim.In the same manner as hydraulic bjuffer 1,
Stop part 9 is attacked by hydraulic pressure respectively and hydraulic pressure relief stop part 15 is applied to the active force on the vehicle body 6 of the vehicle due to right
Between answering the wheel shaft of wheel to swim stroke speed is larger and bigger.
With reference to figure 1A, machinery attack stop part 7 is connected with an end of the cylinder body 2 of buffer, and is located in
Between the cylinder body 2 of buffer and the vehicle body 6 of the vehicle.The machinery attack stop part also has the cross section of annular, so as to
It is passed through by the bar 14 of the piston 3 of buffer 1.Therefore, when piston 3 is more than certain attack stroke, machinery attack stop part 7 exists
It is compressed between the end of the cylinder body 2 of buffer 1 and the vehicle body 6 of the vehicle, so that consumingly brake piston 3 is in the cylinder of buffer
Stroke in body 2.
Preferably, machinery attack stop part 7 is made of the elastomeric material with very strong stiffness constant, so that by
Machinery attack stop part 7 is applied to the active force on the vehicle body 6 of the vehicle with stroke between the attack wheel shaft trip of the wheel
Quickly increase.
In the compression chamber 4 for the cylinder body 2 that hydraulic pressure attack stop part 9 is assemblied in buffer 1.Hydraulic pressure attacks stop part 9
Piston 11 and cylinder body 10, the piston are connected with the lower bottom wall 12 of the cylinder body 2 of buffer, and the cylinder body is used for when described slow
By the movement of piston 3 of the buffer 1 and along attack stop part 9 when rushing near the piston arrival attack end of travel of device
Piston 11 moves.The cylinder body 10 of hydraulic pressure stop part 7 forms the compression chamber 20 filled with hydraulic fluid, in the piston 3 of buffer
When the cylinder body 10 of hydraulic pressure attack stop part 9 being made to be moved towards the lower bottom wall 12 of the buffer, the hydraulic fluid can be due to enclosing
The leakage of the piston 11 of stop part 9 is attacked around hydraulic pressure and escapes the chamber 20.Therefore, the buffering near attack end of travel is reached
The piston 3 of device 1 is quickly braked.
Moreover, hydraulic pressure attack stop part 9 includes returning spring 21, the returning spring surrounds the piston of hydraulic pressure stop part 9
11, and the end of the returning spring is resisted against respectively on the lower bottom wall 12 of the cylinder body 2 of buffer and along hydraulic pressure stop part 9
On the end ring edge of the orifice edge of cylinder body 10.As a result, when cylinder body 10 of the piston 3 of buffer 1 far from hydraulic pressure stop part 9
When, returning spring 21 enables the cylinder body 10 of hydraulic pressure attack stop part 9 to return to resting position.
Floating piston (piston flottant) of the hydraulic pressure relief stop part 15 as the bar 14 around buffer 1, makes
It obtains and keeps annular space 23 between bar 14 and the inward flange of floating piston, hydraulic fluid may pass through the annular space circulation.
Hydraulic pressure relief stop part 15 is located in the decompression chamber 5 of the cylinder body 2 of buffer, and is located in the cylinder body 2 of the buffer
Upper end wall 8 and formed valve flange 22 between, the upper end wall is passed through by the bar 14 of the buffer, the flange and institute
The bar 14 for stating buffer is connected.Machinery decompression stop part 16 is the spring for having strong rigidity in itself, described to have strong rigidity
Spring positioning in decompression chamber 5, and the end of the spring with strong rigidity is resisted against respectively on floating piston 15
In the upper end wall 8 of the cylinder body 2 of buffer 1.
When the piston 3 of hydraulic bjuffer 1 is moved near retraction stroke end, forming the flange 22 of valve makes floating live
The upper end wall 8 of plug 15 towards the cylinder body 2 of buffer 1 moves.Thus compressor mechanical decompression simultaneously stops floating piston 15 on the move
Block piece 16.Moreover, the flange 22 for forming valve closes the inner edge for being in floating piston 15 while being contacted with floating piston 15
Space 23 between edge and bar 14, which increase the upper ends for the cylinder body 2 towards buffer 1 of the hydraulic pressure relief stop part
The resistance of the movement of wall 8.Therefore, reach end of travel near hydraulic bjuffer 1 piston 3 by two decompression stop parts 15,
16 quickly brake.
With reference to the chart of figure 1B, attack stop part 7,9 and decompression stop part 15,16 will now be described according to buffer 1
The configuration that stroke of the piston 3 in the cylinder body 2 of buffer 1 carries out.
Vertical scale indicates the piston 3 of buffer when the stroke between the wheel shaft trip of the wheel of the vehicle in buffer 1
Stroke (in millimeters) in cylinder body 2.Horizontal scale is vision scale, and the vision scale is indicated by the every of hydraulic suspension
A element is applied to the active force at wheel position according to stroke of the piston 3 in the cylinder body 2 of corresponding buffer 1.Described
When the suspension of vehicle is only by the active force of the quality application by the vehicle without by other active forces, zero stroke (zero milli
Rice) correspond to position of the piston 3 of buffer 1 in the cylinder body.The vehicle is then at reference to stable state AR.
Negative stroke of the piston 3 of buffer in cylinder body 2 correspond to the wheel attack wheel shaft trip between stroke, that is,
Say, the suspension tend to compression and the vehicle vehicle body 6 tend to relative to reference to stable state AR close to road.On the contrary
Ground, the positive stroke of the piston 3 of buffer 1 in cylinder body 2 correspond to stroke between the decompression wheel shaft trip of the wheel, that is to say, that
The suspension tends to decompression and the vehicle body 6 of the vehicle tends to relative to reference stable state AR far from road.
To put it more simply, in the context of this specification, it is believed that stroke corresponds to piston 3 corresponding between the wheel shaft trip of wheel
Stroke in buffer.Inclined relative to vertical direction in buffer 1, stroke, which is more than, between the wheel shaft trip of wheel corresponds to
Buffer 1 piston 3 stroke.Certainly, the row of stroke and the piston 3 of corresponding buffer 1 between the wheel shaft of the wheel is swum
Journey is proportional.
Think with the piston of buffer 13 based on the attack stroke or decompression with reference to stable state AR between -15mm and 15mm
Stroke is corresponding to row between the wheel shaft trip of faint energy between stroke or decompression wheel shaft are swum between the attack wheel shaft trip of the corresponding wheel of stroke
Journey DLE, stroke indicates the most common excitation encountered on the second best in quality road between the wheel shaft trip of the faint energy.
Think with the piston of buffer 13 based on corresponding with reference to attack strokes of the stable state AR between -15mm and -50mm
Wheel attack wheel shaft trip between stroke or decompression wheel shaft trip between stroke and with the piston 3 of buffer 1 based on reference to stable state
Stroke pair between stroke or decompression wheel shaft trip between the attack wheel shaft trip of the corresponding wheel of retraction strokes of the AR between 15mm and 50mm
It should stroke DME, the same common excitation of stroke expression between the wheel shaft trip of the medium energy between the trip of the wheel shaft of medium energy.?
Slightly these excitations are encountered on the road of degradation (when wheel crosses smaller barrier (such as smaller deceleration strip)).
Finally, it is believed that with the piston 3 of buffer 1 based on being more than the corresponding vehicle of the attack stroke of -50mm with reference to stable state AR
Wheel attack wheel shaft trip between stroke or decompression wheel shaft trip between stroke and with the piston 3 of buffer 1 based on reference to stable state AR it is big
Stroke corresponds to stronger energy between stroke or decompression wheel shaft trip between the attack wheel shaft trip of the corresponding wheel of retraction stroke of 50mm
Wheel shaft trip between stroke DHE, the stronger energy wheel shaft trip between stroke indicate less common excitation.Especially crossed in wheel
These excitations are encountered when the larger barrier of herringbone deceleration belt type or relatively deep pit-hole.
In order to be more convenient in the context of this specification, the attack stroke of the piston 3 of buffer 1 is expressed with absolute value or is subtracted
Press stroke.
With reference to the chart of figure 1B, once the stroke of the piston 3 of buffer 1 is more than the attack stroke of about 10mm, machinery is attacked
Stop part 7 is hit to be compressed.Therefore, machinery attack stop part 7 is quickly intervened to be made from stroke DME between the trip of the wheel shaft of medium energy
The stroke of the piston 3 of dynamic buffer 1.When the attack stroke of the piston 3 of buffer 1 is more than 50mm (in other words, for higher
Stroke DHE between the wheel shaft trip of energy), the piston 3 of hydraulic bjuffer 1 promotes the cylinder body 10 of hydraulic pressure attack stop part 9 around correspondence
Piston 11 move, with the piston 3 of fast braking buffer 1 in the corresponding cylinder body 2 and preferably vehicle body 6 of protection vehicle.
Referring again to the chart of Figure 1B, when the retraction stroke of the piston 3 of buffer 1 is (excellent more than between 50mm and 70mm
Selection of land is 50mm) value when, hydraulic pressure relief stop part floating piston 15 movement and at the same time compression constitute machinery decompression backstop
The spring of part 16, with the rapidly piston 3 of abutment damper 1 in corresponding cylinder body 2.
When buffer 1 is tilted relative to vertical direction, this for attacking stroke and retraction stroke of the piston 3 of buffer 1
A little values are returned in decline certainly.
With reference to figure 2A, Fig. 2 B, Fig. 3 A, Fig. 3 B, Fig. 4 A and Fig. 4 B, according to a first embodiment of the present invention hang will now be described
Frame system.
For each wheel of the vehicle, the suspension system includes buffer 1 and machinery decompression as described above
15 two decompression stop parts of stop part 16 and hydraulic pressure relief stop part.
For each wheel of the vehicle, suspension system according to a first embodiment of the present invention includes more flexible hangs
Frame spring 17b, the stiffness constant of the more flexible bearing spring are less than the stiffness constant of the bearing spring 17 of the prior art,
Same support S for the bearing spring 17 compared with the existing technology in the compartment 6 of vehicle is ensured simultaneously.Therefore, in vehicle
When in reference to stable state AR, the active force applied by more flexible bearing spring 17b does not change.This more flexible hangs
Frame spring 17b can reduce the vertical resonant frequency in the compartment of vehicle.And the bearing spring 17 of the prior art is used, the vehicle of vehicle
The resonant frequency in compartment 6 is between 1.2Hz and 1.4Hz, and for more flexible bearing spring 17b, the compartment of the vehicle
Resonant frequency is between 1Hz and 1.1Hz.Thus this leads to the increased comfort level of Vehicular occupant.
The vertical resonant frequency f in the compartment of vehiclerPass through formulaTo limit, wherein M is by vehicle vehicle
The sprung mass of a quarter of the vehicle of support is taken turns, and K is the rigidity of the bearing spring 17b at corresponding wheel position.
The sprung mass is that the vehicle component above hydraulic suspension (especially includes wheel, axle journal, the axle journal of vehicle
Frame) quality.The sprung mass of a quarter of vehicle at a wheel position is limited by following manner：Vehicle
Once restriction, the sprung mass of the sprung mass at the rear portion of vehicle and the front of vehicle limits center of gravity successively.The front includes
Vehicle sections be in front part of vehicle and between the horizontal direction (by the center of gravity process of vehicle) of lateral direction of car.The vehicle
Therefore rear portion is the part from the rear portion of vehicle to the horizontal direction.
Therefore, it is possible to respectively by by the sprung mass of front part of vehicle and vehicle rear divided by two come calculate front part of vehicle and
The sprung mass of a quarter of vehicle rear.In each a quarter for the sprung mass for knowing vehicle and the compartment of vehicle
6 through it is expected resonant frequency frWhen, then it is based on formula K=M. (2 π fr)2Directly be inferred to bearing spring 17b is being assembled to vehicle
Correspondence wheel on before stiffness constant.
In order to compensate for the reduction for the active force being applied to by bearing spring 17b on the compartment 6 of vehicle, for the vehicle
Each wheel, hydraulic suspension system according to the present invention further include that the machinery shorter than the machinery attack stop part 7 of the prior art is attacked
Stop part 7b and preferably hydraulic pressure attack stop part 9b are hit, the cylinder body 10b of the hydraulic pressure attack stop part has around correspondence
Piston 11b and attack end of travel and retraction stroke end between (such as between 40 and 60mm) mobile range.
The mobile range is more than (being about 30mm's) mobile range of the cylinder body 10 of the hydraulic pressure attack stop part 9 of the prior art.
Moreover, the structure of the cylinder body 10b of hydraulic pressure attack stop part 9b is different, because the wall of cylinder body 10b includes more
A radial through-hole 13, the multiple radial through-hole move relative to each other in the piston 11b and cylinder body 10b of hydraulic pressure attack stop part 9b
Allow the compression chamber 4 of the cylinder body 2 of hydraulic fluid input or output buffer 1 when dynamic.Therefore, when hydraulic pressure attack stop part 9b's
Cylinder body 10b around corresponding piston 11b towards the cylinder body 2 of buffer 1 lower bottom wall 12 move when, more and more through-holes 13 by
The piston 11b that hydraulic pressure attacks stop part 9b is blocked, and therefore this reduces the total cross section of the through-hole 13, so that for cylinder body
The constant movement speed of 10b increases the active force being applied to by hydraulic pressure attack stop part 9b on the vehicle body 6 of vehicle.
Machinery attack stop part 7b and hydraulic pressure attack stop part 9b are opposite according to the configuration of the stroke of the piston 3 of buffer 1
It is also different in the configuration of the prior art.
In fact, when the piston 3 of hydraulic bjuffer 1 is more than the attack stroke of between 0 and 20mm (being preferably 10mm)
When CA1, the cylinder body 10b of the piston driving hydraulic pressure attack stop part 9b of the hydraulic bjuffer is moved around corresponding piston 11b.
For stroke between the wheel shaft trip of faint energy and medium energy, the larger amt of the cylinder body 10b of hydraulic pressure attack stop part 9b is passed through
Through-hole 13 total cross section it is sufficiently large, to be enough to ensure that the soft braking of the piston 3 for buffer 1.For higher-energy
Stroke DHE (wherein, the close attack end of travel of the piston 3 of buffer 1), passes through the cylinder of hydraulic pressure attack stop part 9b between wheel shaft trip
The total cross section of the through-hole 13 of the lesser amt of body 10b reduces, because in cylinder body 10b around the piston of hydraulic pressure attack stop part 9b
When the lower bottom wall 12 of 11b towards the cylinder body 2 of buffer 1 moves more and more through-holes 13 by hydraulic pressure attack stop part 9b piston
11b is blocked：Which ensure that the more unexpected braking of the piston 3 of buffer 1, to protect vehicle body 6 and the chassis of the vehicle.
Moreover, once the piston 3 of buffer 1 is more than the attack between 30 and 50mm (preferably between 40 and 50mm)
Stroke CA2, machinery attack stop part 7b are compressed and participate in reinforcing the braking of the piston 3 of the buffer 1.
The comfort of the suspension is obviously improved by the hydraulic suspension system of first embodiment of the invention.In fact, by institute
The discontinuity (i.e. the occurring source of the non-comfort of Vehicular occupant) of the active force of suspension system application is stated since hydraulic pressure attack stops
Block piece 9b and reduce strongly, the cylinder body 10b of hydraulic pressure attack stop part has extended mobile range, and the hydraulic pressure is attacked
Stop part is hit to work before machinery attack stop part 7b.Moreover, attacking the active force of stop part 9b applications simultaneously by hydraulic pressure
Movement speed and mobile range of the piston 3 in cylinder body 2 depending on buffer 1, the braking adaptation of the piston 3 of the buffer
In the amplitude and speed of stroke of the piston in cylinder body 2, this also has actively impact to the comfort level of passenger.In addition, liquid
Pressure attack stop part 9b dissipation energies are without cumlative energy, this is thus between the trip of the wheel shaft of faint energy and medium energy in stroke
Avoid any progradation again (effet de relance).Finally, for the use of the bearing spring 17b of faint rigidity
The vertical resonant frequency in compartment 6 is reduced, this can improve the comfort level of the suspension of vehicle.Certainly, from the wheel shaft of medium energy
Stroke DME rises between trip, and flexible increase of bearing spring 17b is compensated by additional buffering, and the additional buffering is attacked by hydraulic pressure
Stop part 9b ensures.
With reference to figure 5A, Fig. 5 B, Fig. 6 A, Fig. 6 B, Fig. 7 A, Fig. 7 B, Fig. 8 A and Fig. 8 B, will now be described according to the present invention second
The suspension system of embodiment.
Element has and the identical attached drawing mark on Fig. 2A, Fig. 2 B, Fig. 3 A, Fig. 3 B, Fig. 4 A and Fig. 4 B on these figures
Note, therefore no longer redescribe herein.
In order to compensate for the reduction for the depressurization power being applied to by bearing spring 17b on the vehicle body 6 of vehicle, for the vehicle
Each wheel, hydraulic suspension system according to a second embodiment of the present invention further includes the machinery decompression backstop than the prior art
The longer machinery decompression stop part 16b of part 16.It is therefore preferred that the floating of hydraulic pressure relief stop part 15b according to the present invention is lived
Fill in have bar 14 around buffer 1 and between resting position and retraction stroke terminal position (such as at 40 and 80 millimeters
Between) mobile range.What the mobile range was more than the floating piston of the hydraulic pressure relief stop part 15 of the prior art (is about 20
To 30mm's) mobile range.Moreover, the extension of the mobile range of hydraulic pressure relief stop part 15b can reduce machinery decompression backstop
The rigidity of the spring of part 16b, hardly to lead to the braking of the piston 3 in the buffer 1 depressurized.In addition, the hydraulic pressure
The floating piston 15b of decompression stop part is formed by radially slotted cyclic rings in whole thickness, and the floating piston is used
In the sliding of bar 14 along buffer 1, to remain in the annular space between bar 14 and the inward flange of floating piston 15b
23b, and the upper part of the decompression chamber 5 of the cylinder body 2 of buffer 1 includes substantially coniform wall 2b, the cross section of the wall
Reduce upwardly toward the wall 8 of buffer 1.Therefore, the effect being applied to by decompression stop part 15b, 16b on the vehicle body of the vehicle
Power is incrementally increased very much with the stroke of floating piston 15b：When floating piston 15b along conical walls 2b towards buffer 1
When the upper end wall 8b movements of cylinder body 2, the notch and annular space 23b of floating piston 15b are gradually closed, this thus reduces hydraulic pressure
The passageway section of fluid.This it is ensured that the journey variable with floating piston 15b buffering, while significantly improving to institute
The control of the vertical and straight movement of the vehicle body of vehicle is stated, and hence improves the comfort of the vehicle.
Machinery depressurizes configurations of the stop part 16b and hydraulic pressure relief stop part 15b according to the stroke of the piston 3 of buffer 1
Configuration compared with the existing technology is different.
In fact, the piston 3 in hydraulic bjuffer 1 is more than retraction stroke 10 to (be preferably 20mm) between 50mm
When CD, flange 22 makes floating piston 15b be moved towards the upper end wall 8 of the cylinder body 2 of buffer 1.Floating piston 15b on the move by
Compressor mechanical depressurizes stop part 16b simultaneously for this.Therefore, once the piston 3 of hydraulic bjuffer 1 is more than retraction stroke CD, the liquid
The piston of compression buffer is gradually by two decompression stop part 15b, 16b brakings.
The comfort of the suspension is obviously improved by the hydraulic suspension system of second embodiment of the invention.In fact, not only
The suspension possesses the advantage identical as the advantages of first embodiment, and to the hydraulic pressure relief stop part 15b (hydraulic pressure reliefs
The floating piston of stop part has the mobile range of bigger) depressurize the stop part 16b (bullets of the machinery decompression stop part with machinery
Spring has the rigidity of relative weak) be applied in combination can between the trip of the decompression wheel shaft of the correspondence wheel of the vehicle in stroke by
The braking of cumulative plus buffer 1 piston 3, this significantly improves the control of the vertical and straight movement to the vehicle body 6 of the vehicle.This
Outside, the vertical resonant frequency in compartment 6 is reduced to the use of the bearing spring 17b of faint rigidity, this can improve the outstanding of vehicle
The comfort level of frame.Certainly, from stroke DME between the trip of the wheel shaft of medium energy, flexible increase of bearing spring 17b is by adding
Buffer compensation, the additional buffering is by hydraulic pressure attack stop part 9b, hydraulic pressure relief stop part 15b and machinery decompression stop part 16b
Ensure.
Finally, in turning, the outside of vehicle has the suspension element in attack moved, and vehicle is interior
Side has the suspension element in decompression.It is according to the present invention to attack stop part and to depressurize stop part and be applied in combination according to vehicle
Sideway amplitude increase buffer level, the stability which improve vehicles in turning.
The construction described in this way is not limited to above-described in Fig. 2A, Fig. 2 B, Fig. 3 A, Fig. 3 B, Fig. 4 A, Fig. 4 B, Fig. 5 A, figure
5B, Fig. 6 A, Fig. 6 B, Fig. 7 A, Fig. 7 B, Fig. 8 A, the embodiment shown on Fig. 8 B.The construction is only given as non-limiting example
Go out.Without departing from the scope of the invention, a variety of modifications can be added.Particularly, the present invention is not limited to hydraulic pressure attacks to stop
The single construction of block piece 9b.For example, it is contemplated that a kind of hydraulic pressure attacks stop part 9b, the hydraulic pressure attack the cylinder body 10b of stop part with
The inner wall of the compression chamber 4 of buffer 1 is connected, and the piston 11b of hydraulic pressure attack stop part is used in corresponding cylinder
It is moved by the piston 3 of buffer 1 in body 10b.Certainly, it is contemplated that known and can be accommodated in the compression chamber 4 of buffer 1
Any kind of hydraulic pressure attack stop part 9b.Especially, it can ideally consider that (hydraulic pressure is attacked to hydraulic pressure attack stop part 9b
The mobile range of piston 11b or cylinder body 10b of stop part are hit as described in the prior art) use so that from medium energy
Wheel shaft trip between stroke DME play the pistons 3 of the buffers 1 and can ensure the piston 11b or cylinder body of hydraulic pressure attack stop part 9b
The movement of 10b.It is also contemplated that for each wheel of vehicle, bearing spring 17b is offset to outside hydraulic bjuffer 1, and with
The hydraulic bjuffer 1 is assemblied in side by side between the axle journal frame of wheel and the vehicle body 6 of the vehicle.It is also contemplated that in vehicle
Rear axle position at, machinery attack stop part 7b deviate and each of be interposed in the axle journal frame of corresponding wheel and the vehicle of vehicle
Between body 6.Finally, it is also contemplated that, in order to further improve vehicle passenger comfort level, by off-load or soft hydraulic cushion
Device (amortisseur hydraulique d é tar é ou assoupli) replaces each hydraulic bjuffer 1 of suspension, for
The off-load or soft hydraulic bjuffer, for ensuring hydraulic bjuffer 1b of the hydraulic fluid from 3 liang of sides of piston to off-load
The aperture circulated in compression chamber 4 or decompression chamber 5 is more than the aperture of the buffer 1 of the prior art.
Claims (14)
1. a kind of vehicle, especially motor vehicles hydraulic suspension system, for each wheel of the vehicle, the hydraulic pressure
Suspension system includes：Buffer (1) with cylinder body (2) and piston (3), the piston is in the cylinder body movably with described
Bound decompression chamber and compression chamber's two chambers (5,4) are distinguished in cylinder body, described two chambers are interposed in vehicle body (6) and institute
Between the axle journal frame for stating the wheel of vehicle；Hydraulic pressure attacks stop part (9b), and the hydraulic pressure attack stop part is assemblied in the compression
In chamber (4) and include movable relative to each other cylinder body (10b) and piston (11b), which is characterized in that for each vehicle
Wheel, the hydraulic suspension system include compressible machinery attack stop part (7b), and the machinery attack stop part is located in institute
It states between cylinder body (2) and the vehicle body (6) of the vehicle or between the axle journal frame of the wheel and the vehicle body (6) of the vehicle,
Also, the piston (11b) and cylinder body (10b) of the hydraulic pressure attack stop part (9b) are used for the piston when the buffer described
It is reached in the cylinder body (2) of buffer (1) opposite by means of the piston (3) of the buffer (1) when the first attack stroke (CA1)
In moving each other, also, the machinery attack stop part (7b) is used for the piston (3) when the buffer (1) in the buffering
The cylinder body (2) in buffer when attacking stroke (CA2) more than the second of first stroke (CA1) is reached in the cylinder body of device
It compresses between the vehicle body (6) of the vehicle or is compressed between the axle journal frame of the wheel and the vehicle body (6) of the vehicle, and
And for each wheel of the vehicle, the hydraulic suspension system further includes bearing spring (17b), the bearing spring
Rigidity is selected such that the vertical resonant frequency of the vehicle body (6) of the vehicle between 1Hz and 1.1Hz.
2. suspension system according to claim 1, which is characterized in that the vertical resonant frequency of the vehicle body (6) of the vehicle
Pass through formulaTo limit, wherein M is the sprung mass of a quarter of the vehicle supported by wheel of vehicle, and
And K is the rigidity of the bearing spring (17b) at corresponding positions of wheels of vehicle.
3. suspension system according to claim 1 or 2, which is characterized in that the buffer (1) is the buffer of off-load.
4. suspension system according to any one of claim 1 to 3, which is characterized in that the piston of the buffer (1)
(3) the first attack reference stable state (AR) of stroke (CA1) based on the vehicle is between zero and 20 millimeters.
5. suspension system according to any one of claim 1 to 4, which is characterized in that the piston of the buffer (1b)
(3) the second attack reference stable state (AR) of stroke (CA2) based on the vehicle is between 40 and 50 millimeters.
6. suspension system according to any one of claim 1 to 5, which is characterized in that the hydraulic pressure stop part (9b)
Cylinder body (10b) is connected with the inner wall of the cylinder body (2) of the buffer (1), also, hydraulic pressure attack stop part (9b)
When piston (11b) is used to reach the first attack stroke (CA1) in the cylinder body (2) of the buffer when the piston of the buffer
It is mobile by the piston (3) of the buffer in corresponding cylinder body (10b).
7. suspension system according to any one of claim 1 to 5, which is characterized in that the hydraulic pressure stop part (9b)
Piston (11b) is connected with the bottom wall (12) of the cylinder body (2) of the buffer, also, hydraulic pressure attack stop part (9b)
Cylinder body (10b) be used for when the buffer piston the buffer (1) cylinder body (2) in reach first attack stroke
(CA1) mobile by the piston (3) of the buffer and mobile along the piston (11b) of the hydraulic pressure stop part (9b) when.
8. suspension system according to any one of claim 1 to 5, which is characterized in that the hydraulic pressure stop part (9b)
Cylinder body (10b) includes multiple radial holes (13), and the multiple radial hole passes through the wall of the cylinder body (10b) and in the hydraulic pressure
Liquid is allowed to input or export described delay when the piston (11b) and cylinder body (10b) of attack stop part (9b) are moved relative to each other
Rush the compression chamber of the cylinder body (10b) of device (1).
9. suspension system according to any one of claim 1 to 8, which is characterized in that for each vehicle of the vehicle
Wheel, the suspension system includes at least one decompression stop part (15,16), and at least one decompression stop part is assemblied in correspondence
Buffer (1) cylinder body (2) decompression chamber (5) in.
10. according to the suspension system described in any one of claim 1 to 5 and 8, which is characterized in that described for each wheel
Suspension system further includes that compressible machinery depressurizes stop part (16b) and the hydraulic pressure relief stop part (15b) with piston, described
Machinery decompression stop part and hydraulic pressure relief stop part are assemblied in the decompression chamber (5), also, the hydraulic pressure relief stop part
The piston of (15b) is used in corresponding cylinder body (2) by the movement of the piston (3) of the buffer (1), meanwhile, the machinery subtracts
Stop part (16b) is pressed to reach third retraction stroke (CD) in the cylinder body (2) of the buffer (1) in the piston of the buffer
When by the buffer piston (3) compress.
11. according to the suspension system described in any one of claim 1 to 5,8 and 10, which is characterized in that the buffer (1)
Piston (3) reference stable state (AR) of the third retraction stroke (CD) based on the vehicle between ten and 20 millimeters.
12. according to the suspension system described in any one of claim 1 to 6,8,10 and 11, which is characterized in that the hydraulic pressure subtracts
Pressure stop part is floating piston (15b), and the floating piston surrounds the bar (14) of the buffer (1), and the floating is lived
It fills in the decompression chamber (5) for the cylinder body (2) for being located in the buffer and in the upper end wall of the cylinder body of the buffer (2) (8)
Between flange (22), the upper end wall is passed through by the bar (14) of the buffer, the bar of the flange and the buffer
(14) it is connected.
13. suspension system according to claim 12, which is characterized in that the machinery decompression stop part (16b) is to reply
Spring, the returning spring are located in the decompression chamber (5), and the end of the returning spring be resisted against respectively it is described
On floating piston (15b) and in the upper end wall of the cylinder body of the buffer (2) (8).
14. a kind of vehicle, the vehicle especially motor vehicles, and include according to any one of claims 1 to 13
Hydraulic suspension system.
Applications Claiming Priority (5)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| FR1652612 | 2016-03-25 | ||
| FR1652612A FR3049227B1 (en) | 2016-03-25 | 2016-03-25 | HYDRAULIC SUSPENSION SYSTEM OF A VEHICLE |
| FR1652613 | 2016-03-25 | ||
| FR1652613A FR3049228B1 (en) | 2016-03-25 | 2016-03-25 | HYDRAULIC SUSPENSION SYSTEM OF A VEHICLE |
| PCT/FR2017/050489 WO2017162951A1 (en) | 2016-03-25 | 2017-03-06 | Hydraulic suspension system for a vehicle |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| CN108778789A true CN108778789A (en) | 2018-11-09 |
Family
ID=58464586
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN201780019608.0A Pending CN108778789A (en) | 2016-03-25 | 2017-03-06 | The hydraulic suspension system of vehicle |
Country Status (3)
| Country | Link |
|---|---|
| EP (1) | EP3433117A1 (en) |
| CN (1) | CN108778789A (en) |
| WO (1) | WO2017162951A1 (en) |
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|---|---|---|---|---|
| GB683198A (en) * | 1951-06-01 | 1952-11-26 | Gabriel Co | Shock absorber |
| GB887191A (en) * | 1959-11-27 | 1962-01-17 | Gen Motors Corp | Improvements relating to hydraulic shock absorbers |
| GB2092707A (en) * | 1981-02-05 | 1982-08-18 | Woodhead Ltd Jonas | Telescopic hydraulic shock absorber with hydraulic rebound stop |
| JPS6264603A (en) * | 1985-09-15 | 1987-03-23 | Showa Seisakusho:Kk | Bottom hit preventive device for wheel suspension hydraulic shock absorber |
| DE102004039702A1 (en) * | 2004-08-17 | 2006-07-13 | Zf Friedrichshafen Ag | Self-pumping hydropneumatic strut has stop ring mounted on piston rod and guide bush mounted above it which supports spring between against rod guide, flexible stop being fitted on stop ring on side facing guide bush |
| CN101927674A (en) * | 2006-12-08 | 2010-12-29 | 丰田自动车株式会社 | The suspension of vehicle |
| WO2015029984A1 (en) * | 2013-08-26 | 2015-03-05 | 株式会社テイン | Hydraulic shock-absorbing device |
| CN104919207A (en) * | 2012-12-03 | 2015-09-16 | 北京京西重工有限公司 | Hydraulic suspension damper with position dependent damping assembly |
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| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| GB2158181B (en) * | 1984-04-30 | 1988-11-02 | Volzh Ob Proizv | Hydraulic telescopic shock-absorber with a rebound bumper |
| JPH01295043A (en) * | 1988-05-20 | 1989-11-28 | Soqi Inc | Hydraulic buffer |
| JP2901639B2 (en) * | 1989-04-24 | 1999-06-07 | 株式会社ユニシアジェックス | Displacement sensitive hydraulic shock absorber |
| FR2664210B1 (en) * | 1990-07-06 | 1994-10-21 | Bianchi Mauro Sa | METHOD OF SUSPENSION OF THE TYPE USING A LARGER STRAIGHTNESS IN THE "REBOUND" RACE THAN IN THE "SHOCK" RACE HAVING A MEANS FOR SOFTENING THE PASSAGE OF ONE STRAIGHTENER TO THE OTHER AND ITS IMPLEMENTATION DEVICE. |
| US5810130A (en) * | 1997-03-14 | 1998-09-22 | General Motors Corporation | Suspension damper with rebound cut-off |
| FR2888780B1 (en) * | 2005-07-25 | 2007-09-07 | Bianchi Mauro Sa | SUSPENSION ASSEMBLY FOR A VEHICLE |
| JP2007146947A (en) * | 2005-11-25 | 2007-06-14 | Showa Corp | Hydraulic shock absorber |
| FR2995048B1 (en) | 2012-09-05 | 2015-04-03 | Soben | HYDRAULIC STOP FOR BRAKING AT THE END OF THE RACE OF A PISTON AND SHOCK ABSORBER WITH SUCH A ROCKET |
| US9193241B2 (en) * | 2013-02-28 | 2015-11-24 | GM Global Technology Operations LLC | Systems and methods for damper having jounce shock |
| JP6274871B2 (en) * | 2014-01-17 | 2018-02-07 | Ｋｙｂ株式会社 | Suspension device |
| JP2015163799A (en) * | 2014-02-28 | 2015-09-10 | 株式会社ショーワ | hydraulic shock absorber |
-
2017
- 2017-03-06 CN CN201780019608.0A patent/CN108778789A/en active Pending
- 2017-03-06 EP EP17715208.9A patent/EP3433117A1/en not_active Withdrawn
- 2017-03-06 WO PCT/FR2017/050489 patent/WO2017162951A1/en active Application Filing
Patent Citations (8)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| GB683198A (en) * | 1951-06-01 | 1952-11-26 | Gabriel Co | Shock absorber |
| GB887191A (en) * | 1959-11-27 | 1962-01-17 | Gen Motors Corp | Improvements relating to hydraulic shock absorbers |
| GB2092707A (en) * | 1981-02-05 | 1982-08-18 | Woodhead Ltd Jonas | Telescopic hydraulic shock absorber with hydraulic rebound stop |
| JPS6264603A (en) * | 1985-09-15 | 1987-03-23 | Showa Seisakusho:Kk | Bottom hit preventive device for wheel suspension hydraulic shock absorber |
| DE102004039702A1 (en) * | 2004-08-17 | 2006-07-13 | Zf Friedrichshafen Ag | Self-pumping hydropneumatic strut has stop ring mounted on piston rod and guide bush mounted above it which supports spring between against rod guide, flexible stop being fitted on stop ring on side facing guide bush |
| CN101927674A (en) * | 2006-12-08 | 2010-12-29 | 丰田自动车株式会社 | The suspension of vehicle |
| CN104919207A (en) * | 2012-12-03 | 2015-09-16 | 北京京西重工有限公司 | Hydraulic suspension damper with position dependent damping assembly |
| WO2015029984A1 (en) * | 2013-08-26 | 2015-03-05 | 株式会社テイン | Hydraulic shock-absorbing device |
Also Published As
| Publication number | Publication date |
|---|---|
| EP3433117A1 (en) | 2019-01-30 |
| WO2017162951A1 (en) | 2017-09-28 |
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