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

Definitions

• the invention relates to a hydraulic suspension system of a vehicle, especially automobile.
• a hydraulic suspension system of a vehicle in particular a vehicle, comprises for each of the wheels of the vehicle a piston damper movable in its corresponding cylinder and interposed between the body and the wheel stub axle. of the vehicle.
• the role of this damper is to greatly limit the oscillations transmitted by the wheels to the vehicle when the wheels encounter roughness or obstacles present on the road on which the vehicle is traveling.
• the latter comprises compressible mechanical strikers and optionally mechanical expansion stops, or possibly hydraulic. The role of these stops is also to protect the chassis of the vehicle when there are strong deflections of the corresponding wheel, due to incidents or significant obstacles, such as the retarders of the type dos-d'astae or the potholes.
• the present invention aims to overcome the above disadvantages of the prior art.
• the invention relates to a hydraulic suspension system of a vehicle, particularly an automobile, according to claim 1. [008] Other features are set forth in the dependent claims.
• the invention also relates to a vehicle, including automobile, comprising such a hydraulic suspension system.
• FIGS. 1A and 1B show a longitudinal sectional diagram of a damper of the prior art and a graph illustrating the arrangement of the components of the damper as a function of the piston stroke of the damper in the cylinder of the shock absorber;
• FIGS. 2A and 2B show a longitudinal sectional diagram of a damper according to a first embodiment of the invention when the vehicle is at a reference attitude and a graph of the arrangement of the elements of the damper corresponding to the position of the piston marked in Figure 2A;
• FIG. 3A and 3B show a longitudinal sectional diagram of a damper according to the first embodiment of the invention when the stroke of the damper piston exceeds a first stroke in the cylinder of the shock absorber and a graph of the arrangement of the elements of the damper corresponding to the position of the piston indicated in FIG. 3A;
• FIGS. 4A and 4B show a longitudinal sectional diagram of a damper according to the first embodiment of the invention when the stroke of the damper piston exceeds a second attacking stroke in the damper cylinder as well as a graph of the arrangement of the elements of the damper corresponding to the position of the piston indicated in FIG. 4A;
• FIGS. 6A and 6B show a longitudinal sectional diagram of a damper according to the second embodiment of the invention when the vehicle is at a reference attitude and a graph of the arrangement of the elements of the damper corresponding to the position of the piston marked in Figure 5A;
• FIGS. 6A and 6B show a longitudinal sectional diagram of a damper according to the second embodiment of the invention when the stroke of the damper piston exceeds a first stroke in attack in the damper cylinder as well as a graph of the arrangement of the elements of the damper corresponding to the position of the piston indicated in FIG. 6A;
• FIGS. 7A and 7B show a longitudinal sectional diagram of a damper according to the second embodiment of the invention when the stroke of the damper piston exceeds a second attacking stroke in the damper cylinder as well as a graph of the arrangement of the elements of the damper corresponding to the position of the piston indicated in FIG. 7A;
• FIGS. 8A and 8B show a longitudinal sectional diagram of a damper according to the second embodiment of the invention when the stroke of the damper piston exceeds a third expansion stroke in the damper cylinder as well as a graph of the arrangement of the elements of the damper corresponding to the position of the piston indicated in FIG. 8A.
• the suspension of the vehicle comprises, for each wheel of the vehicle, a hydraulic damper 1 comprising a body 2 in the form of a cylinder and a piston 3 movable in the cylinder 2.
• This damper 1 is interposed between the body 6 of the vehicle and the corresponding wheel knuckle.
• each hydraulic damper 1 of the vehicle hydraulic suspension system can be described according to a damping law in which the force exerted by the damper 1 depends on the speed of movement of the corresponding wheel. In other words, the faster the piston 3 moves in the cylinder 2 of the damper, the greater the force exerted by the damper 1 on the body 6 of the vehicle is important.
• the hydraulic suspension system also comprises, for each wheel of the vehicle, a suspension spring 17 mounted around the damper 1 and whose ends are respectively supported against the body 6 of the vehicle via a cup 18 and against a cup 19 secured to the cylinder 2 of the damper.
• the suspension spring 17 is a stiffness element whose behavior can be described by a law in which the force exerted by the spring 17 on the body 6 of the vehicle depends on the amplitude of the displacement of the corresponding wheel. In other words, the more the suspension spring 17 is compressed, the greater the force exerted on the body 6 of the vehicle is important.
• the suspension spring 17 essentially serves to carry the body 6 of the vehicle while allowing the deflections.
• the suspension system also comprises, for each wheel of the vehicle, two respectively mechanical and hydraulic driving abutments 7 and 9 respectively mechanical and hydraulic 16 and hydraulic expansion stops respectively.
• Each mechanical stop 7, 16 is similar to a stiffness, and therefore exerts a force on the body 6 according to the movement of the corresponding wheel.
• the force exerted on the body 6 of the vehicle by the mechanical stops respectively of attack 7 and relaxation 16 is even greater than the deflection in attack and relaxation of the corresponding wheel is important.
• each hydraulic stop of attack 9 and relaxation 15 is in turn assimilable to a damper and therefore exerts a force on the body 6 of the vehicle according to the speed of travel of the corresponding wheel.
• the force exerted on the body 6 of the vehicle by the hydraulic stops respectively of attack 9 and relaxation 15 is even greater than the speed of travel of the corresponding wheel is important.
• the mechanical attack abutment 7 is secured to one end of the cylinder 2 of the damper and positioned between the cylinder 2 of the damper and the body 6 of the vehicle. It also has an annular cross-section so as to be traversed by the rod 14 of the piston 3 of the damper 1.
• the mechanical attack stop 7 is compressed between the end of the cylinder 2 of the damper 1 and the body 6 of the vehicle so as to strongly slow the stroke of the piston 3 in the cylinder 2 of the damper.
• the mechanical attack abutment 7 is made of elastomer material having a very high stiffness constant, so that the force exerted by the mechanical attack abutment 7 on the body 6 of the vehicle increases very rapidly with the deflection in attack of the wheel.
• the hydraulic attack stop 9 is mounted in the compression chamber 4 of the cylinder 2 of the damper 1.
• the hydraulic attack abutment 9 comprises a piston 1 1 secured to the bottom bottom wall 12 of the cylinder 2 of the damper, and a cylinder 10 intended to be displaced along the piston 1 1 of the attack abutment 9 by the piston 3 of the damper 1 when it reaches the vicinity of the end of stroke attack.
• the cylinder 10 of the hydraulic abutment 7 forms a compression chamber 20 filled with the hydraulic fluid, which is likely to escape from this chamber 20 by leaks around the piston 1 1 of hydraulic abutment 9 when the piston 3 of the damper moves the cylinder 10 of the hydraulic attack stop 9 towards the lower bottom wall 12 of the damper.
• the piston 3 of the damper 1 arriving near its end stroke attack is very quickly braked.
• the hydraulic attack abutment 9 comprises a return spring 21 surrounding the piston 1 1 of the hydraulic abutment 9 and whose ends bear against respectively the lower bottom wall 12 of the cylinder 2 of the damper and the annular end edge flanking the cylinder 10 hole of the hydraulic stop 9.
• the return spring 21 allows the cylinder 10 of the hydraulic attack stop 9 to return to the rest position when the piston 3 of the damper 1 moves away from the cylinder 10 of the hydraulic stop 9.
• the hydraulic expansion stop 15 is in turn a floating piston surrounding the rod 14 of the damper 1 so as to maintain an annular space 23 between the rod 14 and the inner edge of the floating piston through which the hydraulic fluid is likely to circulate.
• the hydraulic expansion stop 15 is positioned in the expansion chamber 5 of the cylinder 2 of the damper, between the upper end wall 8 of the cylinder 2 of the damper through which the rod 14 of the damper and a collar 22 forming a valve secured to the rod 14 of the damper.
• the mechanical expansion stop 16 is in turn a high stiffness spring positioned in the expansion chamber 5 and whose ends bear respectively against the floating piston 15 and the upper end wall 8 of the cylinder 2 of the damper 1.
• the vertical scale represents the stroke in millimeters of the piston 3 of the damper in the cylinder 2 of the damper 1 during deflections of the vehicle wheel.
• the horizontal scale is a visual scale representing the force exerted by each element of the hydraulic suspension at a wheel as a function of the stroke of the piston 3 in the cylinder 2 of the corresponding damper 1.
• the zero stroke corresponds to the position of the piston 3 of the damper 1 in the cylinder when the suspension of the vehicle does not undergo any other effort than that exerted by the mass of the vehicle. The vehicle is then at the reference base AR.
• the negative races of the piston 3 of the damper in the cylinder 2 correspond to deflections in attack of the wheel, that is to say that the suspension tends to compress and the body 6 of the vehicle to move closer to the road compared to the reference base AR.
• the positive strokes of the piston 3 of the shock absorber 1 in the cylinder 2 correspond to displacements in relaxation of the wheel, that is to say that the suspension tends to relax and the body 6 of the vehicle to move away from the road relative to the reference base AR.
• the wheel deflections correspond to the strokes of the piston 3 in the corresponding damper.
• the wheel deflections are greater than the piston strokes 3 of the corresponding damper 1.
• the wheel deflections are proportional to the piston stroke 3 of the corresponding damper 1.
• wheel deflections in attack or relaxation corresponding to the races in attack or relaxation of the piston 3 of the damper 1, between -15 mm and 15 mm from the reference base AR correspond to low energy DLE deflections which represent the most frequent solicitations encountered on roads of good quality.
• deflections of the wheel in attack or relaxation corresponding to the races in piston attack 3 of the damper 1, between - 15 mm and -50 mm from the reference base AR
• displacements of the wheel in attack or in expansion corresponding to the strokes of the piston 3 of the shock absorber 1, between 15 mm and 50 mm from the reference base AR
• medium energy displacements DME which represent solicitations also frequent.
• deflections of the wheel in attack or relaxation corresponding to the races in piston attack 3 of the damper 1, beyond -50 mm from the reference base AR
• deflections of the wheel in attack or relaxation corresponding to the strokes of the piston 3 of the shock absorber 1, greater than 50 mm from the reference base AR correspond to high energy DHE deflections which represent little solicitations frequent.
• the mechanical attack stop 7 is compressed as soon as the stroke of the piston 3 of the damper 1 exceeds an attack stroke of about 10 mm.
• the mechanical attack stop 7 intervenes quickly to slow the stroke of the piston 3 of the damper 1 from the medium energy deflections DME.
• the piston 3 of the hydraulic damper 1 causes the cylinder 10 of the hydraulic attack stop 9 to move around its corresponding piston 1 1, to rapidly brake the piston 3 of the damper 1 in its corresponding cylinder 2 and better protect the body 6 of the vehicle.
• the floating piston 15 of the hydraulic expansion stop is moved and simultaneously compresses the spring constituting the mechanical expansion stop 16 when the expansion stroke of the piston 3 of the damper 1 exceeds a value between 50 and 70 mm, preferably 50 mm, to quickly brake the piston 3 of the damper 1 in its corresponding cylinder 2.
• each wheel of the vehicle a damper 1 and two respectively mechanical 16 and hydraulic expansion stops 15 as described above.
• the suspension system according to the first embodiment of the invention comprises for each wheel of the vehicle a more flexible suspension spring 17b, whose stiffness constant is lower than the stiffness constant of a suspension spring 17 of the prior art, while providing a support S identical to the body 6 of the vehicle relative to the suspension spring 17 of the prior art.
• a more flexible suspension spring 17b makes it possible to reduce the vertical resonance frequency of the vehicle body. While with a suspension spring 17 of the prior art the resonant frequency of the body 6 of the vehicle is between 1.2 Hz and 1.4 Hz, the latter is between 1 Hz and 1.1 Hz for a suspension spring 17b more flexible. This results in increased comfort for the occupants of the vehicle.
• the suspended mass is the mass of the vehicle elements located above the hydraulic suspension, excluding including the wheels, rockets and stub axles of the vehicle.
• the mass suspended from a quarter of the vehicle at a wheel is defined as follows: once the center of gravity of the vehicle has been defined, the mass suspended from the rear part of the vehicle and the suspended mass of the front part of the vehicle. vehicle are in their defined laps.
• the front portion includes the portion of the vehicle between the front of the vehicle and a direction transverse to the vehicle passing through its center of gravity. The rear part of the vehicle is therefore the part from the rear of the vehicle to this transverse direction.
• the hydraulic suspension system also comprises for each wheel of the vehicle a mechanical attack abutment 7b shorter that the mechanical attack abutment 7 of the prior art, as well as, preferably, a hydraulic abutment 9b whose cylinder 10b has an amplitude of displacement around the corresponding piston 1 1b between its end stroke in attack and its end of stroke in relaxation for example between 40 and 60 mm.
• This displacement amplitude is greater than the displacement amplitude of the cylinder 10 of the hydraulic attack stop 9 of the prior art, which is of the order of 30 mm.
• the structure of the cylinder 10b of the hydraulic attack stop 9b is different, since the cylinder 10b comprises in its wall a plurality of through radial holes 13, and allowing the entry or exit of the hydraulic fluid of the compression chamber 4 of the cylinder 2 of the damper 1 when the piston 1 1b and the cylinder 10b of the hydraulic abutment 9b move relative to each other.
• the arrangement of the mechanical attack abutments 7b and hydraulic 9b as a function of the strokes of the piston 3 of the damper 1 is also different compared to that of the prior art. Indeed, when the piston 3 of the hydraulic damper 1 exceeds an attack stroke CA1 between 0 and 20 mm, preferably 10 mm, the latter causes the displacement of the cylinder 10b of the hydraulic attack stop 9b around its corresponding piston 1 1 b. For low and medium energy deflections, the overall section of a large number of the holes 13 passing through the cylinder 10b of the hydraulic thrust bearing 9b is sufficiently high to ensure gentle braking of the piston 3 of the shock absorber 1.
• the overall section of a smaller number of holes 13 through the cylinder 10b of the attack abutment hydraulic 9b decreases because an increasing number of through holes 13 are plugged by the piston 1 1 b of the hydraulic thrust bearing 9b as the cylinder 10b moves around the piston 1 1 b of the hydraulic thrust bearing 9b in direction of the bottom bottom wall 12 of the cylinder 2 of the damper 1: this ensures a more abrupt braking piston 3 of the damper 1 in order to protect the body 6 and the chassis of the vehicle.
• the mechanical attack stop 7b is compressed and contributes to the strengthening of the braking of the piston 3 of the shock absorber 1.
• the comfort of the suspension is significantly improved by the hydraulic suspension system of the first embodiment of the invention. Indeed, the discontinuity of the force exerted by the suspension system, and generator of discomfort for the passengers of the vehicle, is greatly reduced thanks to the hydraulic attack stop 9b, whose cylinder 10b has an extended range of displacement , who acts before the mechanical attack stop 7b.
• the force exerted by the hydraulic attack stop 9b depends both on the speed and the amplitude of displacement of the piston 3 of the damper 1 in its cylinder 2, the braking of the piston 3 of the shock absorber is adapted to the amplitude and speed of its stroke in the cylinder 2, which also has a positive effect on passenger comfort.
• the hydraulic attack stop 9b dissipates the energy without accumulating it, thereby avoiding any stimulus effect during low and medium energy deflections.
• the use of a suspension spring 17b of low stiffness reduces the vertical resonance frequency of the body 6, which improves the comfort of the suspension of the vehicle. This increase in the flexibility of the suspension spring 17b is of course compensated by the additional damping provided by the hydraulic attack stop 9b from the medium energy DME deflections.
• the hydraulic suspension system according to the second embodiment of the invention also comprises for each wheel of the vehicle a mechanical expansion stop 16b longer than the mechanical expansion stop 16 of the prior art. Consequently, and preferably, the floating piston of the hydraulic expansion stop 15b according to the invention has an amplitude of displacement around the rod 14 of the damper 1, between its rest position and its end-of-travel position. relaxation, for example between 40 and 80 mm. This displacement amplitude is greater than the displacement amplitude of the floating piston of the hydraulic expansion stopper 15 of the prior art, which is of the order of 20 to 30 mm.
• the extension of the displacement amplitude of the hydraulic expansion stop 15b makes it possible to reduce the stiffness of the spring of the mechanical expansion stop 16b, so that it contributes little to the braking of the piston 3 of the shock absorber 1 in relaxation.
• the floating piston 15b of the hydraulic expansion stop is formed by an annular ring radially split over its entire thickness and intended to slide along the rod 14 of the damper 1 so as to maintain an annular space 23b between the rod 14 and the inner edge of the floating piston 15b, while the upper part of the expansion chamber 5 of the cylinder 2 of the damper 1 comprises a wall 2b of substantially frustoconical shape whose cross section decreases in the upper direction towards the wall 8 of the shock absorber 1.
• the force exerted by the detent stops 15b, 16b on the vehicle body increases very gradually with the stroke of the floating piston 15b: as the floating piston 15b moves towards the upper end wall 8 of the cylinder 2 of the damper 1 along the frustoconical wall 2b, the slot and the annular space 23b of the floating piston 15b closes gradually, thereby decreasing the passage section of the hydraulic fluid.
• This therefore ensures a variable damping according to the stroke of the floating piston 15b, significantly improving control of the vertical movements of the vehicle body, and thus the comfort of the vehicle.
• the arrangement of the mechanical expansion stops 16b and hydraulic 15b according to the strokes of the piston 3 of the damper 1 is also different compared to that of the prior art. Indeed, when the piston 3 of the hydraulic damper 1 exceeds a relaxation stroke CD between 10 and 50 mm, preferably 20 mm, the flange 22 moves the floating piston 15b towards the upper end wall 8 of the cylinder 2 of the shock absorber 1. The floating piston 15b moving then simultaneously compresses the mechanical expansion stop 16b. Thus, as soon as the piston 3 of the hydraulic damper 1 exceeds the CD relaxation stroke, the latter is gradually braked by the two stops of relaxation 15b, 16b.
• the comfort of the suspension is significantly improved by the hydraulic suspension system of the second embodiment of the invention. Indeed, not only does it have the same advantages as the first embodiment, but in addition, the combined use of a hydraulic expansion stop 15b whose floating piston has a greater amplitude of displacement and a stop of mechanical expansion 16b whose spring has a relatively low stiffness allows a gradual increase in the braking of the piston 3 of the damper 1 during the expansion movements of the wheel of the corresponding vehicle, significantly improving the control of the vertical movements of the vehicle body 6 .
• a suspension spring 17b of low stiffness reduces the vertical resonance frequency of the body 6, which improves the comfort of the suspension of the vehicle. This increase in the flexibility of the suspension spring 17b is of course compensated by the damping complementary provided by the hydraulic attack stop 9b, the hydraulic expansion stopper 15b and the mechanical expansion stop 16b from the medium energy DME deflections.
• the outer side of the vehicle has elements of the suspension moving in attack and the inner side of the vehicle has suspension elements in relaxation.
• the combined use of the attack and detent stops according to the invention increases the level of damping as a function of the amplitude of the roll of the vehicle, which improves the stability of the latter in turns.
• the configuration as described is not limited to the embodiments described above and shown in FIGS. 2A, 2B, 3A, 3B, 4A, 4B, 5A, 5B, 6A, 6B, 7A, 7B, 8A, 8B. It has been given only as a non-limiting example. Multiple modifications can be made without departing from the scope of the invention.
• the invention is not limited to a single hydraulic thrust bearing configuration 9b.
• a hydraulic attack stopper 9b whose cylinder 10b is secured to the inner walls of the compression chamber 4 of the damper 1 and whose piston 1 1b is intended to be moved in its corresponding cylinder 10b by the piston 3 of the damper 1.
• any type of hydraulic drive stop 9b known and adapted to be housed in the compression chamber 4 of a damper 1 may be considered.
• a hydraulic attack stopper 9b whose displacement of the piston 1 1b or cylinder 10b is as described in the prior art, is perfectly conceivable as long as the piston 3 of the damper 1 is able to ensure the displacement of the piston 1 1b or the cylinder 10b of the hydraulic abutment 9b from the medium energy deflections DME.
• each hydraulic damper 1 of the suspension by a hydraulic damper detaré or softened, that is to say that the orifices ensuring the passage of hydraulic fluid from and the other of the piston 3 in one or the other of the compression chambers 4 and the expansion chamber 5 of the detuned hydraulic damper 1b are wider than the orifices of a shock absorber 1 of the prior art.

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• Engineering & Computer Science (AREA)
• Mechanical Engineering (AREA)
• General Engineering & Computer Science (AREA)
• Fluid-Damping Devices (AREA)
• Vehicle Body Suspensions (AREA)

Applications Claiming Priority (3)

Publications (1)

Family

ID=58464586

Family Applications (1)

Country Status (3)

Family Cites Families (19)

• 2017
  • 2017-03-06 WO PCT/FR2017/050489 patent/WO2017162951A1/fr active Application Filing
  • 2017-03-06 CN CN201780019608.0A patent/CN108778789A/zh active Pending
  • 2017-03-06 EP EP17715208.9A patent/EP3433117A1/de not_active Withdrawn

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