• 专利附录
  • 专利说明
  • 权利要求
  • 类似技术
  • 同族专利
  • 引用文献
  • 法律状态
  • 优先权
    • 专利摘要:
    A motor vehicle hydraulic suspension damper, comprising a main piston (4) displaced during movement of the suspension, separating two main chambers, and an inertia fluid column (26) containing a fluid displaced by the movements of the main piston (4). ), notable in that it comprises two annex chambers each connected to a main chamber, separated by a floating piston (10) comprising a return spring (12) in a central position and a balancing leakage bore (14) , the bore receiving this floating piston (10) having a bypass channel (16) around this median position, the floating piston (10) being connected to a piston of inertia (22) separating two chambers of inertia connected between they by the fluid column (26).
    公开号:FR3073174A1
    申请号:FR1760485
    申请日:2017-11-08
    公开日:2019-05-10
    发明作者:Christophe Monteil；Jean Chillon；Zoran Dimitrijevic；Francis Bontron；Aurelien Pierson
    申请人:PSA Automobiles SA；
    IPC主号:
    专利说明:

    VEHICLE SUSPENSION HYDRAULIC SHOCK ABSORBER WITH INERTIA COLUMN
    The present invention relates to a hydraulic shock absorber for the suspension of a motor vehicle, as well as a motor vehicle equipped with such shock absorbers.
    Motor vehicles have a shock absorber on each wheel arranged in parallel with a suspension spring, which slows the movement of the suspension to ensure comfort and handling. Hydraulic shock absorbers are often used comprising a piston moving in a cylinder to delimit two chambers, with a limitation of the passages of the fluid from one chamber to the other in order to slow down the movements of this piston.
    The braking intensity of the suspension movement, which is generally differentiated according to the direction of this movement, represents a compromise that meets different constraints.
    In particular, it is advantageous to slow down the proper mode of oscillation of the vehicle body representing the suspended mass, at low frequencies generally between 1 and 5 Hz, to improve comfort.
    For this, a known type of damper, presented in particular by document US-A1-20130037362, comprises an inertia system comprising a column of fluid connecting two chambers disposed on each side of a sliding inertia piston with the suspension movement .
    The column of fluid wound around the body of the shock absorber, has a reduced section and a length large enough to contain a mass of fluid set in motion with high speed by the movement of the suspension, which artificially adds inertia to the body during its movements.
    However, a problem which arises for this type of shock absorber is that this inertia is also seen by the unsprung mass comprising the wheel and its hub, generally having a natural frequency of vertical rebound of the wheel with its tire, which is of the 'order of 15Hz.
    This additional inertia lowers the natural frequency of oscillation of the wheel by increasing the amplitude of the movement, which greatly reduces the vibrational comfort, and can also degrade the road holding due to lack of maintenance of this wheel on the ground.
    A known solution consists in having in addition a bypass channel, called “by-pass” in English, in the cylinder receiving the inertia piston, connecting the two chambers by orifices opening out near the standard average level of this piston . Small oscillations of the inertia piston at higher frequencies leave the openings open, the exchanges of fluid from one chamber to another are done by the bypass channel, without passing through the inertia column and without adding braking by inertia.
    The oscillations of larger amplitudes of the inertia piston at lower frequencies close the orifices of the bypass channel, the fluid passes through the inertia column which adds inertia braking.
    However, this solution poses a problem when the average attitude of the vehicle is modified, for example with an on-board load compressing the suspension springs, which means that the inertia piston leaves its standard average level to find itself on an offset average level. , and is no longer centered on the bypass channel. This channel no longer allows free passage from one chamber to another for small oscillations of this piston.
    The object of the present invention is in particular to avoid these problems of the prior art.
    To this end, it provides a hydraulic shock absorber for the suspension of a motor vehicle, comprising a main piston moved during the movements of the suspension, separating two main chambers, and a column of inertial fluid containing a fluid displaced by the movements of the main piston, this shock absorber being remarkable in that it comprises two annex chambers each connected to a main chamber, separated by a floating piston comprising a return spring in a middle position and a balancing leakage bore, the bore receiving this floating piston comprising a bypass channel around this median position, the floating piston being linked to an inertia piston separating two inertia chambers connected together by the fluid column.
    An advantage of this shock absorber is that whatever the average level of the main piston, which can be standard, or offset with, for example, a vehicle load, the balancing leakage hole allows the fluid to transfer between a certain delay the annex chambers under the effect of the return spring, by returning the floating piston to its middle position.
    After this time delay, the floating piston returns to its middle position, which gives full efficiency to the bypass channel arranged around this position, independently of the vehicle load.
    Small oscillations at higher frequencies do not move the inertia piston linked to the floating piston, which does not increase the apparent mass of the vehicle body. The larger oscillations at lower frequencies move the floating piston as well as the inertia piston, which sets in motion the fluid in the inertia column by increasing the apparent mass of the vehicle.
    The hydraulic shock absorber according to the invention may further include one or more of the following characteristics, which can be combined with one another.
    Advantageously, the bypass channel is formed by a continuous groove made on one side of the bore receiving the floating piston. This channel can be produced economically.
    Advantageously, the return spring comprises a helical spring disposed on each side of the floating piston.
    Advantageously, the floating piston and the inertia piston are arranged along the same axis.
    In this case, advantageously the floating piston and the inertia piston are connected by a rigid rod passing through a body of the floating piston and a body of the inertia piston. This embodiment is simple to implement.
    Advantageously, the column of fluid forms a tube wound around a body of the inertia piston.
    Advantageously, the damper comprises a first hydraulic circuit comprising the floating piston and a second hydraulic circuit comprising the inertia piston, having two different fluids. In this case, it is possible to optimize the types of fluid for each circuit.
    In particular for a 15Hz main piston oscillation frequency, the floating piston does not move beyond the bypass channel. In this way, no apparent mass is added for the rebound frequency of a vehicle wheel.
    In particular for an oscillation frequency of the main piston less than 5 Hz, the floating piston moves beyond the bypass channel. In this way we add an apparent mass for the natural frequencies of oscillation of the vehicle body.
    The invention further relates to a motor vehicle fitted with suspension shock absorbers on each running gear, remarkable in that at least one running gear comprises hydraulic shock absorbers comprising any of the preceding characteristics.
    The invention will be better understood and other characteristics and advantages will appear more clearly on reading the description below given by way of example and without limitation, with reference to the accompanying drawings in which:
    - Figure 1 is a diagram of a hydraulic shock absorber according to the invention presented in axial section, having small oscillations around its standard average level;
    - Figure 2 is a diagram of this damper having large oscillations around its standard average level;
    - Figure 3 is a diagram of this damper leaving towards an offset average level; and
    - Figure 4 is a diagram of this damper when it returns to its standard average level.
    Figure 1 shows a shock absorber comprising a main body 2 comprising in a bore a main piston 4 having a rod 6 protruding from one side, delimiting two main chambers. The body 2 and the rod 6 are each connected to the body of the vehicle or to a suspension element, to brake the relative movements between them.
    The vehicle being in a nominal state, comprising for example a low load, the body height gives the main piston 4 an average level 0.
    An annex body 8 comprises a floating piston 10 separating two annex chambers each comprising a helical return spring 12, these return springs tending to return this piston to its central position 0. Each annex chamber is connected to a main chamber of the main body 2 .
    The floating piston 10 has a balancing leak hole 14, having a reduced section in order to allow a slow flow from one chamber annexed to the other. The balancing leakage hole 14 allows, in the absence of stress from the main piston 2, by an exchange of fluid between the annex chambers, the floating piston 10 to return with a delay to its central position 0 under the effect of the springs recall 12 which tend towards this position.
    A bypass channel 16 disposed on the side of the bore of the annex body 8, constitutes a free passage of fluid between the two annex chambers when the floating piston 10 is near its average level 0. Advantageously the bypass channel 16 is formed by a continuous groove made on one side of the bore, protruding axially on each side of the floating piston 10.
    A inertia body 20 arranged in the axis of the annex body 8 comprises a inertia piston 22 separating two inertia chambers, which is connected by a rigid rod 24 to the floating piston 10 passing through the annex body with dynamic sealing. and inertia, so as to couple their axial movements.
    The ends of the bore of the two inertia chambers are permanently connected to each other by a column of inertia fluid 26 having a reduced section, wound around the inertia body 20, in order to maintain the exchange between these two chambers for all movements of the inertia piston 22.
    The length of the inertia column 26 gives a certain mass of fluid displaced with a sufficiently high speed thanks to this reduced section, when the inertia piston 22 moves by transferring the fluid from one inertia chamber to the other . Significant inertia of the fluid is obtained in the inertia column 26.
    FIG. 1 shows oscillating displacements of the suspension around its standard average level 0, with an average frequency comprising a low amplitude, corresponding to the rebound frequency of the wheel linked to the suspension which is of the order of 15 Hz . The equivalent displacements A of the main piston 4 transfer small volumes of fluid into the annex chambers.
    In this case the oscillations of the floating piston 10 around its average position 0 have a low amplitude, this piston remains at the level of the bypass channel 16 which allows a transfer of the fluid from one annex chamber to the other without being braked. The floating piston 10 as well as the inertia piston 22 is hardly used.
    The inertia piston 22 does not act, the suspension remains very flexible, and the wheel rebounds are left free to allow this wheel better grip on the ground.
    FIG. 2 shows the oscillation displacements of the suspension around its standard average level 0, with a low frequency comprising a higher amplitude, corresponding to the proper mode of the body which is between 1 and 5 Hz. The equivalent displacements B of the main piston 4 around the standard mean level 0, transfer large volumes of fluid into the annex chambers.
    The bypass channel 16 and the balancing leakage bore 14 have an insufficient section to quickly transfer the large volumes of fluid arriving in each annex chamber, the floating piston 10 is stressed by substantially following these variations in volume representing the oscillation of the main piston 4.
    The inertia piston 22 reproducing the movement of the floating piston 10, displaces the fluid in the inertia column 26, which by its own inertia is opposed to the oscillating movement of this inertia piston.
    The floating piston 10 is similarly braked, and in turn brakes the main piston 4 by opposing the transfer of fluid which it generates. The vehicle's oscillation movements are braked.
    FIG. 3 shows a load of the vehicle which displaces the suspension on an offset level X. The large volume of fluid displaced by the main piston 4 in the same direction causes an offset of the floating piston 10 upwards.
    However, the return springs 12 applying a constant return force of the floating piston 10 to its middle position 0, force the passage of the fluid in the balancing bore 14 with slow dynamics, which gradually brings this piston back to its middle position 0 .
    Subsequently when the vehicle is running, oscillations of the suspension are applied around the offset middle position X. For oscillations at medium frequency with a low amplitude, operation without damping is obtained by the column of inertia fluid 26 as shown in Figure 1, and for low frequency oscillations with a higher amplitude, operation with the damping of the inertia column 26 as shown in Figure 2.
    The damping efficiency does not change despite the load of the vehicle.
    FIG. 4 shows a discharge from the vehicle which displaces the suspension towards the standard medium level 0. The large volume of fluid displaced in the same direction causes an offset of the floating piston 10 downwards.
    In the same way the return springs 12 apply a constant force on the floating piston 10, bringing it back with a slow dynamic towards its middle position 0 thanks to the transfer of fluid by the balancing bore 14.
    Subsequently, the damper regains the same efficiency, depending on the oscillation frequency of the suspension.
    Obtained in a simple and effective manner, with an economical system which is purely mechanical, an efficiency of a suspension with inertial damping which is independent of the average position of the suspension, and of the vehicle load.
    In addition, it will be noted that two independent hydraulic circuits are used, a first for the main piston 4 and the floating piston 10, and a second for the inertia piston 22. Two different fluids can be used by adapting each fluid for the desired functions. , in particular by using a higher density fluid for the inertia piston 22 in order to obtain a higher damping performance.
    权利要求:
    Claims (10)
    [1" id="c-fr-0001]
    1 - Hydraulic shock absorber for the suspension of a motor vehicle, comprising a main piston (4) moved during the movements of the suspension, separating two main chambers, and a column of inertia fluid (26) containing a fluid displaced by the movements of the main piston (4), characterized in that it comprises two annex chambers each connected to a main chamber, separated by a floating piston (10) comprising a return spring (12) in a middle position and a balancing leakage hole ( 14), the bore receiving this floating piston (10) comprising a bypass channel (16) around this median position, the floating piston (10) being linked to an inertia piston (22) separating two inertia chambers interconnected by the fluid column (26).
    [2" id="c-fr-0002]
    2 - Hydraulic damper according to claim 1, characterized in that the bypass channel (16) is formed by a continuous groove formed on one side of the bore receiving the floating piston (10).
    [3" id="c-fr-0003]
    3 - Hydraulic damper according to claim 1 or 2, characterized in that the return spring (12) comprises a helical spring disposed on each side of the floating piston (10).
    [4" id="c-fr-0004]
    4 - Hydraulic damper according to any one of the preceding claims, characterized in that the floating piston (10) and the inertia piston (22) are arranged along the same axis.
    [5" id="c-fr-0005]
    5 - Hydraulic damper according to claim 4, characterized in that the floating piston (10) and the inertia piston (22) are connected by a rigid rod (24) passing through a body of the floating piston (8) and a body of the inertia piston (20).
    [6" id="c-fr-0006]
    6 - Hydraulic damper according to any one of the preceding claims, characterized in that the fluid column (26) forms a tube wound around a body of the inertia piston (20).
    [7" id="c-fr-0007]
    7 - Hydraulic damper according to any one of the preceding claims, characterized in that it comprises a first hydraulic circuit comprising the floating piston (10) and a second hydraulic circuit comprising the inertia piston (22), having two different fluids.
    [8" id="c-fr-0008]
    8 - Hydraulic damper according to any one of the preceding claims, characterized in that for an oscillation frequency of the piston
    5 main (4) of 15Hz, the floating piston (10) does not move beyond the bypass channel (16).
    [9" id="c-fr-0009]
    9 - Hydraulic damper according to any one of the preceding claims, characterized in that for an oscillation frequency of the main piston (4) less than 5Hz, the floating piston (10) moves beyond the channel
    [10" id="c-fr-0010]
    10 bypass (16).
    10 - Motor vehicle equipped with suspension shock absorbers on each running gear, characterized in that at least one running gear comprises hydraulic shock absorbers according to any one of the preceding claims.
    类似技术:
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    同族专利:
    公开号 | 公开日
    FR3073174B1|2019-10-04|
    引用文献:
    公开号 | 申请日 | 公开日 | 申请人 | 专利标题
    WO2011089373A1|2010-01-25|2011-07-28|Lotus Renault Gp Ltd|Fluid inerter|
    JP5161395B1|2012-11-14|2013-03-13|株式会社免制震ディバイス|Vibration suppression device|
    CN202991714U|2012-12-07|2013-06-12|江苏大学|Inertia coefficient-adjustable vehicle hydraulic inert container device|
    EP2808578A1|2013-04-17|2014-12-03|Kayaba System Machinery Co., Ltd.|Vibration reduction apparatus|
    JP2015137658A|2014-01-20|2015-07-30|清水建設株式会社|vibration reduction device|
    CN204526713U|2015-02-02|2015-08-05|江苏大学|Liquid electrical hookup formula vehicle suspension impedance control device|CN110397695A|2019-07-17|2019-11-01|重庆大学|Magnetorheological half active variable damping and the suspension damper mechanism for actively becoming used appearance|
    FR3102098A1|2019-10-17|2021-04-23|Psa Automobiles Sa|HYDRAULIC TYPE INERTIAL SUSPENSION AND INERTIA ASSEMBLY INCORPORATED|
    FR3106302A1|2020-01-20|2021-07-23|Psa Automobiles Sa|INERTIAL SUSPENSION FOR VEHICLES|
    法律状态:
    2018-10-24| PLFP| Fee payment|Year of fee payment: 2 |
    2019-05-10| PLSC| Publication of the preliminary search report|Effective date: 20190510 |
    2019-10-22| PLFP| Fee payment|Year of fee payment: 3 |
    2020-10-21| PLFP| Fee payment|Year of fee payment: 4 |
    2021-10-20| PLFP| Fee payment|Year of fee payment: 5 |
    优先权:
    申请号 | 申请日 | 专利标题
    FR1760485|2017-11-08|
    FR1760485A|FR3073174B1|2017-11-08|2017-11-08|HYDRAULIC DAMPER FOR VEHICLE SUSPENSION WITH INERTIA COLUMN|FR1760485A| FR3073174B1|2017-11-08|2017-11-08|HYDRAULIC DAMPER FOR VEHICLE SUSPENSION WITH INERTIA COLUMN|
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