• 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:

    公开号:FR3017673A1
    申请号:FR1451154
    申请日:2014-02-14
    公开日:2015-08-21
    发明作者:Gabriel Lemaire；Alain Bellamy
    申请人:Hutchinson SA；
    IPC主号:
    专利说明:

    [0001] Hydraulic antivibratory support. The present invention relates to controllable hydraulic antivibration mounts. More particularly, the invention relates to a controllable hydraulic antivibration support intended to be interposed for the purpose of damping between first and second rigid elements, this antivibration support 10 comprising: - first and second armatures intended to be fixed to the two rigid elements to - an elastomeric body which interconnects the first and second armatures and which at least partially delimits a working chamber; a deformable compensation chamber which communicates with the working chamber via a first passage; constricted, the compensation chamber, the working chamber and the first constricted passage 20 forming a hydraulic volume filled with liquid, the first constricted passage having a resonance frequency of between 5 and 20 Hz, - an auxiliary chamber, - a check valve decoupling comprising an elastomeric decoupling membrane 25 which separates the the work and the auxiliary chamber and first and second stop grids respectively communicating with the working chamber and with the auxiliary chamber, the decoupling membrane being disposed between the first and second stop grids and at a distance from each stop gate in order to be able to freely debate between said first and second stop grids, - a control device adapted to selectively block the decoupling membrane. EP-A-0115417 discloses an antivibratory support of this type, in which the auxiliary chamber is a pneumatic chamber and the control device can selectively isolate or interconnect this auxiliary chamber.
    [0002] The present invention is intended in particular to improve the effectiveness of antivibration mounts of the type above. For this purpose, according to the invention, an antivibration support of the kind in question is characterized in that the auxiliary chamber is filled with liquid and communicates with said hydraulic volume via a second constricted passage having a resonance frequency less than 5 Hz, in that it further comprises a pneumatic control chamber separated from the auxiliary chamber by a movable wall, and in that the control device is adapted to selectively vent said chamber pneumatic control, or empty said pneumatic control chamber so as to block said movable wall. Thanks to these arrangements, the displacement limiting function of the decoupling membrane and the decoupling deactivation function are separated, which allows: on the one hand, to optimize the travel of the decoupling membrane, in particular so that it does not disturb the operation of the first constricted passage (it is generally sought to limit the displacement of the decoupling membrane to less than 1 mm, or even less than 0.5 mm), and secondly, to optimize the deactivation of the decoupling by allowing a large clearance to the aforementioned movable wall, which greatly limits the volume of air remaining in the air chamber when empty. In addition, the auxiliary chamber is always at the same static or quasi-static pressure as the working chamber, thanks to the presence of the second throttled passage, so that the decoupling membrane is always substantially equidistant from the two grids. This limit allows for optimal operation of the decoupling valve. Furthermore, the dimensioning of the second throttling passage means that it is neutralized at the relatively high frequencies concerned by the decoupling, so that it does not disturb the operation of the decoupling valve. decoupling valve. In various embodiments of the antivibration support according to the invention, one or more of the following provisions may also be used: the control device comprises an air outlet valve allowing normally only the air outlet from the pneumatic control chamber to the atmosphere and not vice versa, and an operable venting device for selectively venting said pneumatic control chamber; the pneumatic control chamber is delimited between a cup and the movable wall which is an elastomeric control membrane, the air outlet valve communicating with the pneumatic control chamber through an opening in the cup and the diaphragm; control being adapted to press against the bowl under the effect of the air outlet valve when the venting device is not actuated; the compensation chamber is separated from the working chamber by a rigid partition which is secured to the second reinforcement, said rigid partition comprising the stop grids, the first throttled passage, the second throttled passage, the auxiliary chamber and the membrane; decoupling; The rigid partition comprises first and second superimposed plates, the first plate comprising the first stop gate, the second stop gate being clamped between the first and second plates, the second plate comprising an opening arranged in correspondence with the auxiliary chamber; and sealingly closed by said movable wall constituted by an elastomeric control membrane; - The decoupling membrane is mounted between the first and second stop grids with a clearance of less than 1 mm with respect to each grid and the movable wall is movable on a deflection of several millimeters relative to its median position. Other features and advantages of the invention will become apparent from the following description of one of its embodiments, given by way of non-limiting example, with reference to the accompanying drawings. In the drawings: FIG. 1 is a perspective view of an antivibration support according to one embodiment of the invention, FIG. 2 is a view in axial section of the antivibration support of FIG. 1, FIG. 3 is an enlarged view of detail III of FIG. 2, and FIG. 4 is a radial sectional view of the antivibration support of FIGS. 1 and 2. In the various figures, the same references denote identical or similar elements. FIG. 1 shows a controllable hydraulic antivibration support 1, comprising: a first rigid reinforcement 2 having for example the shape of a metal base and intended for example to be fastened to the engine of a vehicle, a second rigid reinforcement 3 , for example an annular frame of metal or plastic, which is intended to be fixed for example to the vehicle body directly via at least one fastening member 3a, - an elastomer body 4 capable of supporting In particular the static forces due to the weight of the vehicle engine and connecting the first and second armatures 2, 3, this elastomer body may for example have a bell shape which extends axially along an axis, for example vertical Z, between a 4a top adhered and overmolded 10 on the first frame 2 and an annular base 4b overmolded and adhered to the second frame 3. As shown in Figure 2, the the antivibration support 1 further comprises a rigid partition 5 secured to the second armature 3 and sealingly applied against the base 4b of the elastomeric body, delimiting therewith a hydraulic working chamber A. A flexible bellows-forming elastomeric membrane 6, sealingly applied against the partition 5 opposite the working chamber A, defining with said partition 5 a hydraulic compensation chamber B which communicates with the working chamber A through A choke passage C. The working chamber, the compensation chamber B and the choke passage C together form a hydraulic volume filled with liquid, especially glycol or the like. The throttled passage C is sized to have a resonance frequency of between 5 and 20 Hz, typically between 8 and 12 Hz. As shown in FIGS. 2 and 4, the antivibration support 1 further comprises a hydraulic auxiliary chamber E, filled with liquid, which communicates with said hydraulic volume A, B, C by another constricted passage D itself filled with liquid. The constricted passage D is of very small cross-section, and is dimensioned so as to have a resonance frequency of less than 5 Hz, for example about 1 to 2 Hz (the cutoff frequency of this passage D, in particular the cutoff frequency at 3dB, is also less than 5 Hz). More particularly, the constricted passage D communicates with the constricted passage C in the example considered here. This constricted passage D could also be in the form of a small hole (not shown) formed in the decoupling membrane 31 which will be described below. The antivibration support 1 comprises a pneumatic chamber P separated from the auxiliary chamber E by a movable wall which may have all known shapes (including piston, flexible membrane or other). In the example considered here, the movable wall is a flexible elastomer control membrane, and this control membrane may advantageously be a part 6a of the above-mentioned membrane 6, in particular a central portion 6a of said membrane 6. In the example shown in Figure 1, the hydraulic antivibration support comprises a cover 7, 20 made for example of molded plastic material, which covers the bellows 6 downwards. In the example shown, the cover 7 may comprise an annular base 8, extended at its outer periphery by an upstanding annular side wall 9, which side wall 9 forms an annular projection 9a and terminates in a flange. outer ring 10 which may for example be sandwiched between the second frame 3 and the fastener 3a, which are fixed together by any known means, for example by screws. The cover 7 may further comprise an inner annular wall 11 which extends upwardly the inner periphery of the bottom 8. This inner annular wall 11 extends to a radial wall 12 which delimits the pneumatic control chamber downwards. P.
    [0003] More particularly, the upper face 13 of the radial wall 12 may be concave, so as to form a bowl which delimits said pneumatic control chamber P.
    [0004] In the example shown, the rigid partition 5 and the outer periphery of the membrane 6 are clamped between the base 4b of the elastomer body 4 and the projection 9a of the cover, while the periphery of the portion 6a of the membrane 6 is pinched between the periphery of the radial wall 12 and the rigid partition 5. The pneumatic chamber P communicates with the atmosphere via an opening 14 pierced in the radial wall 12 of the cover 7, and via a control device 15 fixed within the aforementioned inner annular wall 11 of the cover 7. This control device 15 includes an air outlet valve 16 which is adapted for, in normal operation (i.e. out of the forced open state), allow only the air outlet from the pneumatic chamber P to the atmosphere and not the other way around. The air outlet valve 16 may comprise a valve member 17 which is biased resiliently by a spring 18 so as to be applied against a valve seat 19. In the example considered here, the valve seat 19 is formed by the lower face of the annular wall 12. The dead volume defined inside the opening 14 between the inner surface 13 and the valve seat 19, is thus reduced to the maximum. This dead volume is advantageously between 0 and 0.3 cm3. The valve member 17 may comprise, for example: a seal 20 made of elastomer or the like, adapted to fit sealingly against the valve seat 19, a slider 21 comprising at least one ferromagnetic part, bearing the seal 20 and urged towards the radial wall 12 by the spring 18. The control device 15 further comprises an electromagnet 23, connected for example by an electrical connector 24 to external control means belonging to the vehicle, such as the control computer. CALC edge. On command of the calculator CALC, the electromagnet 23 produces a magnetic field which moves the valve member 17 away from the valve seat 19, which puts the pneumatic chamber P in communication with the atmosphere. Note that the electromagnet 23 could be replaced by any other actuator, including electric or pneumatic. Furthermore, in the example shown in FIGS. 2 and 3, the rigid partition 5 may comprise three superimposed radial plates, made of metal or plastic and clamped between the base 4b of the elastomer body and the projection 9a of the cover. a first plate 25 disposed towards the working chamber A and forming at its center a first disk-shaped stop grid 26, this first plate 25 having at its outer periphery a channel 27 which is open over its entire length to the opposite of the working chamber A and which also has an opening 27a to the working chamber, - a second disc-shaped stop grid 29 arranged in correspondence with the first gate 26 under the first plate 25, a second annular plate 28 disposed under the first plate 25 and the second stop gate 29, having a central opening 28a in correspondence with the control membrane 6a and the stop grids 26, 29 second plates, the second plate comprising an opening arranged in correspondence with the auxiliary chamber and sealingly closed by the portion 6a of the membrane 6. The second plate 28 defines the throttled passage C with the first plate 25, and has an opening 27b (Figure 4) which communicates the constricted passage C with the compensation chamber B. The second plate 28 further comprises, on its upper face, a bowl defining the auxiliary chamber E, and a thin channel which delimits the constricted passage D and communicates the constricted passage C with the auxiliary chamber E (see Figures 2 and 4).
    [0005] The stop grids 26, 29 delimit between them a housing 30 in which is engaged a decoupling membrane 31 of elastomer, which may have any known shape. As shown in more detail in FIG. 3, the decoupling membrane 31 is mounted with a certain clearance e with respect to each stop grid 26, 29, so as to be able to freely debate between the stop grids 26, 29. e is typically of the order of a few tenths of a millimeter, for example about 0.5 mm. The decoupling membrane 31 may be locally clamped between the stop grids 26, 29, for example at the periphery 31a of said decoupling membrane 31. The stop grids 26, 29 and the decoupling membrane 31 together form a valve decoupling whose function is to absorb the vibrations of relatively high frequency (greater than 20 Hz) and relatively low amplitude (of the order of 0.5 mm and lower). Thanks to the second constricted passage D, the auxiliary chamber E is always at the same pressure as the working chamber when the vehicle is not operating, so that this spacing e on both sides of the decoupling membrane is maintained despite the pressure created in the working chamber by the weight of the vehicle engine. The device that has just been described operates as follows.
    [0006] When the engine of the vehicle is operating under certain predefined conditions, for example at idle speed, the vehicle computer activates the electromagnet 23 to open the air outlet valve 16, so that the pneumatic chamber P communicates with the vehicle. This allows the membrane 6a to move freely: in this mode of operation, the vibrations of the motor are transmitted to the working chamber A by the elastomer body 4, which causes fluctuations in the volume of said chamber. working. These frequency fluctuations of greater than 20 Hz and of relatively low amplitude are absorbed by the decoupling valve 26, 29, 31. In other predetermined conditions, for example during the running of the vehicle (i.e. particularly when the engine speed is above a certain predetermined limit), the vehicle computer stops activating the electromagnet, so that the air outlet valve 16 returns to the closed position under the action of the 18. In this mode of operation, the vibratory displacements of the motor, of relatively large amplitude and frequency generally between 5 and 20 Hz, in particular between 8 and 12 hours (so-called "hash" movements), result in relatively large volume variations of the working chamber A, which cause deformations of the compensation chamber B, so that the constricted passage C is then the seat of phenomena of resonance onance allowing vibration damping in good conditions. In addition, at the beginning of the establishment of this mode of operation, the pneumatic chamber P still contains air, so that the portion 6a of the membrane 6 can move, but these movements drive the air out of the air. pneumatic chamber P through the air outlet valve 16. When almost all the air contained in the chamber P has been driven out, the portion 6a of the membrane 6 remains substantially pressed against the upper surface 13 of the radial wall 12 (Position shown in phantom in Figure 2), and the auxiliary hydraulic chamber E can no longer be deformed. In addition, the liquid does not pass through the constricted passage D at the hash frequencies, so that the decoupling membrane is immobilized. The decoupling valve is thus deactivated in this mode of operation. Note that the portion 6a of the membrane 6 is movable over a travel of several millimeters relative to its median position, which optimizes the efficiency of the deactivation of the decoupling valve. The antivibration support which has just been described is particularly well suited for 3-cylinder engines or having operating modes on 3 cylinders.
    权利要求:
    Claims (6)
    [0001]
    REVENDICATIONS1. A controllable hydraulic antivibration support intended to be interposed for the purpose of damping between first and second rigid elements, this antivibration support comprising: first and second armatures (2, 3) intended to be fixed to the two rigid elements to be joined; an elastomeric body (4) which interconnects the first and second armatures (2, 3) and at least partially delimits a working chamber (A), - a deformable compensation chamber (B) which communicates with the chamber the working chamber (A) via a first constricted passage (C), the compensation chamber (B), the working chamber (A) and the first throttled passage (C) forming a hydraulic volume filled with liquid the first constricted passage having a resonance frequency of 5 to 20 Hz; an auxiliary chamber (E); a decoupling valve (26, 29, 31) comprising: an elastomeric decoupling membrane (31) which separates the working chamber (A) and the auxiliary chamber (E), and first and second stop grids (26, 29) communicating respectively with the working chamber (A) and with the auxiliary chamber (E), the decoupling membrane (31) being disposed between the first and second stop grids (26, 29) and at a distance from each stop gate for free movement between said first and second stop grids, - a control device (15). ) adapted to selectively lock the decoupling membrane (31), characterized in that the auxiliary chamber (E) is filled with liquid and communicates with said hydraulic volume via a second constricted passage (D) having a frequency of resonance less than 5 Hz, in that it further comprises a pneumatic control chamber (P) separated from the auxiliary chamber (E) by a movable wall (6a), and in that the control device (15) is Suitable for sel ec ectively either venting said pneumatic control chamber (P), or emptying said pneumatic control chamber so as to block said movable wall (6a).
    [0002]
    An antivibration support according to claim 1, wherein the control device (15) comprises an air outlet valve (16) normally allowing only an air outlet from the pneumatic control chamber (P) to the atmosphere. and not the opposite, and a venting device (23) operable to selectively vent said pneumatic control chamber (P).
    [0003]
    3. Antivibration support according to claim 2, wherein the pneumatic control chamber (P) is delimited between a bowl (13) and the movable wall (6a) which is an elastomer control membrane (6a), the valve of air outlet (23) communicating with the pneumatic control chamber (P) through an opening (14) in the bowl (13) and the control membrane being adapted to press against the bowl (13) under the effect of the air outlet valve when the venting device (23) is not actuated.
    [0004]
    4. Antivibration support according to any one of the preceding claims, wherein the compensation chamber (B) is separated from the working chamber (A) by a rigid partition (5) which is integral with the second armature (3) said rigid partition comprising the first and second stop grids (26, 29), the first constricted passage (C), the second throttled passage (D), the annular space (E) and the decoupling membrane (31).
    [0005]
    5. Antivibration support according to claim 4, wherein the rigid partition (5) comprises first and second superimposed plates (25, 28), the first plate (25) comprising the first stop gate (26), the second gate of abutment (29) being clamped between the first and second plates (25, 28), the second plate (28) comprising an opening (28a) arranged in correspondence with the auxiliary chamber (E) and sealingly closed by said movable wall (6a), constituted by an elastomeric control membrane.
    [0006]
    An anti-vibration mount according to any one of the preceding claims, wherein the decoupling membrane (31) is mounted between the first and second abutment grids with a clearance (e) of less than 1 mm from each grid and the movable wall (6a) is movable on a displacement of several millimeters with respect to its median position.
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    同族专利:
    公开号 | 公开日
    US9416843B2|2016-08-16|
    FR3017673B1|2016-02-12|
    EP2908023A1|2015-08-19|
    CN104847837B|2017-06-13|
    US20150233443A1|2015-08-20|
    CN104847837A|2015-08-19|
    引用文献:
    公开号 | 申请日 | 公开日 | 申请人 | 专利标题
    US20060006593A1|2004-07-07|2006-01-12|Jean-Pierre Bretaudeau|Controllable hydraulic vibration-damping support|
    US20080023897A1|2006-07-26|2008-01-31|Tokai Rubber Industries, Ltd.|Fluid filled type vibration damping device|
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    FR2937702B1|2008-10-23|2010-11-26|Hutchinson|HYDRAULIC ANTIVIBRATORY SUPPORT AND VEHICLE COMPRISING SUCH A SUPPORT|
    DE102010060885A1|2010-08-26|2012-03-01|Contitech Vibration Control Gmbh|Engine mounts for a motor vehicle|FR3029251B1|2014-12-02|2017-04-28|Hutchinson|PILOTABLE HYDRAULIC ANTIVIBRATORY SUPPORT|
    JP6619702B2|2016-06-23|2019-12-11|株式会社ブリヂストン|Vibration isolator|
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    DE102016120959B4|2016-11-03|2020-07-09|Vibracoustic Gmbh|Hydraulically damping bearing|
    DE102017007999A1|2017-08-24|2019-02-28|Sumitomo Riko Company Limited|Switchable hydraulic bearing|
    CN110360266B|2018-09-10|2020-12-18|北京京西重工有限公司|Hydraulic suspension device and separating piece|
    法律状态:
    2015-02-26| PLFP| Fee payment|Year of fee payment: 2 |
    2016-02-25| PLFP| Fee payment|Year of fee payment: 3 |
    2017-01-18| PLFP| Fee payment|Year of fee payment: 4 |
    2018-01-23| PLFP| Fee payment|Year of fee payment: 5 |
    2019-01-25| PLFP| Fee payment|Year of fee payment: 6 |
    2020-01-29| PLFP| Fee payment|Year of fee payment: 7 |
    2021-01-20| PLFP| Fee payment|Year of fee payment: 8 |
    2022-01-26| PLFP| Fee payment|Year of fee payment: 9 |
    优先权:
    申请号 | 申请日 | 专利标题
    FR1451154A|FR3017673B1|2014-02-14|2014-02-14|PILOTABLE HYDRAULIC ANTIVIBRATORY SUPPORT|FR1451154A| FR3017673B1|2014-02-14|2014-02-14|PILOTABLE HYDRAULIC ANTIVIBRATORY SUPPORT|
    US14/622,390| US9416843B2|2014-02-14|2015-02-13|Hydraulic vibration-damping support|
    EP15155111.6A| EP2908023A1|2014-02-14|2015-02-13|Controllable hydraulic anti-vibration mounting|
    CN201510081404.2A| CN104847837B|2014-02-14|2015-02-15|Controllable hydraulic vibration Damper Braces|
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