• 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:
    The damper and spring unit comprises a damper (10) with a cylinder (14) and a rod (16), a spring (12) arranged around the damper (10) and a linear actuator (20) provided to vary in a manner controlled the axial position of a lower end of the spring (12) relative to the cylinder (14) of the damper (10). The actuator (20) comprises an inner cylindrical member (22) adapted to be assembled around the cylinder (14) of the damper (10), an outer cylindrical member (24), which is assembled axially sliding relative to the inner cylindrical element (22) and which is adapted to support the lower end of the spring (12), and a working chamber (26) adapted to be filled with fluid under pressure to adjust the axial position of the outer cylindrical element ( 24) relative to the inner cylindrical member (22). The working chamber (26) is delimited, either radially or axially, only by the inner cylindrical member (22) and the outer cylindrical member (24). The outer cylindrical member (24) is provided with a support flange (28) adapted to support the lower end of the spring (12). The support flange (28) is positioned below the upper end of the outer cylindrical member (24), so that the outer cylindrical member (24) is at least partly arranged within the the volume of the spring (12), and extends radially outwardly relative to the outer cylindrical member (24), so that the inner diameter (Di) of the spring (12) is greater than the outside diameter (De) of the outer cylindrical member (24).
    公开号:FR3029463A3
    申请号:FR1561824
    申请日:2015-12-03
    公开日:2016-06-10
    发明作者:Massimo Seminara；Massimo Trinchera
    申请人:Sistemi Sospensioni SpA；
    IPC主号:
    专利说明:

    [0001] Linear actuator for adjusting the vertical position of a spring of a shock absorber group and a spring for a vehicle suspension and a shock absorber group and a spring for a vehicle suspension comprising such an actuator The present invention relates to a linear actuator intended to be used in a shock absorber and spring assembly for vehicle suspension to adjust the vertical position of the spring, and hence the height of the vehicle body from the ground. In a vehicle suspension comprising a damping and springing unit, wherein the damper is connected at its lower end to a wheel carrier or suspension arm and at its upper end to the body of the vehicle and wherein the spring is arranged around the damper and rests at its lower end against a spring plate attached to the damper and at its upper end against the body of the vehicle, it is known the use of a linear actuator interposed between the damper and the spring plate to vary the vertical position of the spring plate and consequently to adjust the height of the body of the vehicle from the ground. The document WO2009 / 033985 proposes a shock absorber and spring unit for a vehicle suspension provided with a linear actuator for adjusting the height of the body of the vehicle from the ground, in which the actuator is interposed between the shock absorber and the plate. on springs. The linear actuator comprises a cylinder attached to the damper and an annular piston vertically removable relative to the cylinder. The cylinder comprises an inner cylindrical member and an outer cylindrical member which are made as separate pieces from each other. The inner cylindrical member is arranged around the damper coaxially therewith. Between the inner cylindrical member and the outer cylindrical member is provided a working chamber which can be supplied with pressurized oil via a connector. The annular piston is slidably guided in the working chamber. At the free end (upper end) of the annular piston the spring plate is connected in such a way that the vertical displacement of the annular piston with respect to the cylinder determines a corresponding vertical displacement of the spring plate, and therefore of the lower end of the spring, with respect to the cylinder, and therefore with respect to the damper. The linear actuator known from this prior document therefore consists of three parts, ie the inner cylindrical element, the outer cylindrical element and the annular piston. These three parts together define the working chamber, insofar as the working chamber is closed laterally by the inner cylindrical element and the outer cylindrical element, below by the inner cylindrical element and in the upper part. by the annular piston. By the document W02012 / 156418 to the name of the Applicant, there is a further example of a linear actuator interposed between the damper and the spring of a damper group and spring for vehicle suspension to adjust the height of the body of the vehicle. ground, in which the linear actuator consists of three parts, two of which form the cylinder and a part forms the piston of the actuator. According to such a known example, in addition, the spring rests with its lower end on a spring plate assembled above the piston of the actuator and therefore results entirely arranged above the piston of the actuator.
    [0002] A linear actuator for adjusting the vertical position of the spring of a damper and spring unit for vehicle suspension is further known from DE 2005 008 814. Such a known linear actuator is basically composed of only two elements, namely an inner cylindrical member, or cylinder, adapted to be assembled around the damper cylinder, and an outer cylindrical member, or piston, which is assembled axially sliding relative to the inner cylindrical member and is adapted to bear the lower end of the spring. The two cylindrical elements of the actuator contain, either radially or axially, a working chamber capable of being filled with pressurized fluid to adjust the axial position of the outer cylindrical element with respect to the element. cylindrical interior, and from there the vertical position of the lower end of the spring relative to the cylinder of the damper. According to such a known solution, the spring is supported on a spring seat provided at the upper end of the outer cylindrical member of the actuator and the result then arranged completely above such an element of the actuator. In addition, this earlier document does not show or explain how the upward stroke of the outer cylindrical member is stopped. In addition, considering the mode of spring support on the outer cylindrical member, it is very difficult, if not impossible, to position an upper stop member which stops the upward stroke of the outer cylindrical member. Consequently, the solution of a linear actuator proposed by the document DE 10 2005 008 814 does not result in practice.
    [0003] The object of the present invention is to provide a linear actuator usable in a shock absorber and spring unit for vehicle suspension to adjust the vertical position of the spring, and subsequently the height of the vehicle body from the ground, of improved type. compared to the known technique, previously treated.
    [0004] This and other objects are quite achieved according to the invention by a linear actuator comprising an inner cylindrical member adapted to be assembled around a cylinder of the damper and an outer cylindrical member, which is assembled axially slidable with respect to the inner cylindrical member and adapted to support a lower end of the spring, wherein the inner cylindrical member and the outer cylindrical member are configured to completely enclose, either radially or axially, a working chamber adapted to be filled with pressurized fluid to adjust the axial position of the outer cylindrical member with respect to the inner cylindrical member, wherein the outer cylindrical member is provided with a support flange adapted to support the inner cylindrical member; lower end of the spring, and wherein the support flange is positioned below the upper end of the spring outer cylindrical member, such that the outer cylindrical member is arranged at least partly within the spring volume, and extends radially outwardly relative to the outer cylindrical member, so that that the inner diameter of the spring results greater than the outer diameter of the outer cylindrical member.
    [0005] Other features and advantages of the present invention will become more apparent from the following detailed description, given by way of non-limiting example only with reference to the accompanying drawings, in which: FIG. 1 is a perspective view of an actuator linear arrangement for a shock absorber and spring assembly for a vehicle suspension according to a first embodiment of the present invention; FIGS. 2 and 3 are axial sectional views which show the linear actuator of FIG. 1, respectively in the minimum and maximum extension positions, corresponding to the minimum vertical position and the maximum vertical position respectively. lower end of the spring; Figure 4 is a perspective view of a linear actuator for a shock absorber and spring assembly for vehicle suspension according to a second embodiment of the present invention; Figure 5 is an axial sectional view of the linear actuator of Figure 4; Figure 6 is a cross-sectional view along the section plane designated VI-VI in Figure 5; Figures 7 and 8 are axial sectional views showing a linear actuator for a shock absorber and spring assembly for vehicle suspension according to a third embodiment of the present invention, respectively in the corresponding minimum and maximum extension positions; respectively at the minimum vertical position and at the maximum vertical position of the lower end of the spring; and FIG. 9 is an axial sectional view of a linear actuator for a vehicle suspension and damping unit according to a fourth embodiment of the present invention, in the minimum extension position corresponding to the minimum vertical position. from the lower end of the spring.
    [0006] In the description and in the claims which follow, terms such as "upper" and "lower" are to be understood as related to the condition of assembly of the damping unit and spring on a vehicle. In addition, the terms "axial" and "longitudinal" and the like are used herein to identify the direction of the axis of the linear actuator, which axis in the assembly condition coincides with the axis of the damper , while the term "radial" is used to identify a direction crossing the axis of the damper and located in a plane perpendicular to such axis. Referring first to FIGS. 1-3, a damper and spring assembly for vehicle suspension comprises, in a manner known per se, a damper 10 and a spring 12. Either the damper or the spring are well-known components and so they will not be described here and illustrated in detail. Such components will only be described such elements and parts useful for the purpose of the description of the present invention.
    [0007] The damper 10 comprises a cylinder 14 strictly connected to a wheel-carrier (not shown) and a piston (not shown) sliding inside the cylinder 14 and having a rod 16 coming out of the upper end of the cylinder 14. cylinder 14 and which is coaxial with respect thereto. Either the cylinder 14 or the piston with its relative rod 16 are components of the type in themselves known. The axis of the cylinder 14 is marked z and coincides with the direction of the extension and retraction movement of the rod 16 relative to the cylinder 14. The x-axis is typically directed vertically or with a slight inclination with respect to the vertical. The rod 16 is fixed at its upper end to the body of the vehicle (not shown). The spring 12 is made as a helical spring and extends around the rod 16 of the damper 10. The damping and springing unit comprises a hydraulic linear actuator (henceforth simply designated as an actuator), generally located 20, provided to vary in a controlled manner the vertical position of the spring 12, specifically the vertical position of the lower end of the spring 12, for example to adjust the height from the vehicle body floor. The actuator 20 is interposed between the cylinder 14 of the damper 10 and the spring 12 so as to agree to adjust the relative position of the lower end of the spring 12 relative to the cylinder 14 of the damper 10 along the z axis, and from there to adjust the vertical position of the lower end of the spring 12, for example to vary the height of the vehicle body of the ground or to maintain constant the height of the vehicle body of the ground by compensating for height variations due to variations in the load on the vehicle. The actuator 20 basically comprises an inner cylindrical member 22 and an outer cylindrical member 24 which enclose a working chamber 26 and serve respectively as cylinder and piston of the actuator 20. The inner cylindrical member 22 is fixed to the cylinder 14 of the damper 10. The outer cylindrical member 24 is assembled around the inner cylindrical member 22 coaxially therewith. The outer cylindrical member 24 is provided with a support flange 28 which supports the lower end of the spring 12 and thus acts as a lower spring plate. The support flange 28 is preferably made in one piece with the outer cylindrical element 24. Preferably, a ring of elastomeric material 18 is interposed between the lower end 3029463 of the spring 12 and the support flange 28. The support flange 28 is positioned below the upper end of the outer cylindrical member 24, preferably in the lower half of such an element, and furthermore extends radially outwardly with respect to such an element. In this way, the outer cylindrical member 24 results at least partially within the volume defined by the spring 12 and furthermore the inner diameter (marked Di) of the spring 12 is greater than the outside diameter (Spotted from ) of the outer cylindrical member 24 (flange excluded). The outer cylindrical member 24 is axially slidable relative to the inner cylindrical member 22 between a minimum height position (Fig. 2), corresponding to the minimum height requirement from the ground of the lower end of the spring 12, and a position of maximum height (FIG. 3), corresponding to the condition of maximum height from the ground of the lower end of the spring 12. The working chamber 26 can be supplied with fluid (oil) under pressure and for this purpose it is connectable to a pressurized fluid supply source (not shown) via a feed passage 30 in the inner cylindrical member 22, preferably a feed passage 30 which extends vertically from a supply fitting 30a provided on the underside of the inner cylindrical member 22. Feeding pressurized fluid the working chamber 26 from the ha position 2 (or any intermediate position between the minimum height position and the maximum height position), the outer cylindrical element 24 moves axially upwards, lifting the spring with 12, up to the maximum height position of FIG. 3. On the contrary, starting from the maximum height position of FIG. 3 (or any intermediate position between the minimum height position). and the position of maximum height), the working chamber 26 is discharged, the outer cylindrical member 24, and with it the spring 12, moves in axial direction down to reach at most the height position minimum of Figure 2.
    [0008] As has been said above, according to one aspect of the invention, the working chamber 26 is completely enclosed by the two cylindrical elements 22 and 24. For this purpose, according to the illustrated embodiment, the inner cylindrical element 22 has a first outer cylindrical surface 22a, along which a first inner cylindrical surface 24a of the outer cylindrical member 24 is slidably arranged, and a second outer cylindrical surface 22b of larger diameter relative to the first surface. 22a, along which a second inner cylindrical surface 24b of the outer cylindrical member 24, larger in diameter relative to the first inner cylindrical surface 24a is slidably arranged. The first outer cylindrical surface 22a and the second outer cylindrical surface 22b of the inner cylindrical member 22 are contiguous to each other, the first surface being placed above the second. The two cylindrical surfaces 22a and 22b of the inner cylindrical member 22 are separated by a shoulder forming a stop surface 22c directed upwardly. The first inner cylindrical surface 24a and the second inner cylindrical surface 24b of the outer cylindrical member 24 are contiguous to each other, the first surface being placed above the second. The two cylindrical surfaces 24a and 24b of the outer cylindrical member 24 are separated by a shoulder forming an abutment surface 24c directed downwards. The working chamber 26 thus results delimited radially between the first outer cylindrical surface 22a of the inner cylindrical element 22 and the second inner cylindrical surface 24b of the outer cylindrical element 24 and in the axial direction between the abutment surface 22c of the the inner cylindrical element 22 and the abutment surface 24c of the outer cylindrical element 24.
    [0009] As shown in FIG. 2, the minimum height position of the actuator 20 is defined by the abutment between the abutment surface 22c of the inner cylindrical element 22 and the abutment surface 24c of the outer cylindrical element 24. In such a condition, the working chamber 26 is empty. As shown in FIG. 3, the maximum height position of the actuator 20 is defined by the stop between an upwardly facing abutment surface 32a of a stop member 32, which is made for example in the form of a ferrule and is screwed to the lower end of the outer cylindrical element 24, and a downwardly facing abutment surface 22d of the inner cylindrical element 22.
    [0010] Suitable seals 34 and 36 are interposed between the first outer cylindrical surface 22a and the first inner cylindrical surface 24a and between the second outer cylindrical surface 22b and the second inner cylindrical surface 24b to prevent leakage. oil between such surfaces to the outside of the actuator. In addition, the actuator is preferably provided with a dust cap 38 attached to the inner cylindrical member 22.
    [0011] In the embodiment described above, the two cylindrical elements 22 and 24 are free to rotate relative to each other about the z axis. Therefore, such an embodiment can not be used in these applications, for example in MacPherson suspensions for steered wheels, in which it is necessary to prevent relative rotation of the spring plate relative to the damper.
    [0012] With reference to FIGS. 4 to 6, in which the parts and elements which are identical or corresponding to those of FIGS. 1 to 3 are assigned the same reference numerals, in an alternative embodiment of the invention, the actuator 20 is configured for use on MacPherson suspension for steering wheels and is therefore provided with anti-rotation means able to prevent the relative rotation of the outer cylindrical member 24 with respect to the inner cylindrical member 22 around the z-axis. The description provided above concerning the embodiment of FIGS. 1-3 also applies to the embodiment of FIGS. 4-6 and will therefore not be repeated. What fundamentally changes from the embodiment of FIG. 1-3 is that the stop member 32 also acts as an anti-rotation means capable of preventing the relative rotation of the outer cylindrical member 24 relative to to the inner cylindrical member 22 around the z axis. For this purpose, the stop member 32 has an inner surface 32b of non-circular shape, for example of elliptical shape, and the lower end portion of the inner cylindrical member 22 has an outer surface 22e, along Which slides the stop element 32, of complementary shape to that of the inner surface 32b. The stop element 32 can therefore not rotate around the axis z with respect to the inner cylindrical element 22. The stop element 32 is fixed to the outer cylindrical element 24, for example by means of screws 40, and consequently even the outer cylindrical element 24 is locked in rotation with respect to the inner cylindrical element 22.
    [0013] As shown in FIGS. 7 and 8, in which parts and elements which are identical or corresponding to those of the preceding figures are assigned the same reference numerals, in an additional embodiment of the invention, also intended (as in FIG. the embodiment of Figs. 4-6) for use on MacPherson suspensions for steered wheels, the maximum height position of the actuator 20 is defined by a stop member 42 which is attached to the upper end of the inner cylindrical member 22 and which has a downwardly directed abutment surface 42a adapted to cooperate with an upwardly facing abutment surface 24d of the outer cylindrical member 24. The element stop 42 has for example an inverted glass shape and is attached to the inner cylindrical member 22 for example by means of a threaded coupling 44.
    [0014] According to such an embodiment, the rigid connection in rotation between the outer cylindrical element 24 and the inner cylindrical element 22, and consequently between the support flange 28 and the cylinder 14 of the damper 10, is obtained by means of in that the outer surface 22b of the inner cylindrical member 22 has a non-circular shape, for example of elliptical shape, and the inner surface 24b of the outer cylindrical member 24 is of complementary shape to that of the inner surface 22b . An additional exemplary embodiment of the invention is shown in FIG. 9, in which parts and elements that are identical or corresponding to those of the preceding figures are assigned the same reference numbers. According to such an embodiment, which is always intended for use on MacPherson suspensions for steered wheels, the maximum extension position of the actuator 20 is always obtained thanks to a stop element 42 assembled to the upper end of the inner cylindrical member 22, as in the embodiment of Figures 7 and 8. The rotational coupling between the outer cylindrical member 24 and the inner cylindrical member 22, is obtained here with 2 The use of one or more spring pins 46 supported by the outer cylindrical element 24 in their respective vertical guide grooves 48 provided in the inner cylindrical element 22, in particular on the outer cylindrical surface 22b of such an element .
    [0015] Naturally, the principle of the invention being of course, the modes of implementation and the details of implementation are likely to be widely varied with respect to what has been described and illustrated by way of example in no way limiting without departing from the scope of the invention as defined in the appended claims.
    权利要求:
    Claims (12)
    [0001]
    REVENDICATIONS1. Linear actuator (20) for adjusting the vertical position of a spring (12) of a damping unit (10) and a spring (12) for vehicle suspension, the actuator (20) comprising an inner cylindrical member (22) ) adapted to be assembled around a cylinder (14) of the damper (10) and an outer cylindrical member (24), which is assembled axially sliding relative to the inner cylindrical member (22) and which is adapted to supporting a lower end of the spring (12), wherein the inner cylindrical member (22) and the outer cylindrical member (24) are configured to completely enclose, either radially or axially, a working chamber (26). ) adapted to be filled with pressurized fluid to adjust the axial position of the outer cylindrical member (24) relative to the inner cylindrical member (22), characterized in that the outer cylindrical member (24) is provided with a support flange (28) adapted to support the lower end of the spring (12), the support flange (28) being positioned below the upper end of the outer cylindrical member (24), so that the element outer cylindrical portion (24) is at least partly arranged within the volume of the spring (12), and extending radially outwardly relative to the outer cylindrical member (24), so that the inner diameter (Di) of the spring (12) is greater than the outer diameter (De) of the outer cylindrical member (24).
    [0002]
    An actuator according to claim 1, wherein the support flange (28) is formed in one piece with the outer cylindrical member (24). 25
    [0003]
    An actuator according to claim 1 or claim 2, wherein the inner cylindrical member (22) has a first outer cylindrical surface (22a), along which a first inner cylindrical surface (24a) of the outer cylindrical member (24) is slidably arranged, and a second outer cylindrical surface (22b), of larger diameter relative to the first outer cylindrical surface (22a), along which is slidably arranged a second inner cylindrical surface (24b) of the outer cylindrical member (24) having a larger diameter relative to the first inner cylindrical surface (24a), wherein the first outer cylindrical surface (22a) and the second outer cylindrical surface (22b) of the element cylindrical interior (22) are contiguous with each other, with the first outer cylindrical surface (22a) positioned above the second surface 5 and 22b), and are separated from each other by a shoulder forming an upwardly facing abutment surface (22c), and wherein the first inner cylindrical surface (24a) and the second surface cylindrical interior (24b) of the outer cylindrical member (24) are contiguous with each other, with the first inner cylindrical surface (24a) positioned above the second inner cylindrical surface (24b), and they are separated Each other by a shoulder forming an abutment surface (24c) directed downwards, so that the working chamber (26) is delimited radially between the first outer cylindrical surface (22a) of the inner cylindrical member (22) and the second inner cylindrical surface (24b) of the outer cylindrical member (24) and in axial direction between the abutment surface (22c) of the inner cylindrical member (22) and the stop surface (24c) of the outer cylindrical member (24).
    [0004]
    4. An actuator according to any one of the preceding claims, further comprising a stop member (32) which is attached to the lower end of the outer cylindrical member (24) and which is adapted to act as a stop in the lifting movement of the outer cylindrical member (24) relative to the inner cylindrical member (22).
    [0005]
    5. An actuator according to any one of claims 1 to 3, further comprising a stop member (42) which is attached to the upper end of the inner cylindrical member (22) and which is adapted to serve as a abutment in the lifting movement of the outer cylindrical member (24) relative to the inner cylindrical member (22).
    [0006]
    6. An actuator according to any one of the preceding claims, further comprising anti-rotation means (22e, 32b, 22b, 24b, 46, 48) adapted to prevent relative rotation of the outer cylindrical member (24) relative to to the inner cylindrical member (22) about the longitudinal axis (z) of the actuator.
    [0007]
    An actuator according to claim 6, wherein said anti-rotation means (22e, 3029463, 32b, 22b, 24b, 46, 48) comprises an outer surface (22e, 22b) with a non-circular cross section and a surface interior (32b, 24b) of complementary shape to that of said outer surface (22e, 22b), said outer surface (22e, 22b) being rotationally integral with the inner cylindrical member (22) and said inner surface (32b, 24d) being integral in rotation with the outer cylindrical element (24).
    [0008]
    An actuator according to claims 4 and 7, wherein the inner surface (32b, 24b) of said anti-rotation means (22e, 32b, 22b, 24b, 46, 48) is a surface (32b) formed by the element stop (32).
    [0009]
    An actuator according to claim 7, wherein the inner surface (32b, 24b) and outer surface (22e, 22b) of said anti-rotation means (22e, 32b, 22b, 24b, 46, 48) are respectively formed by said second inner cylindrical surface (24b) and the second outer cylindrical surface (22b).
    [0010]
    An actuator according to claim 7, wherein said anti-rotation means (22e, 32b, 22b, 24b, 46, 48) comprise at least one vertical groove (48) provided in the second outer cylindrical surface (22b) of the inner cylindrical member (22) and at least one spring pin (46) which is respectively carried by the outer cylindrical member (24) and engages said at least one vertical groove (48).
    [0011]
    11 Damper and spring unit for vehicle suspension, comprising a damper (10) with a cylinder (14) and a rod (16), a spring (12) arranged around the damper (10), and a linear actuator ( 20) according to any one of the preceding claims, the linear actuator (20) being interposed between the cylinder (14) of the damper (10) and a lower end of the spring (12) to vary in a controlled manner the axial position of the spring (12) relative to the cylinder (14) of the damper. 30
    [0012]
    Vehicle suspension comprising a damping and spring unit according to claim 11.
    类似技术:
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    同族专利:
    公开号 | 公开日
    FR3029463B3|2017-01-13|
    US9834058B2|2017-12-05|
    DE202015106622U1|2016-03-03|
    RU171988U1|2017-06-23|
    US20160159191A1|2016-06-09|
    引用文献:
    公开号 | 申请日 | 公开日 | 申请人 | 专利标题
    US2874955A|1957-06-11|1959-02-24|Monroe Auto Equipment Co|Vehicle suspension system|
    DE1294234B|1965-02-05|1969-04-30|Teves Gmbh Alfred|Suspension strut for motor vehicles formed from a telescopic fluid vibration damper and a coil spring surrounding it|
    US3936039A|1974-06-21|1976-02-03|Tropic Industries, Inc.|Load-levelling shock absorber|
    US4736931A|1986-10-03|1988-04-12|Christopherson Rollin F|Dampening shock absorber|
    US4830395A|1988-02-22|1989-05-16|Foley Jimmy D|Stabilizer system for racing cars|
    EP0597996A1|1991-08-07|1994-05-25|Microhydraulics, Inc.|Active suspension system|
    DE4231641C2|1992-09-22|1996-12-12|Daimler Benz Ag|Suspension strut for automotive suspension systems|
    GB9323047D0|1993-11-09|1994-01-05|Acg France|A method of forming a suspension strut|
    DE19632805C2|1996-08-16|1999-02-04|Daimler Benz Ag|Device for height-adjustable support of a wheel or axle suspension on the body of a motor vehicle|
    US5996982A|1997-07-29|1999-12-07|Gabriel Ride Control Products, Inc.|Vehicle shock absorber with coil over preload adjustment|
    US5961106A|1998-06-08|1999-10-05|Shaffer; Theodore E.|Vehicle shock absorber assembly having height adjustment|
    DE10153007A1|2001-10-26|2003-05-08|Audi Ag|Height adjustment device|
    JP2004197838A|2002-12-18|2004-07-15|Kayaba Ind Co Ltd|Single cylinder type hydraulic buffer|
    US6691991B1|2003-03-18|2004-02-17|Tan-Cheng Huang|Shock absorber|
    RU2258616C2|2003-07-22|2005-08-20|Петров Виктор Дмитриевич|Vehicle wheel suspension|
    DE102005008814A1|2005-02-24|2006-09-07|H & R Spezialfedern Gmbh & Co. Kg|Hydraulic height adjusting device for e.g. motor vehicle chassis, has piston mechanism circularly surrounding exterior of support tube, and chamber formed by tube exterior, interiors of cylindrical arrangement and front side of mechanism|
    DE102007044538A1|2007-09-11|2009-03-12|Wohlfarth, Klaus|Device for height adjustment|
    ITTO20110434A1|2011-05-16|2012-11-17|Sistemi Sospensioni Spa|MACPHERSON SUSPENSION FOR VEHICLE INCLUDING A DEVICE TO ADJUST THE HEIGHT OF THE GROUND VEHICLE BODY|
    JP5985333B2|2012-09-25|2016-09-06|株式会社ショーワ|Height adjustment device for motorcycles|
    ITMI20121683A1|2012-10-08|2014-04-09|Gabriele Bellani|SUSPENSION FOR VEHICLE WITH WHEELS|
    DE102013217028B4|2013-08-27|2018-09-20|Zf Friedrichshafen Ag|Vibration damper for a motor vehicle|EP3046783B1|2013-09-17|2019-04-17|Sistemi Sospensioni S.p.A.|Suspension strut for a motor vehicle with a height-adjustment device|
    US9751374B2|2014-09-22|2017-09-05|GM Global Technology Operations LLC|Vehicle and a height adjustment system for the vehicle|
    JP6788984B2|2016-03-28|2020-11-25|Ｋｙｂ株式会社|Buffer|
    US20190101178A1|2017-09-29|2019-04-04|Fox Factory, Inc.|Damper with hydraulically-adjustable preload and/or cross-over|
    DE102018214041A1|2018-08-21|2020-02-27|Bayerische Motoren Werke Aktiengesellschaft|Height-adjustable spring damper system for a vehicle|
    法律状态:
    2016-11-21| PLFP| Fee payment|Year of fee payment: 2 |
    2017-11-20| PLFP| Fee payment|Year of fee payment: 3 |
    2019-11-19| PLFP| Fee payment|Year of fee payment: 5 |
    2020-11-19| PLFP| Fee payment|Year of fee payment: 6 |
    2021-11-17| PLFP| Fee payment|Year of fee payment: 7 |
    优先权:
    申请号 | 申请日 | 专利标题
    ITTO20141011|2014-12-04|
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