CN101550981A - Damping force adjustment type buffer - Google Patents

Damping force adjustment type buffer Download PDF

Info

Publication number
CN101550981A
CN101550981A CN 200910130681 CN200910130681A CN101550981A CN 101550981 A CN101550981 A CN 101550981A CN 200910130681 CN200910130681 CN 200910130681 CN 200910130681 A CN200910130681 A CN 200910130681A CN 101550981 A CN101550981 A CN 101550981A
Authority
CN
China
Prior art keywords
valve
pressure
damping force
chamber
portion
Prior art date
Application number
CN 200910130681
Other languages
Chinese (zh)
Inventor
中楯孝雄
根津隆
片山洋平
片山茂郎
矢部博行
Original Assignee
株式会社日立制作所
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Priority to JP093351/08 priority Critical
Priority to JP2008093351A priority patent/JP5120629B2/en
Priority to JP116213/08 priority
Priority to JP040780/09 priority
Application filed by 株式会社日立制作所 filed Critical 株式会社日立制作所
Publication of CN101550981A publication Critical patent/CN101550981A/en

Links

Abstract

The invention relates to a damping force adjustment type buffer, capable of preventing the response delay of a pressure control valve and the self-excited vibration of the valve. The buffer controls the flow of the oil liquor between a ring oil line (21) and an oil storage chamber (4) generated by the slide of an inner piston of a hydraulic cylinder by a back pressure main valve (27) and a pressure control valve (28) to generate damping force. The direct damping force is generated by the pressure control valve (28) and the inner pressure of a back pressure chamber (53) is adjusted to control the valve opening pressure of the main valve 927). A valve spring (57) is mounted between a valve (56) and a plunger (34) in the pressure control valve (28) and the weight of the valve (56) is fully less than the weight of the plunger (34) and the spring rigid of the valve spring (57) is higher than the spring rigid of the plunger spring (36). Thus the response of the valve (56) is increased and the response delay of the damping force control is prevented. In addition, the natural frequency of the valve (56) is increased therefore the generation of the self-excited vibration is prevented.

Description

衰减力调节式緩冲器 Damping force adjustable shock absorber

技术领域 FIELD

本发明涉及一种安装在汽车等车辆的悬架装置等的衰减力调节式緩沖器。 The present invention relates to a damping force of a suspension device installed in a vehicle such as automobile adjustable shock absorber.

背景技术 Background technique

安装于汽车的悬架装置的衰减力调节式緩沖器通常在封入了油液的液压缸内可滑动地嵌装有与活塞杆连结的活塞而将液压缸内分成两室,通过由节流孔、圆盘阀等构成的衰减力产生机构控制由液压缸内的活塞的滑动而产生的油液的流动,产生衰减力,另外,利用流量控制阀、压力控制阀等使衰减力产生机构的流通阻力发生变化,由此,调节衰减力。 Damping force adjustable shock absorber mounted on a suspension apparatus of an automobile is typically sealed in the oil hydraulic cylinder slidably fitted with a piston and the piston rod, which connects the hydraulic cylinder into two chambers, through the orifice damping force generating mechanism composed of a disc valve or the like to control the flow of oil from the hydraulic cylinder piston slidably generated, generates a damping force, Further, the use of the flow control valve, the pressure control valve so that the flow damping force generating mechanism resistance changes, thereby adjusting the damping force.

这种衰减力调节式緩冲器的结构如专利文献1所示,在衰减力产生机构即、圆盘阀的背部形成有背压室,将该背压室经由固定节流孔与上游侧的液压缸室连接,另外,经由压力控制阀(电磁阀)与下游侧的液压缸室连接。 This damping force adjustable shock absorber structure as shown in Patent Document 1, i.e., the back of the disc valve is formed with a back pressure chamber in the damping force generating mechanism, the back pressure chamber via the fixed orifice with the upstream side cylinder chamber is connected, further, via a pressure control valve (solenoid valve) is connected to the cylinder chamber on the downstream side.

才艮据这种结构,由于可通过压力控制阀直接调节油液的流通阻力,而且调节背压室的内压来调节圆盘阀的开阀压力,所以能够扩大衰减力特性的调节范围。 It was Gen this configuration, since the flow resistance of the oil can be directly adjusted by the pressure control valve, regulating the internal pressure of the back pressure chamber and to adjust the valve opening pressure of the disk valve, it is possible to extend the adjustment range of damping force characteristics.

但是,专利文献1所记载的衰减力调节式緩沖器存在以下问题。 However, the damping force in Patent Document 1 describes the following problem adjusting shock absorber. 例如,在衰减力调节式緩冲器安装于汽车等车辆的悬架控制装置、根据车辆的行驶状态利用来自控制器的控制信号执行衰减力控制的情况下,由于压力控制阀(电磁阀)的柱塞的惯性等而产生响应延迟,从而衰减力控制过量、或因压力控制阀的阀体的自激振动而产生噪音。 For example, in the damping force adjustable shock absorber attached to a vehicle such as a suspension control apparatus using a case of performing the damping force control signal from the controller controls the traveling state of the vehicle based on, since the pressure control valve (electromagnetic valve) the inertia of the plunger is generated a response delay, so as to control the damping force in excess, or self-excited vibration due to the pressure control valve and valve element of the generation of noise.

专利文献l:(日本)特开2001 - 12534号公报发明内容 Patent Document l :( Japanese) Laid-Open 2001-- No. 12534 DISCLOSURE OF THE INVENTION

本发明是鉴于所述问题点而开发的,其目的在于提供一种衰减力调节式缓沖器,该衰减力调节式緩沖器防止压力控制阀的响应延迟及阀体的自激振动的发生。 The present invention was developed in view of the above problems and its object is to provide a damping force adjustable shock absorber, the damping force adjustable shock absorber to prevent delay in response of the pressure control valve and valve element of self-excited vibration.

4为了解决所述课题,本发明的衰减力调节式緩沖器具备:液压缸,其被封入了流体;活塞,其可滑动地嵌装于该液压缸内;活塞杆,其一端连结于所述活塞而另一端向所述液压缸的外部延伸;压力控制阀,其对通过所述液压缸内所述活塞的滑动产生的流体的流动进行控制并产生衰减力,从而可调节开阀压力,其特征在于,所述压力控制阀具备:阀体、将该阀体向轴向一侧施力并调节开阀压力的柱塞、介于所述阀体和所述柱塞之间安装的阀弹簧、将所述柱塞或所述阀体向轴向另一侧施力的主弹簧,所述阀体的质量小于所述柱塞,所述阀弹簧的弹簧刚性高于所述主弹簧。 4 In order to solve the above problems, the damping force adjustable shock absorber according to the present invention includes: a hydraulic cylinder, which is sealed in a fluid; a piston slidably fitted in the hydraulic cylinder; a piston rod having one end connected to the the piston and the other end extending to the outside of the cylinder; pressure control valve controls the flow of the hydraulic cylinder by said sliding piston and generating a fluid damping force is generated, thereby adjusting the valve opening pressure, which characterized in that, the pressure control valve comprising: a valve body and adjusting the valve opening pressure of the plunger in the axial direction urging the side, mounted between a valve spring interposed between said plunger and said valve body the mass of the main spring urging the plunger of the valve body or the other side in the axial direction, said plunger is smaller than the valve body, the valve springs of higher rigidity than the primary spring.

根据本发明的衰减力调节式緩沖器,能够提高阀体的响应性,从而能够防止衰减力控制的响应延迟,另外,还能够提高阀体的固有频率,从而防止自激振动的发生。 The damping force adjustable shock absorber according to the present invention, it is possible to improve the responsiveness of the valve body, thereby preventing a response delay of the damping force control, in addition, also possible to increase the natural frequency of the valve body, thereby preventing self-excited vibration.

附图说明 BRIEF DESCRIPTION

图1是放大表示本发明第一实施方式的衰减力调节式液压緩冲器的衰减 FIG 1 is an enlarged damping force of the first embodiment of the present invention the hydraulic shock absorber of formula adjustable attenuator

力产生^M勾的纵向剖面图; Force generating longitudinal sectional view of the hook ^ M;

图2是表示图1所示的衰减力产生机构的压力控制阀的阀弹簧的正面图;图3是表示图1所示的衰减力产生机构的压力控制阀的阀弹簧的变形例 FIG 2 is a front view of the valve of the valve spring pressure damping force generating mechanism shown in FIG. 1 the control; FIG. 3 shows a modified embodiment of the pressure valve spring damping force generating mechanism shown in FIG. 1 the control valve

的正面图; Front view;

图4是本发明第一实施方式的衰减力调节式液压緩沖器的纵向剖面图;图5是放大表示本发明第二实施方式的衰减力调节式液压緩沖器的衰减 FIG 4 is a longitudinal sectional view of a first embodiment of a damping force adjustable hydraulic shock absorber of the present invention; Figure 5 is an enlarged view of a second embodiment of a damping force adjustable attenuator of the present invention the hydraulic shock absorber of formula

力调产生机构的压力控制阀部分的纵向剖面图; Adjusting the pressure force of the control means generating a longitudinal sectional view of the valve portion;

图6是放大表示本发明第二实施方式的变形例的压力控制阀部分的纵向 6 is an enlarged showing a pressure variation of the second embodiment of the present invention, a control valve portion of the longitudinal

剖面图; Cross-sectional view;

图7是放大表示本发明第二实施方式的其他变形例的压力控制阀部分的纵向剖面图; 7 is an enlarged longitudinal sectional view showing the valve portion of the pressure variation of the second embodiment of another embodiment of the present invention, a control;

图8是放大表示本发明第二实施方式的其他变形例的压力控制阀部分的纵向剖面图; FIG 8 is an enlarged longitudinal sectional view of the valve portion of the other pressure variation of the second embodiment of the present invention, a control;

图9是放大表示本发明第二实施方式的其他变形例的压力控制阀部分的纵向剖面图; FIG 9 is an enlarged longitudinal sectional view of the valve portion other pressure variation of the second embodiment of the present invention, a control;

图IO是放大表示本发明第二实施方式的其他变形例的压力控制阀部分的纵向剖面图;图ll是放大表示本发明第二实施方式的其他变形例的压力控制阀部分的 FIG IO is an enlarged longitudinal sectional view of the valve portion of the other pressure variation of the second embodiment of the present invention, a control; ll is an enlarged FIG other pressure variation of the second embodiment of the present invention, the control valve portion

纵向剖面图; Longitudinal sectional view;

图12是放大表示本发明的一实施方式的衰减力调节式液压緩冲器的压力控制阀的座面及座部的纵向剖面图; 12 is an enlarged vertical sectional view showing the seat portion of the seat surface and the valve damping force to an embodiment of the present invention, the hydraulic shock absorber of adjustable pressure control;

图13是表示本发明的一实施方式的衰减力调节式液压緩沖器的衰减力特性的曲线图; 13 is a damping force to an embodiment of the present invention to adjust the damping force characteristic graph type hydraulic shock absorber;

图14是放大表示本发明第三实施方式的衰减力调节式液压緩沖器的衰减力产生^4勾的压力控制阀部分的纵向剖面图。 FIG 14 is an enlarged damping force of the third embodiment of the present invention the damping force adjustable hydraulic shock absorber of formula ^ a longitudinal sectional view of the valve generating a pressure portion 4 of the hook control. 附图标记说明 REFERENCE NUMERALS

1衰减力调节式液压緩冲器(衰减力调节式緩冲器)2 液压釭 A damping force adjustable hydraulic shock absorber (damping force adjustable shock absorber) second hydraulic Gang

5 活塞 5 piston

6 活塞杆 6 piston rod

28 压力控制阀34 柱塞 A pressure control valve 34 of the plunger 28

36柱塞弹簧(主弹簧) 36 the plunger spring (main spring)

56 阀体 56 Body

57 阀弹簧 A valve spring 57

具体实施方式 Detailed ways

下面,参照附图,说明本发明的第一实施方式。 Referring to the drawings, a first embodiment of the present invention. 如图4所示,本实施方式的衰减力调节式液压緩冲器1 (衰减力调节式緩沖器)为在液压缸2的外侧设有外筒3的双层筒结构,在液压缸2和外筒3之间形成有储油室4。 Damping force adjustable hydraulic shock absorber, the present embodiment of FIG. 41 (damping force adjustable shock absorber) is provided with an outer cylinder 3 of the double tube structure in the outer cylinder 2, the hydraulic cylinder 2 and oil reservoir chamber 4 is formed between the outer cylinder. 在液压缸2内可滑动地嵌装有活塞5,通过该活塞5将液压缸2内分成液压缸上室2A和液压缸下室2B两室。 In the cylinder 2 is slidably fitted with a piston 5, by the cylinder piston 5 into an upper chamber 2A and a cylinder lower chamber 2B two chambers of the hydraulic cylinder 2. 活塞杆6的一端通过螺母7与活塞5连结,活塞杆6的另一端侧通过液压缸上室2A,穿通安装于液压缸2及外筒3的上端部的导杆8及油封9,并向液压缸2的外部延伸。 One end of the piston rod 6 the piston 5 by a nut 7 connected to the other end of the piston rod side chamber 6 by the hydraulic cylinder. 2A, through the cylinder 2 is attached to the outer cylinder and the guide bar 8 and the upper portion of the oil seal 93, and extending the outer cylinder 2. 在液压缸2的下端部设有划分液压缸下室2B和储油室4的底部阀(《一;^V":/) 10。 In the lower portion of the cylinder 2 is provided with a bottom dividing the cylinder lower chamber 2B and the reservoir valve chamber 4 ( "a; ^ V": /) 10.

活塞5中设有使液压缸上下室2A、 2B间连通的油路11、 12。 The piston 5 is provided with upper and lower chambers of the hydraulic cylinders 2A, 2B communication between the oil passage 11, 12. 另外,油路11中i殳有只允许油液从液压釭下室2B侧向液压缸上室侧2A流通的逆止阀13,另外,在油路12中设有圓盘阀14,该圆盘阀14在液压缸上室2A侧 Further, the oil passage 11 i Shu permitting only the oil chamber 2B side to side of the cylinder 2A to flow from lower hydraulic chamber Gang check valve 13, further, the disc valve 14 is provided in the oil passage 12, the circle chamber 2A side disk valve 14 on the hydraulic cylinder

6的油液的压力达到了规定压力时开阀,使油液向液压缸下室2B侧溢流。 6 the oil pressure reaches a predetermined valve opening pressure when the hydraulic oil overflowing the cylinder lower chamber 2B side.

在底部阀10中设有使液压缸下室2B和储油室4连通的油路15、 16。 Valve 10 is provided in the bottom of the hydraulic cylinder lower chamber 2B and the reservoir chamber 4 communicating passage 15, 16. 而且,在油路15中设有只允许油液从储油室4向液压缸下室2B侧流通的逆止阀17,另外,在油路16中设有圓盘阀18,该圆盘阀18在液压缸下室2B侧的油液的压力达到了规定压力时开阀,使油液向储油室4侧溢流。 Further, in the oil passage 15 is provided with a check valve allowing only flow of oil from the reservoir chamber 4 to the cylinder lower chamber 2B side 17, further, the disc valve 18 is provided in the oil passage 16, the valve disc 18 under the oil pressure of the cylinder chamber 2B side reaches a predetermined valve opening pressure when the oil reservoir 4 side toward the overflow chamber. 在液压缸2内封入有油液,在储油室4内封入有油液及气体。 In the cylinder 2 is filled with fluid, and a gas sealed within the fluid reservoir chamber 4.

在液压缸2的上下两端部经由密封部件19外嵌有隔离筒20,在液压缸2和隔离筒20之间形成有环状油路21 。 In the upper and lower ends of the hydraulic cylinder 2 via a tube fitted with a separator 19 of the outer seal member 20, annular oil passage 21 is formed between the cylinder 2 and the spacer tube 20. 环状油路21通过设于液压缸2的上端部附近的侧壁的油路22与液压缸上室2A连通。 Communication through the annular passage 21 2A passage provided in the cylinder sidewall 2 in the vicinity of the upper end portion of the cylinder 22 with the hydraulic chamber. 在隔离筒20的侧壁设有小径的开口23,另外,在外筒3的侧壁设有与开口23大致同心的大径的开口24,在外筒3的侧壁开口24安装有衰减力产生^L构25。 The sidewall spacer 20 is provided with a small diameter cylindrical opening 23, Further, the outer tube side wall 3 is provided with an opening 24 substantially concentric with the opening 23 of the large diameter of the side wall of the outer cylinder 24 is attached to an opening 3 of a damping force generating ^ 25 L-configuration.

参照图1~3,对衰减力产生机构25进行说明。 Referring to FIGS. 1 to 3, the damping force generating mechanism 25 will be described. 如图l所示,圆筒状的壳体26的一端部插入开口24并由焊接而固定。 As shown in FIG. L, a cylindrical end portion of the insertion opening 24 of the housing 26 is fixed by welding. 在壳体26内插入先导行口7卜)型(背压型)的主阀27及压力控制阀28 (电磁阀) 一体化的阀单元30,由螺母31固定。 Pilot line insertion opening in the housing 267 BU) Type (back pressure type) main valve 27 and a pressure control valve 28 (solenoid valve) integrated valve unit 30 is fixed by a nut 31.

阀单元30具备通过螺母31固定于壳体26的电磁铁壳体32。 The valve unit 30 includes a nut 31 fixed to the housing 32 of the housing 26 of the electromagnet. 在电磁铁壳体32的外侧端部沿轴向形成有导向孔33。 The outer end portion of the solenoid housing 32 has a guide hole 33 formed in the axial direction. 在导向孔33内,可滑动地引导柱塞34,且收纳有线圈35 (电磁铁)、作为主弹簧的柱塞弹簧36 (压缩线圈弹簧),铁芯37与电磁铁壳体32嵌合,且通过铆接将其固定于电磁铁壳体32,由此,将线圈35固定,且支承柱塞弹簧36的一端部。 In the guide hole 33, the plunger 34 is slidably guided and housed coil 35 (electromagnet), as the main spring 36, the plunger spring (compression coil spring), the iron core 32 fitted to the housing 37 and the electromagnet, and it is fixed by caulking to the solenoid housing 32, thereby fixing the coil 35, and an end portion of the plunger spring 36 is supported. 通电用的引线38与线圈35连接且延伸到外部。 The energization coil 35 is connected to the leads 38 and extend to the outside.

在电磁铁壳体32的内侧端部形成有与导向孔33同心的通路孔39,导向孔33和通路孔39经由小径的口40连通。 39 is formed, through the small diameter opening 39 communicating via holes 40 with a hole 33 concentric with the guide hole 33 and guide hole via the inside of the end portion 32 of the electromagnet housing. 在电;兹4失壳体32的内侧端部依次配置有底圆筒状的导向部件41及有底圆筒状的阀部件42,带台阶圓筒状的通路部件43的一端部插通阀部件42及导向部件41的底部,其前端部拧入通路孔39,将这些一体结合在一起。 Electrical; hereby inner end 32 of the housing 4 out sequentially disposed a bottomed cylindrical guide member 41 and a bottomed cylindrical valve member 42, an end portion of a stepped cylindrical passage member 43 is inserted through the valve the guide member 42 and bottom member 41, which is screwed into the distal portion of the via hole 39, to combine them integrally. 通路部件43的中间的大径部44嵌合于阀部件42,在阀部件42的内部形成有室45。 Intermediate passage member 43 is fitted to the large-diameter portion 44 of the valve member 42, with a chamber 45 formed within the valve member 42. 通路部件43的另一端部嵌合于隔离筒20的开口23,通路部件43内部的轴向油路46的一端部与环状油路21连通。 The other end of the passage member 43 is fitted into the partition cylinder 20 and opening 23, an end portion 21 communicates with the axial oil passage inside the annular passage member 46, 43. 在轴向通路46的中间部设有固定节流孔47 (导入节流孔)。 The intermediate portion 46 is provided in the axial passage 47 (introduction orifice) fixed orifice.

在阀部件42的底部设有多条油路49,在底部的外侧端面的油路49的外周侧突出有环状的阀座50。 A plurality of oil passages provided in the bottom 49 of the valve member 42, at the outside of the bottom end surface of the outer peripheral side of the oil passage 49 of the annular valve seat 50 protrudes. 在阀部件42和导向部件41之间,层叠有多个圆盘阀51 (主阀)的内周部被夹住,圓盘阀51的外周部落座在阀座50上。 Between the valve member 42 and the guide member 41, a plurality of stacked disk valve 51 (main valve) is sandwiched between the inner peripheral portion, the outer periphery of the disc valve tribal seat 51 in the valve seat 50. 另外,在圆盘阀51的背面紧固有环状的密封部件52,密封部件52液体密封且可滑动地嵌合于导向部件41的圆筒部的内周面,在导向部件41的内部形成有背压室53。 Further, an annular seal member 52 is fastened on the back surface of the disc valve 51, the seal member 52 liquid-tightly and slidably fitted in the guide member inner periphery of the cylindrical portion 41 is formed in the interior of the guide member 41 back pressure chamber 53. 而且,圆盘阀51受到油路49的油液的压力而挠曲,从阀座50离开(开阀), >火而4吏阀部件42内的室45与壳体26内的室48 (通过外筒3的开口24与储油室4连通)连通。 Further, the disc valve 51 by the oil pressure of the oil passage 49 and deflected away from the valve seat 50 (valve opening),> chamber within the housing chamber 45 and fire officials valve member 4 422 648 ( 3 through the opening 24 of the outer cylinder in communication with the reservoir chamber 4) communication. 而且,通过圆盘阀51和背压室53形成有先导型(背压型)的衰减阀,背压室53的内压作用在圓盘阀51的闭阀方向。 Further, there is a pilot type (back pressure type) damping valve, the back pressure chamber 53 in the valve closing pressure acting direction of the disc valve 51 is formed by the disc valve 51 and the back pressure chamber 53. 阀部件42的轴向油路46的固定节流孔47的上游侧经由设于通路部件43上的油路54与阀部件42内的室45连通,另夕卜,固定节流孔47的下游侧经由径方向油路55与背压室53连通。 The communication passage 42 axially valve member chamber on the upstream side of fixed orifice 46 provided in the passage 47 via the oil passage 54 and the valve member 42 on the inner member 4345, another Bu Xi, downstream of the fixed orifice 47 communication via the radial oil passage 55 side with the back pressure chamber 53.

在柱塞34的前端部在轴向可移动地支承有对口40进行开闭的阀体56,阀体56由阀弹簧57 (板簧)弹性支承。 In the front end portion of the plunger 34 is axially movably supported in the valve body 56 with a mouth 40 for opening and closing the valve body 56 is elastically supported by a valve spring 57 (leaf spring). 阀体56为由大径的头部58和小径的轴部59形成的多台阶形状,头部58突出有落座于导向孔33内的口40的周缘部的座面60的环状的座部61。 The valve body 56 by a multi-step shape of the head of the large-diameter portion 58 and small diameter shaft 59 is formed, the head 58 is seated in the port protrudes in the guide hole 33 of the annular seat surface 60 of the peripheral edge portion 40 of the seat portion 61. 另外,轴部59可滑动地插入贯通于柱塞34的中心部的导向孔62。 Further, the shaft portion 59 is slidably inserted through the guide hole 34 of the central portion 62 of the plunger.

另外,在阀体56的头部58的环状的座部61的内周附近与口40相对形成有与口40大致同径的凹部80,由此,大大减小落座于环状的座部61的座面60的前端部的径向的宽度。 Further, in the vicinity of the inner periphery of the annular valve body 56 of the head portion 58 of the seat 40 opposite the mouth 61 is formed with a recessed portion 40 of the mouth 80 is substantially the same diameter, thereby, greatly reducing seated on an annular seat portion the radial width of the front end portion 61 of the seat surface 60.

如图2所示,阀弹簧57在大致圆形的抵接部63设有阀孔63A,从抵接部63向柱塞34的直径方向延伸有脚部64。 As shown, the valve spring 57 abutting a substantially circular portion 63 provided with a valve bore. 63A, extending from the contact portion 63 in the radial direction of the plunger 34 has a leg 64 in 2. 而且,阀体56的轴部59插通阀孔63A,头部58抵接于抵接部63,脚部64的前端部抵接于向柱塞34的前端外周缘部突出的环状的弹簧座部65,且被柱塞34在轴向上可移动地支承。 Further, the shaft portion 59 of the valve body 56 is inserted through the valve bore. 63A, the head 58 abuts the abutment portion 63, the distal end portion of the leg 64 abuts the forward end portion of the outer periphery of the plunger 34 projecting annular spring the seat portion 65, and is supported by the plunger 34 is movable in the axial direction. 另外,如图3所示,阀弹簧57的脚部64也可以放射状地配置多个(图示的例中,等间隔三个)。 Further, as illustrated, the leg portion 64 of the valve spring 57 may be more than three radially arranged (in the illustrated embodiment, three intervals).

由口40和阀体56形成压力控制阀28,阀体56当口40内的油液的压力达到规定压力时开阀,其开阀压力根据柱塞弹簧36的弹簧力及电磁铁的推力即线圈35的通电电流进行调节。 When the valve opening 40 is formed by opening the pressure control valve 56 and the valve body 28, the oil pressure in the port 40 when the valve body 56 reaches the predetermined pressure, the valve opening pressure of the thrust spring force of the plunger spring 36 and the electromagnet coil, i.e. 35 energizing current is adjusted. 导向孔33经由形成于电磁铁壳体32的油路66与室48连通。 Guide hole 33 via a passage 66 formed in communication with the chamber 48 of the housing 32 of the electromagnet. 在柱塞34上设有使形成于其两端的室彼此连通的节流通路67,对其移动作用适度的衰减力。 The plunger 34 has formed thereon chamber communicate with each other across the throttle passage 67, moving its modest effect damping force.

阀弹簧57的弹簧刚性高于柱塞弹簧36的弹簧刚性,另外,阀体56的质量大大小于柱塞34的质量,将阀体56的固有频率设定为十分高。 A valve spring 57 is higher than the spring rate of the spring rigidity of the plunger spring 36, further, the quality of the valve body 56 is substantially less than the mass of the plunger 34, the natural frequency of the valve body 56 is set to be sufficiently high.

8接着,对如上构成的本实施方式的作用进行说明。 8 Next, the operation of embodiment of the present embodiment configured as described above will be described. 安装于汽车等车辆悬 Installed in vehicles such as cars hanging

架装置的衰减力调节式液压缓沖器1,其液压缸2侧连结于弹簧下侧,活塞杆6侧连结于弹簧上侧,另外,线圈35的引线38连结于控制器(未图示)。 Damping force adjustable hydraulic device frame buffer 1, which is connected to the hydraulic cylinder 2 side to the side at the spring, the piston rod 6 is connected to the upper side of the spring side, The coil 35 is connected to leads 38 to a controller (not shown) .

在活塞杆6的拉伸行程时,通过液压缸2内活塞5的移动,关闭活塞5的逆止阀13,在圆盘阀I4开阀前,液压釭上室2A側的油液^皮加压,通过油路22及环状油路21 ,从隔离筒20的开口23流向衰减力产生机构25的轴向油路46。 6 when the piston rod extension stroke by the piston 2 moves within the cylinder 5, the closing piston 13 of the check valve 5, the disk valve prior to valve opening I4, Gang hydraulic fluid chamber 2A side of the ^ Piga pressure, through the oil passage 22 and the annular oil passage 21, the opening 20 of the cartridge 23 from flowing to the isolation damping force generating mechanism 25 is an axial passage 46. 而且,在主阀27的圓盘阀51开阀前,油液通过固定节流孔47、通路孔39及口40,打开压力4空制阀28的阀体56,流向导向孔33,再通过油3各66及室48流向储油室4。 Further, before the main valve disk valve 51 opening valve 27, the oil through the fixed orifice 47, via hole 39 and the opening 40, the opening pressure of the valve body 564 of the air valve 28, the flow guide hole 33, and then through 3 each of the oil chambers 66 and 48 flows to the oil reservoir chamber 4. 另外,当阀部件42的室45内的压力达到圓盘阀51的开阀压力时,打开圓盘阀51,油液从轴向油路46的固定节流孔47的上游侧通过油3各54、油室45及油^各49流向室48。 Further, when the pressure in the chamber 42 of the valve member 45 reaches the valve opening pressure of the disk valve 51, the disc valve 51 is opened, fluid from the upstream side of fixed orifice 46 of the axial passage 47 through the oil each 3 54, 45 and the oil chamber 49 to the oil chamber 48 of each ^.

此时, <吏活塞5移动的部分的油液打开底部阀IO的逆止阀17,从储油室4流入液压缸下室2B。 In this case, <officials fluid portion of the piston 5 is moved to open the bottom valve IO check valve 17, flows into the cylinder lower chamber 2B 4 from the oil reservoir chamber. 另外,当液压缸上室2A的压力达到活塞5的圓盘阀14的开阀压力时,打开圆盘阀14,将液压缸上室2A的压力向液压缸下室2B溢流,由此,防止液压缸上室2A的压力过度上升。 Further, when the pressure on the cylinder chamber 2A reaches the valve opening pressure of the piston disk 14 of the valve 5, the disc valve 14 is opened, the pressure in the cylinder upper chamber 2A, 2B overflow to the hydraulic cylinder lower chamber, whereby, cylinder pressure chamber prevents an excessive increase 2A.

在活塞杆6的压缩行程时,通过液压缸2内活塞5的移动,打开活塞5的逆止阀13,关闭底部阀10的油路15上的逆止阀17,在圓盘阀18开阀前,活塞下室2B的油液流入液压缸上室2A,使活塞杆6侵入到液压缸2内的部分的油液从液压缸上室2A通过与上述拉伸行程时同样的路径流向储油室4。 The compression stroke when the piston rod 6, by moving the second piston within the cylinder 5, the opening 13 of the piston check valve 5, the bottom valve 10 to close the oil passage 17 on the check valve 15, the valve opening 18 in the disc valve before, the oil chamber 2B flows into the lower piston cylinder upper chamber 2A, the piston rod 6 intruding into the inner portion of the fluid from the second hydraulic cylinder on the cylinder chamber 2A through the oil flow path similar to the above-described extension stroke room 4. 另外,当液压缸下室2B内的压力达到底部阀10的圆盘阀18的开阀压力时,圆盘阀18打开,将液压缸下室2B的压力向〗诸油室4溢流,由此,防止液压缸下室2B的压力过度上升。 Further, when the pressure in the cylinder lower chamber 2B reaches the bottom of the valve when the valve opening pressure of the disk 18 is 10, the disc valve 18 is opened, the pressure in the cylinder lower chamber 2B to 4〗 various oil overflow chamber by this prevents the hydraulic cylinder lower chamber 2B to an excessive increase in pressure.

由此,在活塞杆6的伸缩行程时,且在主阀27开阀前(活塞速度低速区域),通过固定节流孔47及压力控制阀28产生衰减力,在主阅27开阀后(活塞速度高速区域),根据其开度产生衰减力。 Accordingly, when the piston rod 6 of the telescopic stroke, the main valve and before opening the valve 27 (low piston speed region), through the fixed orifice 47 and the pressure generating damping force control valve 28, 27 after the main valve opening reading ( high piston speed region), generates a damping force according to its degree of opening. 另外,通过向线圈35的通电电流调节压力控制阀28的开阀压力,由此,不管活塞速度如何,都能够直接控制衰减力。 Further, by adjusting the energizing current to the coil 35 a pressure control valve opening pressure of valve 28, whereby, irrespective of the piston speed, damping force can be directly controlled. 此时,由于冲艮据压力控制阀28的开阀压力来调节背压室53的内压,所以能够同时调节主阀27的开阀压力,由此,能够扩大衰减力特性的调节范围。 In this case, according to Burgundy red valve opening pressure of the pressure control valve 28 to regulate the pressure of the back pressure chamber 53, it is possible to simultaneously adjust the valve opening pressure of the main valve 27, whereby the damping force adjusting range can be enlarged characteristic.

此时,压力控制阀28中的阀弹簧57的弹簧刚性被设定得高于柱塞弹簧36的弹黃刚性,另外,阀体56的质量被设定得大大小于柱塞34的质量,阀体56的固有频率被设定得十分高,因此不容易发生由柱塞34的惯性引起的响应延迟,防止过量而能够进行适宜的衰减力控制。 At this time, the pressure control valve spring 28. Valve spring 57 is set higher than the rigidity of the plunger spring rigidity of the spring 36, further, the quality of the valve body 56 is set to be much smaller than the mass of the plunger 34, the valve body 56 the natural frequency is set sufficiently high, and therefore does not easily occur due to the response delay of the inertia of the plunger 34, it is possible to prevent excessive damping force control appropriately. 另外,在口40的压力急剧上升的情况下,阀弹簧57挠曲,只有轻量的阀体56后退,在开阀后,柱塞34随之后退,因此,背压室53的压力不会因为压力控制阀28的开阀延迟而上升过度,能够进行稳定的衰减力控制。 Further, in the case of a sharp rise in the pressure port 40, a valve spring 57 flexes only lightweight valve element 56 back in the valve opening, the plunger 34 will reverse, therefore, the back pressure chamber 53 does not since the pressure control valve opening delay and valve 28 rises excessively, a stable damping force can be controlled. 另外,由于阀体56的固有频率被设定得很高,所以能够防止自激振动引起的噪音的产生及衰减力的不稳定。 Further, since the natural frequency of the valve element 56 is set high, it is possible to prevent the unstable self-excited vibration induced noise and the damping force.

另外,通过在压力控制阀28的阀体56的头部58设有环状的座部61,从而能够扩大开阀时的流路面积,能够扩大软侧(乂7卜側)的衰减力的调节范围。 Further, the pressure control valve 28 of the valve body 56 of the head 58 is provided with an annular seat portion 61, thereby expanding the flow passage area when the valve opening, the soft side damping force can be increased (BU qe 7 side) of the Adjustment range. 与此相反,例如特开平7-259918号公报记载的所示,作为压力控制阀,在使用针阀的情况下,在开阀时不能得到大的流路面积,因此,难以充分减小软侧的衰减力。 In contrast, as shown in Japanese Patent Publication No. 7-259918 described as a pressure control valve, in the case where the needle valve, when the valve opens can not obtain a large passage area, it is difficult to sufficiently reduce the soft side the damping force.

参照图12,'压力控制阀28在开阀时,利用从口40向导向孔33内流出的高速的油液的流动,在阀体56上作用闭阀方向的流体力。 Referring to FIG. 12, 'pressure control valve 28 when the valve opens, the high-speed flow of the oil flowing out from the opening 40 into the guide hole 33, the fluid forces acting on the valve body 56 in the valve closing direction. 但发生如下问题,由于该流体力,阀体56的开阀压力上升,软侧的衰减力增大,另外,流体力根据活塞速度及阀体56的开度发生变动,压力控制阀28的衰减力控制不稳定,另外,因阀体56振动而发生颤动。 However, a problem occurs, since the fluid force, the valve opening pressure of the valve body 56 is increased, the soft side damping force is increased further, the hydrodynamic force changes depending speed and the opening degree of the valve piston 56, the damping valve 28 of the pressure control power control is unstable, Further, due to vibration of the valve body 56 and fluttering. 因此,例如特开平11 -287281号公报记载的所示,在作为压力阀使用圆盘阀的情况下,存在这样的流体力影响的问题。 Thus, as shown in Japanese Patent Publication No. 11 -287281 described, in the case where the valve disc valve used as a pressure, a problem such stream impact strength.

与之相对,在环状的座部61的内周附近形成有凹部80,从而能够大大减小流体力作用于座部61的前端部的受压面积A,减轻流体力的影响,大大减小软侧的衰减力,另外,能够使压力控制阀28的衰减力控制稳定。 In contrast, a concave portion 80 is formed near the inner periphery of the annular seat portion 61, it is possible to greatly reduce the pressure-receiving area A of a fluid force to the distal portion of the seat portion 61, reducing the effect of fluid forces, greatly reduced soft side damping force, is also possible to control the damping force of the pressure control valve 28 is stable. 如上所述,希望在环状的座部61的内周部附近形成凹部80, ^f旦即佳乂人环状的座部61朝向凹部80的底面例如为锥度小的锥部,与使用圆盘阀相比,也能够减小颤动等问题。 As described above, it is desirable concave portion is formed in the vicinity of the inner circumferential portion of the annular portion 61 of the seat 80, ^ f qe good denier i.e. human annular seat portion 61 toward the bottom of the recess 80, for example, a small portion of the tapered cone, and circularly compared to the valve plate, it is possible to reduce the fibrillation problems.

图13表示衰减力调整式液压緩冲器1的衰减力特性。 13 shows damping force characteristics of the damping force control type hydraulic shock absorber 1. 如图13所示,衰减力调整式液压緩沖器的从软到硬的衰减力特性的调节范围R比目前的衰减力调整式液压缓冲器的调节范围r大。 As shown, the damping force control type hydraulic shock absorber is adjusted to the range R from the soft damping force characteristic of a hard damping force than the current-adjustable hydraulic shock absorber of a large adjustment range 13 r.

另外,在上述实施方式中,将主阀27及压力控制阀28—体化了的阀单元30配置在液压缸2的侧部的壳体26内,控制环状油路21和储油室4之间的油液的流动而产生衰减力,但也可以将阀单元30配置于活塞5或底部阀10上,适宜控制其油路的油液的流动,产生衰减力。 Further, in the above-described embodiment, the main valve and the pressure control valves 28- 27 of the body 30 of the valve unit arranged in the housing side portion 26 of the cylinder 2, annular oil passage 21 and the control oil chamber 4 fluid flow between the damping force is generated, but the valve unit 30 may be arranged on the piston 5 or the bottom of the valve 10, which is suitable for controlling the flow of the oil passage, the damping force is generated. 接着,参照图5~图11,对本发明的第二实施方式进行说明。 Next, with reference to FIGS. 5 to 11, a second embodiment of the present invention will be described. 另外,在 In addition,

以下的说明中,与上述第一实施方式相比较,相同的部分使用相同的符号,只对不同的部分详细进行-〖兌明。 The following description, as compared with the first embodiment, the same parts using the same reference numerals, and only different portions in detail - against 〖described.

图5扩大表示本实施方式的主要部分即衰减力产生机构25的压力控制阀28的部分。 FIG 5 showing enlarged main part of the embodiment, and the partial pressure of the damping mechanism 25 of the control valve 28 of the force. 如图5所示,本实施方式中,形成压力控制阀28的口40、阀体56的头部58、轴部59及座部61的直径分别比上述第一实施方式的大。 5, in this embodiment, a pressure control valve port 40, the head 56 of the valve body 58, the diameter of the shaft portion 59 and the seat 61 are larger than the first embodiment 28 of the embodiment. 另外,在阀体56上沿其轴向贯通有阀体连通3各70。 Further, the valve body 56 through the valve body along an axial communication with each of 70 3. 在柱塞34的导向孔62的后端部,管状的导向销7被1压入、固定,并向柱塞34的后部突出。 In the rear end portion of the guide hole 62 of the plunger 34, the tubular guide pin 7 is press-fit and fixed, and the rear portion of the plunger 34 protrudes. 在导向销71中沿其轴向贯通有连通路72。 In the axial direction thereof through the guide pin 71 in the communication path 72. 在铁芯37上与导向销71对置设有导向穴73,导向销71可滑动且液体密封地插入导向穴73,在导向穴73内形成有阀体背压室74。 On the core 37 and the opposite guide pin 71 provided with a guide hole 73, the guide pin 71 slidably and liquid-tightly inserted into the guide hole 73, there is formed a back pressure chamber 74 within the valve body guide hole 73.

另外,在压力控制阀28闭阀时,即阀体56的座部61落座于座面60的状态下,阀体背压室74经由导向销71的连通路72、柱塞34的导向孔62及阀体56的阀体连通路70与口40连通。 Further, the pressure control valve 28 when closing the valve, i.e., the seat portion 61 of the valve body 56 is seated on the seat surface 60 in the state, the back pressure valve chamber 74 through the guide pin 71 of the communication passage 72, the guide hole 62 of the plunger 34 and the valve body 56 of the communication passage 70 in communication with port 40. 因此,阀体56相对口40的受压面积为从座61内侧的面积减去轴部59的截面积后的面积。 Accordingly, the pressure receiving area of ​​the valve element 56 is opposite port 40 from the seat 61 inside the area minus the area of ​​the cross-sectional area of ​​the shaft portion 59.

由此,阀体56不仅能够通过座部61的直径,而且能够通过轴部59的直径调节相对于口40的受压面积,因此能够提高压力控制阀28的开阀特性的设定自由度,进而提高衰减力产生机构25的衰减力特性的设定自由度。 Accordingly, the diameter of the valve body 56 only through the seat portion 61, but also with respect to the pressure-receiving area of ​​the opening 40 by adjusting the diameter of the shaft portion 59, it is possible to improve the degree of freedom in setting the pressure control valve opening characteristic 28, thereby increasing the freedom in setting the damping force generating damping force characteristic mechanism 25.

例如,在^f吏口40的直径变大,阀体56开阀时的软侧的衰减力大大减小而进行设定的情况下,通过增大轴部59的直径,也能够减小阀体56的受压面积,因此不需要大的柱塞34的推力,就能够提高压力控制阀28的开阀压力,增大硬侧的衰减力。 For example, when the diameter of the ^ f official port 40 increases, the soft side of the damping force when the valve body 56 greatly decreases the valve opening setting case, by increasing the diameter of the shaft portion 59, the valve can be reduced pressure-receiving area of ​​the body 56, so no large thrust plunger 34, it is possible to improve the valve opening pressure of the pressure control valve 28, the hard side damping force is increased.

另夕卜,如图12所示,在本实施方式中,压力控制阀28的阀体58使座部61的内周部的凹部80的侧壁80A与座面61大致垂直,4吏外周侧形成为锥形状,相对于乂人口40向导向孔33内流出的油液的流动产生的流体力,大大减小座部61的前端部的受压面积A,且成为流体力难以作用的形状,因此,能够有效地减轻流体力的影响,大大减小软侧的衰减力,另外,还使压力控制阀28的衰减力控制稳定。 Another Bu Xi, 12, in the present embodiment, the pressure control valve 58 causes the valve 28 to the inner circumferential portion of the recessed portion 61 of the seat portion 80A and the side wall 61 substantially perpendicular to the seat surface 80, an outer circumferential side 4 officials formed in a tapered shape, the flow of the fluid force of fluid 40 flowing out of the population qe into the guide hole 33 for the production, greatly reducing the pressure receiving area a of the front end portion of the seat portion 61, and becomes difficult to effect the physical shape of the flow, Accordingly, it is possible to effectively reduce the effect of fluid forces, greatly reduce the damping force of the soft side, further, the pressure control valve 28 controls the damping force stability.

接着,参照图6-图11,说明上述第二实施方式的变形例。 Next, with reference to FIGS. 6-11, described a modification of the second embodiment. 图6所示的变形例在上述第二实施方式的基础上,使导向销71与柱塞34—体形成。 Modification shown in FIG 6 based on the above-described second embodiment, the guide pin 71 is formed with the plunger body 34-. 由此能够减少零件个数。 Whereby the number of parts can be reduced.

ii图7所示的变形例在上述第二实施方式的基础上,具有与铁芯37分体设置的导向孔73的有底圓筒状的导向部件75插入设于铁芯37(电磁铁的壳体)的安装穴76。 Modification shown in FIG. 7 ii based on the above-described second embodiment, the core has a guide hole 37 provided separately bottomed cylindrical guide member 73 is provided in the iron core 75 is inserted 37 (electromagnet housing) 76 mounting hole. 导向部件75使其底部与安装穴76的底部4氐接且在轴向上固定。 The guide member 75 so that the bottom of the mounting hole 76 of the bottom portion 4 connected to Di and fixed in the axial direction. 由此,导向部件75成为背压室形成部件,在柱塞34的外部形成阀体背压室74,且在安装穴76内只在径方向上进^"移动,由此,能够緩和导向销71和导向穴73的同心精度的要求。另外,也可以使导向部件75与图6所示的变形例进4于组合。 Thus, the guide member 75 be formed in the back pressure chamber member, a back pressure valve chamber 74 formed in the outer plunger 34, and is fed in the radial direction only in the mounting hole 76 ^ "movement, whereby the guide pin 71 can be alleviated and accuracy required concentric guide hole 73. Further, the guide member may be deformed as shown in FIG. 6 and 75 in combination into 4.

图8所示的变形例在上述第二实施方式的基础上,省略了导向销71,阀体的轴部59被延长,其延长部59A从柱塞34的后部突出,可滑动且液体密封地插入导向穴。 Modification of FIG. 8 on the basis of the above-described second embodiment, the guide pin 71 is omitted, the shaft portion of the valve body 59 is extended, which extension portion 59A projecting from the rear of the plunger 34 is slidably and liquid-tight inserted into the guide hole. 而且,通过轴部59的延长部59A,在导向穴73内形成有阀体背压室74。 Further, the shaft portion 59A through the extension portion 59, the back pressure chamber 74 has a valve body formed in the guide hole 73. 由此,由于口40和阀体背压室74通过阀体连通路70直接连通,所以能够抑制来自滑动部的泄漏。 Thus, since a direct communication passage 40 and the valve opening pressure chamber 74 is connected through the valve body 70, it is possible to suppress leakage from the sliding portion. 该情况下,如图9所示,由于为阀体56的头部和轴部作为不同的部件而彼此结合的结构,所以,作为轴部59能够使用管材,因此能够降低制造成本。 In this case, as shown in FIG. 9, since the head portion of the valve body 56 and a shaft portion as a different member bonded to each other, so that the shaft portion 59 can be used as a pipe material, the manufacturing cost can be reduced. 另外,也可以在图8及图9所示的变形例中组合图7所示的导向部件75。 Further, the guide may be shown in a seventh modification shown in FIG combination member 75 in FIG. 8 and FIG 9.

图10所示的变形例与上述第二实施方式相比,替代具有连通路72的导向销71而设有实心的导向销77。 Modification shown in FIG. 10 as compared with the second embodiment, instead of the communication passage 72 having a guide pin 71 and guide pin 77 is provided with a solid. 导向销77压入铁芯37的导向穴73并被固定,在柱塞34的导向孔62中可滑动且液体密封地被插入。 The guide pin 77 is pressed into the guide hole 73 of the core 37 and fixed slidably in the guide hole 62 and the plunger 34 is inserted liquid-tightly. 由此,阀体背压室74在柱塞34的导向孔62内形成,并通过阀体连通路70与口40连通。 Thus, the back pressure chamber 74 of the valve body guide hole 62 formed in the plunger 34 and the valve body 70 through the communication port 40 and communication path. 该情况下,在导向销77中设有如图5所示的导向销77的连通孔72所示贯通轴向的通路,从而使阀体背压室74与铁芯37的导向穴73连通,由此能够增大阀体背压室74的容积。 In this case, a through hole communicating the axial passage shown guide pins 77 as shown in FIG. 5 of the pin 72 in the guide 77, so that the back pressure chamber 74 and the valve body guide hole 73 of the core 37, the this is possible to increase the volume of the back pressure chamber 74 of the valve body.

另外,如图ll所示,导向销77也可以不压入导向穴73,而插入i殳于铁芯37上的安装穴76,使其底部与安装穴76的底部抵接并在轴向固定。 Further, as shown in FIG ll, the guide pin 77 may not be pressed into the guide hole 73, is inserted into the hole i Shu mounted on the core 37 of 76, its bottom and bottom mounting hole 76 and abuts axially secured . 由此,能够缓和导向销77和铁芯37侧的同心精度的要求。 This alleviates the guide pin 77 and the side core 37 of the concentric accuracy requirements.

接着,参照图14,说明本发明的第三实施方式。 Next, with reference to FIG. 14, a third embodiment of the present invention. 另外,在以下的说明中,对于上述第二实施方式,相同的部分标注相同的符号,只详细iJt明不同的部分。 In the following description, the above-described second embodiment, the same parts are denoted the same reference numerals and only different portions in detail iJt out. 另外,图14中为了便于说明,将溢流阀84、阀体87、杆88、柱塞34等错开表示成电磁铁为非通电时的状态即、图的上侧、和表示通电时的阀体87落座于座面60的状态即、图的下侧。 Further, for convenience of explanation in FIG. 14, the spill valve 84, the valve body 87, the rod 88, the plunger 34, etc. denotes the non-displaced state when energized i.e., upper side of the drawing into an electromagnet, showing the valve when energized and body 87 is seated on the seat surface 60, i.e., the lower side of FIG.

在本实施方式中,电磁铁壳体32的通路孔39及拧入通路孔39内的通路部件43的圆筒部43A被大径化。 In the present embodiment, the passage member 39 and the inner via hole 39 is screwed into the electromagnet housing 32 via holes 43 is a cylindrical portion 43A of a large diameter. 在圆筒部43A中插入具有大径部81A及小径部81B的带台阶圓筒状的口部件81的大径部81B。 Port member inserted in the cylindrical portion 43A has a stepped large diameter cylindrical portion 81A and a small diameter portion 81B of the large diameter portion 81 of 81B. 在口部件81形成有口40及座面60,在连通设于通路部件43的径方向的第二油路86及固定节流孔47的通路43B中插入小径部81B, 口40与径方向油路86及固定节流孔47连通。 In the mouth member 81 has a port 40 and the seat surface 60 is formed, the small diameter portion 81B is inserted into the second passage 43B and the oil passage 86 is provided in communication with a fixed orifice member 43 of the radial passage 47, the oil port 40 to the radial direction the communication passage 86 and the fixed orifice 47. 另外,在通路孔39及圆筒部43A内的口40的下游侧形成有阀室83,阀室83经由电;兹铁壳体32的第一油^各66与室48连通。 In addition, a 83, a valve chamber 83 the valve chamber via an electrical via hole 39 and the downstream side in the opening 43A of the cylindrical portion 40; iron hereby communicates the first oil housing 32 and the chamber 48 ^ 66 each. 在口部件81和通路部件43之间i殳有溢流阀84。 Between the port 81 and the passage member 43 i Shu relief valve member 84. 而且,阀室83和室48经由形成于口部件81上的油路85、溢流阀84及形成于圆筒部43A的第二油路86连通。 Further, the valve chamber 83 and the chamber 48 via an oil passage 85 formed on the opening member 81, the spill valve 84 and the cylindrical portion is formed communicating the second oil passage 86 43A of. 溢流阀84在阀室83的压力达到规定的开阀压力时开阀,将其压力向室48侧溢流。 Spill valve opening 84 when the pressure in the valve chamber 83 reaches a predetermined valve opening pressure to the pressure relief chamber 48 side. 在向线圈35通电时且阀体87的座部61从座面60离开时,阀体87从座面60和台阶部96的任一个离开。 When the seat portion 61 and the valve element 87 away from the seat surface 60 when the coil 35 is energized, a valve seat surface 60 away from any of the stepped portions 96 and 87. 该状态时,经由电^兹铁壳体32的第一油S各100主要与室48连通。 When this state, electrical communication via the first oil S ^ hereby iron housing 32 of each chamber 48 and 100 mainly. 由于第二油路86上具有溢流阀84,所以几乎不连通。 Since the spill valve 84 has a second oil passage 86, there is almost no communication. 另一方面,在不向线圈35通电时,座部件93与台阶部96 4氐4^,关闭第一油路100,只有第二油路86与室48连通。 On the other hand, when the coil 35 is not energized, the seat member 93 and the stepped portion 964 Di ^ 4, closing the first oil passage 100, only the second oil passage 86 communicates with the chamber 48.

在阀室83内设有具有小径部87A及大径部87B的大致凸形状的阀体87。 In the valve chamber 83 has a valve body 87 equipped with a substantially convex shape and the small-diameter portion 87A of the large-diameter portion 87B. 在阀体87中插入安装于柱塞34的空心的杆88的前端部。 Is inserted in the valve body 87 is attached to the distal end portion of the hollow rod 88 of the plunger 34. 在阀体87的小径部87A的前端部突出有离开、落座于口部件81的座面60的环状的座部61,由口40及阀体87构成压力控制阀28。 The small-diameter portion 87A at the front end portion of the valve element 87 protrudes away, seated on the annular seat surface 60 of the port member 81 of seat portion 61, the mouth 40 is constituted by a pressure control valve 87 and the valve 28. 而且,与上述第二实施方式相同,在座部61的内周部附近形成有凹部80,座部61的外周侧形成为锥状。 Further, the above-described second embodiment, and a concave portion 80, the outer peripheral side of the seat portion 61 is formed as a tapered seat portion 61 near the inner circumferential portion. 由此,减轻流体力的影响,大大减小软侧的衰减力,另外,还能够进行稳定的衰减力控制。 Thus, reducing the effect of fluid forces, greatly reduce the damping force of the soft side, further, it is possible to perform stable damping force control. 在阀体87上形成有轴向贯通的开口89,在开口89可滑动且液体密封地插入杆88的前端部。 In the valve body 87 is formed with an opening 89 extending axially therethrough, is slidable in the opening 89 and the liquid seal 88 inserted into the end of the lever. 在阀体87的大径部87B的端面外周缘部突出有环状的抵接部90。 The outer end surface of the peripheral edge portion of the large-diameter portion 87B of the valve element 87 has an annular projecting portion 90 abuts.

杆88贯通柱塞34并固定于柱塞34。 34 through the plunger rod 88 and is fixed to the plunger 34. 杆88的后端部可滑动且液体密封地插入形成于引导柱塞34的后端部的有底圆筒状的导向部件91的底部的导向穴73,在导向穴73内形成有阀体背压室74。 A rear end portion of the rod 88 slidably and liquid-tightly inserted into the bottomed cylindrical guide formed in the rear end portion of the guide member 34 of the plunger guide hole 73 of the base 91, the guide hole 73 formed in the valve body back pressure chamber 74. 阀体背压室74经由空心的杆88内的连通3各88A与阀体87的凹部80内连通。 74 communicates via the communication recess 87 and the valve body 88A 3 are each within the hollow rod 88 of the back pressure chamber 80 of the valve body.

在形成于杆88的前端侧的台阶部固定有挡圈92,在介于挡圏92和阀体87的抵接部92之间安装有环状的座部件93及阀弹簧(板簧)。 The step portion is formed at a front end side of the rod 88 of the retaining ring 92 is fixed, the valve member 93 and a spring 92 interposed between the mounting seat 92 and stop rings of the valve body 87 is an annular abutment portion (plate spring). 座部件93及阀弹簧94的外周部与抵接部90抵接,内周部与挡圈92抵接。 An outer circumferential portion of the valve seat member 93 and the spring 94 and the contact portion 90 comes into contact with the inner circumferential portion of the retaining ring 92 abuts. 而且,通过向线圈35通电,对柱塞34产生推力,如图14中的下侧所示,通过柱塞34的推力抵抗复位弹簧95的弹力,推压阀体87将座部61推到座面60。 Further, by the plunger 34 of the coil 35 is energized to produce thrust, as shown in the lower side in FIG. 14, against the force of the return spring 95 by the urging force of the plunger 34, urging valve element 87 to push the seat 61 to the seat portion surface 60. 此时,阀体87通过阀弹簧94弹性地支承于杆88上。 At this time, the valve body 87 by a valve spring 94 is elastically supported on the rod 88. 在介于口部件81和阀体87之间安装有作为主弹簧的复位弹簧95 (螺旋弹簧)。 Of between 81 and the valve body opening member 87 is attached to a return spring 95 (coil spring) as the main spring. 在通路孔39的底部侧的与阀体87的抵接部90相对的部位形成有台阶部96。 Forming the valve body portion 87 of the abutting portion 90 opposite to the side passage hole 39 at the bottom of the step portion 96. 而且,在线圈35非通电;兹时,如图14中的上侧所示,阀体87通过复位弹簧95的弹力后退,座部件93抵接于台阶部96,关闭油路66,通过座部93的节流孔97将阀室83 、室48间连通。 Further, in the non-energized coil 35; hereby time, the upper side in FIG. 14, the valve body 87 by the elastic force of the return spring 95 is retracted, the seat member 93 abuts the stepped portion 96, to close the oil passage 66, through the seat portion 97 the valve chamber 83, chamber 48 of the orifice 93. 阀弹簧94的弹簧刚性大于复位弹簧95的弹簧刚性,另外,阀体87的质量与柱塞34相比4艮小。 Spring valve spring 94 is more rigid than the spring rigidity of the return spring 95, further, the valve body 87 and the plunger 344 mass smaller than Gen.

才艮据这样的结构,如图14中的下侧所示,压力控制阀28通过使35通电,由此,利用柱塞34的推力抵抗复位弹簧95的弹力,推压阀体87,将座部61推到座面60,调节开阀压力。 According to such a configuration only Burgundy, as shown in the lower side 14, 28 by the pressure control valve 35 is energized, whereby the use of the thrust of the plunger 34 against the spring force of the return spring 95, pushing the valve body 87, the seat 61 to push the seat surface portion 60, a pressure regulating valve opening. 此时,与上述第一及第二实施方式相同,在口40的压力急剧上升的情况下,阀弹簧94挠曲,只是轻量的阀体87后退,开阀后,柱塞34随之后退,因此柱塞34的惯性引起的响应延迟不容易发生,防止颤动,能够进行适宜的衰减力控制。 In this case, the above-described first embodiment and second embodiment of the same, in the case of a sharp rise in the pressure port 40, a valve spring 94 flexes only lightweight valve element 87 backward, the valve opening, the plunger 34 backward along , the inertia of the plunger 34 so that the response delay caused is not likely to occur, preventing chattering, damping force can be appropriately controlled. 另外,能够控制压力控制阀28的开阀延迟引起的背压室53的压力过度上升,能够进行稳定的衰减力控制。 Further, it is possible to control the pressure control valve opening pressure chamber 28 of the pressure caused by delay 53 rises excessively, a stable damping force can be controlled. 另夕卜,能够抑制阀体87的自激振动引起的噪音的发生及衰减力的不稳定。 Another Bu Xi, can be suppressed and the occurrence of the unstable self-excited vibration damping force of the valve body 87 due to noise.

另外,与上述第二实施方式一样,在压力控制阀28闭阀时,即在阀体87的座部61落座于座面60的状态下,阀体背压室74经由杆88的连通路88A与口40连通,因此,阀体87相对于口40的受压面积为乂人座61内侧的面积减去杆88的截面积后的面积。 Further, the above-described embodiment, like the second embodiment, the pressure control valve 28 when the valve is closed, i.e. seated on the seat surface 60 in the state of the seat portion 61 of the valve body 87, the back pressure valve chamber 74 through the communication passage 88A of the rod 88 and the communication port 40, therefore, the valve body 87 relative to the pressure-receiving area of ​​the port 40 to the area of ​​the inner area qe seater 61 by subtracting the sectional area of ​​the rod 88. 由此,阀体87不仅能够通过座部61的直径,而且能够通过杆88的直径调节相对于口40的受压面积,因此能够提高压力控制阀28的开阀特性的设定自由度,进而能提高衰减力产生机构25的衰减力特性的设定的自由度。 Accordingly, the diameter of the valve body 87 only through the seat portion 61, but also with respect to the pressure-receiving area of ​​the opening 40 by adjusting the diameter of the rod 88, it is possible to improve the degree of freedom in setting the pressure control valve opening characteristics of the valve 28, and further can improve the degree of freedom in setting the damping force of the damping force characteristic mechanism 25.

在由于控制器发生故障、线圈35的断线等故障的发生而使柱塞34失去推力的情况下,如图14中的上侧所示,阀体87利用复位弹簧95的弹力而后退,座部件95抵接于通路孔39的台阶部96,关闭第一油路IOO,阀室83、室48间通过节流孔97连通。 Due to controller failure, such as disconnection fault occurs in the coil 35, the plunger 34 of the lower case of loss of thrust, the upper side in FIG. 14, the valve body 87 by the elastic force of the return spring 95 is retracted, the seat member 95 abuts the stepped portion 96 via hole 39, the IOO closing the first oil passage, the valve chamber 83, the communication between the chamber 48 through the orifice 97. 而且,阀室83的压力随着活塞速度的上升等而上升,当达到溢流阀84的开阀压时,溢流阀84开阀,将其压力向室48溢流。 Furthermore, the pressure rise in the valve chamber 83 with the piston speed rises, and the like, when it reaches the valve opening pressure relief valve 84, the relief valve 84 is opened, the pressure chamber 48 to overflow.

由此,根据节流孔97的流路面积及溢流阀84的溢流压力产生衰减力,由此,调节背压室53的压力即圓盘阀51的开阀压力,因此通过适宜设定这些的流路面积及溢流压力,即使在发生故障时,也能够产生适度的衰减力。 Accordingly, the damping force is generated according to the relief pressure and the flow passage area of ​​the orifice 97 of the relief valve 84, thereby adjusting the valve opening pressure of the back pressure chamber 53, i.e. the valve disc 51, and thus by appropriately setting the flow path area and pressure relief, even when a failure occurs, it is possible to generate an appropriate damping force.

14另外,如图13所示,扩大衰减力特性的调节范围的结果是,即使在硬时的衰减力相当大的情况下,在发生故障时,也不具有硬特性,而能够通过节流孔 Further 14, 13, to expand the range of adjustment of the damping force characteristic of a result, even in a hard damping force relatively large, when a fault occurs, not having a hard characteristic, it is possible through the orifice

97及溢流阀84产生适度的衰减力。 97 and relief valve 84 to generate an appropriate damping force. 例如,在发生故障时,由于具有硬和软之间的中间特性,所以能够抑制对车身的影响。 For example, when a failure occurs, since the intermediate characteristic between the hard and soft, it is possible to suppress the influence on the vehicle body.

Claims (10)

1、一种衰减力调节式缓冲器,具备:液压缸,其被封入了流体;活塞,其可滑动地嵌装于该液压缸内;活塞杆,其一端连结于所述活塞而另一端向所述液压缸的外部延伸;压力控制阀,其对通过所述液压缸内所述活塞的滑动产生的流体的流动进行控制并产生衰减力,从而可调节开阀压力,其特征在于,所述压力控制阀具备:阀体、将该阀体向轴向一侧施力并调节开阀压力的柱塞、介于所述阀体和所述柱塞之间安装的阀弹簧、将所述柱塞或所述阀体向轴向另一侧施力的主弹簧,所述阀体的质量小于所述柱塞,所述阀弹簧的弹簧刚性高于所述主弹簧。 A damping force adjustable shock absorber comprising: a hydraulic cylinder, which is sealed in a fluid; a piston slidably fitted in the hydraulic cylinder; a piston rod having one end connected to the other end of the piston extending the outer cylinder; pressure control valve controls the flow of the hydraulic cylinder by said sliding piston and generating a fluid damping force is generated, thereby adjusting the valve opening pressure, characterized in that said pressure control valve comprising: a valve body and adjusting the valve opening pressure of the plunger in the axial direction urging the side, mounted between a valve spring interposed between said valve body and said plunger, said column main spring urging the valve body of the plug or the other side in the axial direction, is less than the mass of the valve plunger, the valve springs of higher rigidity than the primary spring.
2、 如权利要求1所述的衰减力调节式緩冲器,其特征在于,所述阀体由所述柱塞沿其轴向且可滑动地引导。 2, as claimed in the damping force adjustable shock absorber according to claim 1, wherein said valve body is slidably guided in its axial direction by the plunger and.
3、 如权利要求1所述的衰减力调节式緩沖器,其特征在于,所述岡弹簧为板簧。 3. The damping force adjustable shock absorber as claimed in claim 1, wherein said spring is a leaf spring Gang.
4、 如权利要求1所述的衰减力调节式緩沖器,其特征在于,所述阀体具有对流路进行开闭的环状的座部,在该座部的内周部附近形成有凹部。 4, as claimed in claim 1, the damping force adjustable shock absorber, characterized in that the valve body has an annular flow path for opening and closing the seat portion, a concave portion is formed near the inner circumferential portion of the seat portion.
5、 如权利要求1所述的衰减力调节式緩冲器,其特征在于,具有:主阀,其对通过所述液压缸内的所述活塞的滑动产生的流体的流动进行控制并产生衰减力;背压室,其使该主阀向闭阀方向作用内压,将所述流体的流动的一部分导入所述背压室,通过所述压力控制阀调节所述背压室的内压,由此,控制所述主阀的开阀。 5, as claimed in the damping force adjustable shock absorber according to claim 1, further comprising: a main valve which controls flow through the sliding piston of the hydraulic cylinder and the fluid produced is attenuated force; back pressure chamber, so that the internal pressure of the main valve in the valve closing direction, a portion of the flow of fluid introduced into the back pressure chamber, the internal pressure of the back pressure regulating chamber by the pressure control valve, thus, the control valve opening the main valve.
6、 如权利要求1所述的衰减力调节式緩冲器,其特征在于,具有:主阀,其对通过所述液压缸内的所述活塞的滑动产生的流体的流动进行控制并产生衰减力;背压室,其使该主阀向闭阀方向作用内压;固定节流孔,其从所述主阀的上游侧向所述背压室侧导入流体,通过所述压力控制阀控制流体从所述背压室向所述主阀的下游侧的流动,调节所述背压室的内压。 6, as claimed in the damping force adjustable shock absorber according to claim 1, further comprising: a main valve which controls flow through the sliding piston of the hydraulic cylinder and the fluid produced is attenuated force; back pressure chamber, so that the internal pressure of the main valve in the valve closing direction; fixed orifice for introducing the fluid from the upstream side of the main valve chamber side of the back pressure control valve is controlled by the pressure the fluid flowing from the back pressure chamber to the downstream side of the main valve, the internal pressure of the back pressure regulating chamber.
7、 如权利要求6所述的衰减力调节式緩冲器,其特征在于,所述压力控制阀具备:阀体背压室,其设于所述阀体的背面侧;阀体连通路,其将所述阀体的上游侧和所述阀体背压室连通;电,兹铁,其调节所述柱塞的推力,控制所述阀体的开阀压,所述阀体相对于所述阀体背压室的受压面积小于相对于上游侧的受压面积。 7, as claimed in claim 6, the damping force adjustable shock absorber, characterized in that, the pressure control valve comprising: a valve body back pressure chamber, which is provided on the back side of the valve body; body communication path, which an upstream side of the valve body and the valve back pressure chamber; electrical, hereby iron, which regulates the thrust of the plunger, the control valve opening pressure of the valve body, the valve body with respect to said pressure-receiving area of ​​the valve body with respect to the back pressure chamber is smaller than the pressure receiving area of ​​the upstream side.
8、 如权利要求1所述的衰减力调节式緩沖器,其特征在于,所述主弹簧向所述阀体的开阀方向施力。 8, as claimed in the damping force adjustable shock absorber according to claim 1, characterized in that the main spring urges the valve opening direction of the valve body.
9、 如权利要求8所述的衰减力调节式緩沖器,其特征在于,所述压力控制阀在发生故障时,所述阀体利用所述主弹簧的施力向开阀方向移动,关闭向下游侧的第一流路,使流体经由节流孔再经由第二流路向下游侧流通。 9, damping force adjustable shock absorber as recited in claim 8, wherein said pressure control valve when a fault occurs, the valve body using a valve opening direction of the main spring biased to move, close to the the first flow path on the downstream side of the fluid flow toward the downstream side and then through the second channel through the orifice.
10、 如权利要求1所述的衰减力调节式緩沖器,其特征在于,所述压力控制阀配置在所述液压缸的側部。 10, as claimed in the damping force adjustable shock absorber according to claim 1, characterized in that the pressure control valve is disposed in a side portion of the hydraulic cylinder.
CN 200910130681 2008-03-31 2009-03-27 Damping force adjustment type buffer CN101550981A (en)

Priority Applications (4)

Application Number Priority Date Filing Date Title
JP093351/08 2008-03-31
JP2008093351A JP5120629B2 (en) 2008-03-31 2008-03-31 Damping force adjustable shock absorber and suspension control apparatus using the same
JP116213/08 2008-04-25
JP040780/09 2009-02-24

Publications (1)

Publication Number Publication Date
CN101550981A true CN101550981A (en) 2009-10-07

Family

ID=41155394

Family Applications (1)

Application Number Title Priority Date Filing Date
CN 200910130681 CN101550981A (en) 2008-03-31 2009-03-27 Damping force adjustment type buffer

Country Status (2)

Country Link
JP (1) JP5120629B2 (en)
CN (1) CN101550981A (en)

Cited By (11)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN102734371A (en) * 2011-03-31 2012-10-17 日立汽车系统株式会社 Attenuation force adjusting bumper
CN102808888A (en) * 2011-05-31 2012-12-05 日立汽车系统株式会社 Bumper
CN103154562A (en) * 2010-12-17 2013-06-12 Zf腓特烈斯哈芬股份公司 Adjustable damping valve device
CN103282220A (en) * 2011-01-31 2013-09-04 日立汽车系统株式会社 Suspension controller
CN103429929A (en) * 2011-03-02 2013-12-04 本田技研工业株式会社 Damper with variable damping force
CN104981639A (en) * 2013-02-15 2015-10-14 萱场工业株式会社 Solenoid valve
CN105008757A (en) * 2013-03-13 2015-10-28 萱场工业株式会社 Damping valve
CN105190085A (en) * 2013-03-13 2015-12-23 萱场工业株式会社 Damping valve
CN105531498A (en) * 2013-09-17 2016-04-27 Kyb株式会社 Damping valve
CN103883666B (en) * 2012-12-20 2017-03-01 Wp性能系统有限公司 A semi-active damping valve for a vibration damper arrangement
CN107923472A (en) * 2015-10-27 2018-04-17 日立汽车系统株式会社 Damping force adjustment-type shock absorber

Families Citing this family (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2011078317A1 (en) * 2009-12-25 2011-06-30 ヤマハ発動機株式会社 Shock absorber
JP5483007B2 (en) * 2010-01-29 2014-05-07 日立オートモティブシステムズ株式会社 Shock absorber
CN102822559A (en) * 2010-02-12 2012-12-12 日立汽车系统株式会社 Suspension device
WO2013042569A1 (en) 2011-09-21 2013-03-28 日立オートモティブシステムズ株式会社 Shock absorber
KR101464578B1 (en) * 2013-08-05 2014-11-24 주식회사 인팩 The Solenoid Of Shock Absorber System
JP6363414B2 (en) * 2014-07-11 2018-07-25 日立オートモティブシステムズ株式会社 Shock absorber
JP2016070429A (en) * 2014-09-30 2016-05-09 株式会社ショーワ Shock absorber
JP6482929B2 (en) * 2015-03-31 2019-03-13 株式会社ショーワ Shock absorber

Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPH09151980A (en) * 1995-11-27 1997-06-10 Oehlins Racing Ab Hydraulic shock absorber
US6182805B1 (en) * 1998-06-26 2001-02-06 Tokico Ltd. Damping force control type hydraulic shock absorber
US6371262B1 (en) * 1999-04-28 2002-04-16 Tokico Ltd. Damping force control type hydraulic shock absorber
CN1721729A (en) * 2004-05-25 2006-01-18 日产自动车株式会社 Hydraulic shock absorber

Family Cites Families (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPH05231464A (en) * 1992-02-17 1993-09-07 Kayaba Ind Co Ltd Hydraulic shock absorber
JP4288430B2 (en) * 1995-12-26 2009-07-01 株式会社日立製作所 Damping force adjustable hydraulic shock absorber
JP4161151B2 (en) * 1999-06-30 2008-10-08 株式会社日立製作所 Damping force adjustable hydraulic shock absorber
JP2007303545A (en) * 2006-05-11 2007-11-22 Kayaba Ind Co Ltd Shock absorber

Patent Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPH09151980A (en) * 1995-11-27 1997-06-10 Oehlins Racing Ab Hydraulic shock absorber
US6182805B1 (en) * 1998-06-26 2001-02-06 Tokico Ltd. Damping force control type hydraulic shock absorber
US6371262B1 (en) * 1999-04-28 2002-04-16 Tokico Ltd. Damping force control type hydraulic shock absorber
CN1721729A (en) * 2004-05-25 2006-01-18 日产自动车株式会社 Hydraulic shock absorber

Cited By (20)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN103154562A (en) * 2010-12-17 2013-06-12 Zf腓特烈斯哈芬股份公司 Adjustable damping valve device
CN103154562B (en) * 2010-12-17 2014-12-24 Zf腓特烈斯哈芬股份公司 Adjustable damping valve device
CN103282220B (en) * 2011-01-31 2016-07-06 日立汽车系统株式会社 Suspension control apparatus
CN103282220A (en) * 2011-01-31 2013-09-04 日立汽车系统株式会社 Suspension controller
CN103429929A (en) * 2011-03-02 2013-12-04 本田技研工业株式会社 Damper with variable damping force
CN103429929B (en) * 2011-03-02 2014-12-31 本田技研工业株式会社 Damper with variable damping force
CN102734371A (en) * 2011-03-31 2012-10-17 日立汽车系统株式会社 Attenuation force adjusting bumper
CN102734371B (en) * 2011-03-31 2016-08-03 日立汽车系统株式会社 Damping force control shock absorber
CN102808888A (en) * 2011-05-31 2012-12-05 日立汽车系统株式会社 Bumper
CN102808888B (en) * 2011-05-31 2016-06-01 日立汽车系统株式会社 buffer
CN105697636A (en) * 2011-05-31 2016-06-22 日立汽车系统株式会社 Shock absorber
CN103883666B (en) * 2012-12-20 2017-03-01 Wp性能系统有限公司 A semi-active damping valve for a vibration damper arrangement
CN104981639B (en) * 2013-02-15 2018-04-17 Kyb株式会社 The electromagnetic valve
CN104981639A (en) * 2013-02-15 2015-10-14 萱场工业株式会社 Solenoid valve
CN105008757A (en) * 2013-03-13 2015-10-28 萱场工业株式会社 Damping valve
CN105190085A (en) * 2013-03-13 2015-12-23 萱场工业株式会社 Damping valve
CN105008757B (en) * 2013-03-13 2017-03-15 Kyb株式会社 Damping valve
CN105531498A (en) * 2013-09-17 2016-04-27 Kyb株式会社 Damping valve
US9810280B2 (en) 2013-09-17 2017-11-07 Kyb Corporation Damping valve
CN107923472A (en) * 2015-10-27 2018-04-17 日立汽车系统株式会社 Damping force adjustment-type shock absorber

Also Published As

Publication number Publication date
JP5120629B2 (en) 2013-01-16
JP2009243636A (en) 2009-10-22

Similar Documents

Publication Publication Date Title
KR101078532B1 (en) Damping valve
US7694785B2 (en) Controllable damping force hydraulic shock absorber
US7743896B2 (en) Shock absorber having a continuously variable semi-active valve
US7441638B2 (en) Front fork
KR100835488B1 (en) Hydraulic shock absorber
US20030106753A1 (en) Damping force control type hydraulic shock absorber
US6981577B2 (en) Controlling damping force shock absorber
US7322449B2 (en) Hydraulic shock absorber
CN101290037B (en) Damping force adjustable fluid pressure shock absorber
EP1983212B1 (en) Fluid pressure shock absorber
CN102808888B (en) buffer
US8857582B2 (en) Hydraulic shock absorber
CN1871452A (en) Stroke dependent bypass
JP2000110881A (en) Two-stage type shock absorber
CN1721729A (en) Hydraulic shock absorber
JP2015064107A (en) Shock absorber having continuously variable valve with base line valving
JP4427066B2 (en) Damping force control valve and a shock absorber using the same
JP6305246B2 (en) Suspension control system
US8413774B2 (en) Shock absorber
JP2003166585A (en) Attenuating force adjustable hydraulic damper
KR100544488B1 (en) Damping force variable valve and shock absorber using same
JP4630760B2 (en) Valve and damper
US20030098209A1 (en) Controllable damping force hydraulic shock absorber
US20120048666A1 (en) Shock absorber
EP1975453A2 (en) Damping force adjustable fluid pressure shock absorber

Legal Events

Date Code Title Description
C06 Publication
C10 Entry into substantive examination
C02 Deemed withdrawal of patent application after publication (patent law 2001)