JPH05180261A - Variable damping force type damper - Google Patents

Variable damping force type damper

Info

Publication number
JPH05180261A
JPH05180261A JP34596591A JP34596591A JPH05180261A JP H05180261 A JPH05180261 A JP H05180261A JP 34596591 A JP34596591 A JP 34596591A JP 34596591 A JP34596591 A JP 34596591A JP H05180261 A JPH05180261 A JP H05180261A
Authority
JP
Japan
Prior art keywords
poppet
passage
pressure
back pressure
damper
Prior art date
Legal status (The legal status 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 status listed.)
Pending
Application number
JP34596591A
Other languages
Japanese (ja)
Inventor
Yasuo Tsuyuki
保男 露木
Mitsuru Murata
充 村田
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
KYB Corp
Original Assignee
Kayaba Industry Co Ltd
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
Application filed by Kayaba Industry Co Ltd filed Critical Kayaba Industry Co Ltd
Priority to JP34596591A priority Critical patent/JPH05180261A/en
Publication of JPH05180261A publication Critical patent/JPH05180261A/en
Pending legal-status Critical Current

Links

Landscapes

  • Fluid-Damping Devices (AREA)

Abstract

PURPOSE:To adjust damping force of a damper of large capacity by a small solenoid valve. CONSTITUTION:A poppet 17 to open and close in accordance with flowing pressure of operating oil is provided in a passage to flow the operating oil in accordance with telescopic motion of a damper main body 1. Thereafter, the poppet 17 is energized in the shut-off direction by a spring 18. An orifice 19 one end of which is opened to the upstream of the poppet 17 and the other end of which is opened to a back pressure cell 22 shut-off from the passage 13 and an alternate passage 20 to connect the back pressure cell 22 to the passage 13 on the downstream side of the poppet 17 are provided. A solenoid comparative pressure control valve 21 to control pressure of this back pressure cell 22 in accordance with an input signal is provided.

Description

【発明の詳細な説明】Detailed Description of the Invention

【0001】[0001]

【産業上の利用分野】本発明は、発生減衰力を信号に応
じて制御する減衰力可変型ダンパの改良に関する。
BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a damping force variable damper for controlling a generated damping force according to a signal.

【0002】[0002]

【従来の技術】発生減衰力を信号に応じて制御する減衰
力可変型ダンパとして、例えばダンパ伸縮に伴って作動
油を流通させる通路に電磁弁を介装し、外部から送られ
る信号に応じて電磁弁が通路の流通抵抗を変えることで
発生減衰力を可変としたものが知られている。
2. Description of the Related Art As a damping force variable damper for controlling a generated damping force according to a signal, for example, a solenoid valve is provided in a passage through which hydraulic oil flows as the damper expands and contracts, and responds to a signal sent from the outside. It is known that the solenoid valve changes the flow resistance in the passage to change the generated damping force.

【0003】[0003]

【発明の課題】このようなダンパにおいては、流通する
作動油の全量が電磁弁を通過するため、大容量のダンパ
には大型の電磁弁を使用する必要があり、ダンパが大き
くなるのに伴って電磁弁も大型化し、その分コストが上
昇することは避けられなかった。
In such a damper, since the entire amount of hydraulic oil flowing through the damper passes through the solenoid valve, it is necessary to use a large solenoid valve for a damper having a large capacity, and the damper becomes larger. Therefore, it is inevitable that the solenoid valve will become larger and the cost will increase accordingly.

【0004】本発明は、上記問題を解決すべくなされた
もので、小型の電磁弁を用いて大容量のダンパの減衰力
調整を行うことを目的とする。
The present invention has been made to solve the above problems, and an object thereof is to adjust the damping force of a large-capacity damper by using a small solenoid valve.

【0005】[0005]

【課題を達成するための手段】本発明は、ダンパ本体の
伸縮に応じて作動油を流通させる通路と、この通路を作
動油の流通圧力に応じて開閉するポペットと、ポペット
を閉鎖方向に付勢するスプリングと、前記通路のポペッ
ト上流側とポペットに背圧を及ぼす背圧室とを連通する
オリフィスと、背圧室を前記通路のポペット下流側に接
続する迂回通路と、背圧室の圧力を入力信号に応じて制
御する電磁比例圧力制御弁とを備えている。
SUMMARY OF THE INVENTION According to the present invention, there is provided a passage through which hydraulic oil flows according to expansion and contraction of a damper main body, a poppet that opens and closes this passage according to circulating pressure of hydraulic oil, and a poppet in a closing direction. A biasing spring, an orifice that connects the poppet upstream side of the passage with a back pressure chamber that exerts a back pressure on the poppet, a bypass passage that connects the back pressure chamber to the poppet downstream side of the passage, and the pressure of the back pressure chamber. And an electromagnetic proportional pressure control valve for controlling the control signal according to an input signal.

【0006】[0006]

【作用】作動油の流通流量が少ない時は、作動油はオリ
フィスと電磁比例圧力制御弁とを介して迂回通路を流通
し、ダンパは電磁比例圧力制御弁の制御圧力に対応した
減衰力を発生させる。
[Operation] When the flow rate of the hydraulic oil is small, the hydraulic oil flows through the bypass passage through the orifice and the electromagnetic proportional pressure control valve, and the damper generates a damping force corresponding to the control pressure of the electromagnetic proportional pressure control valve. Let

【0007】迂回通路の流量が増加するとオリフィス前
後の圧力差が上昇し、この圧力差によりポペットがスプ
リングに抗してリフトし、作動油はポペットによって開
かれた通路を介して流通する。この場合のダンパの発生
減衰力はポペットのリフト量に対応して変化するが、こ
のリフト量はポペットに作用する背圧に対応して変化
し、背圧は電磁比例圧力制御弁の制御圧力に応じて変化
する。つまり、この場合もダンパの発生減衰力は電磁比
例圧力制御弁の制御圧力に対応して変化するので、小流
量の電磁比例圧力制御弁を用いて大容量のダンパの発生
減衰力を制御できる。
When the flow rate in the bypass passage increases, the pressure difference before and after the orifice rises, the pressure difference lifts the poppet against the spring, and the hydraulic oil flows through the passage opened by the poppet. In this case, the damping force generated by the damper changes according to the lift amount of the poppet, but this lift amount changes according to the back pressure acting on the poppet, and the back pressure becomes the control pressure of the electromagnetic proportional pressure control valve. Change accordingly. That is, also in this case, the damping force generated by the damper changes in accordance with the control pressure of the electromagnetic proportional pressure control valve, so that the damping force generated by the large capacity damper can be controlled using the small flow rate electromagnetic proportional pressure control valve.

【0008】[0008]

【実施例】図1及び図2に本発明の実施例を示す。1 and 2 show an embodiment of the present invention.

【0009】図1において、1はダンパ本体であり、シ
リンダ2にピストン3を摺動自由に収装し、ピストン3
に結合するピストンロッド4がシリンダ1から軸方向に
突出する。
In FIG. 1, reference numeral 1 is a damper body, in which a piston 3 is slidably housed in a cylinder 2 and
A piston rod 4 connected to the cylinder 1 projects axially from the cylinder 1.

【0010】シリンダ1の内部はピストン3によりピス
トンロッド4側の油室5と反対側の油室6に画成され
る。
The interior of the cylinder 1 is defined by a piston 3 into an oil chamber 5 on the piston rod 4 side and an oil chamber 6 on the opposite side.

【0011】ピストン3には油室6から油室5への作動
油の流通のみを許容するチェック弁7が設けられる。ま
た、シリンダ1の外側にはアウタチューブ8が同軸的に
設けられ、これらの間の環状隙間にシリンダ1内の油量
変動を補償すべく油面上方に空気を密封した油溜室9が
設けられる。シリンダ1の底部には油溜室9から油室6
への作動油の流通のみを許容するチェック弁10が設け
られる。
The piston 3 is provided with a check valve 7 which allows only the flow of hydraulic oil from the oil chamber 6 to the oil chamber 5. Further, an outer tube 8 is coaxially provided outside the cylinder 1, and an oil reservoir chamber 9 in which air is sealed above the oil surface is provided in an annular gap between the outer tube 8 and the cylinder 1 to compensate for fluctuations in the amount of oil in the cylinder 1. Be done. The oil chamber 9 to the oil chamber 6 are provided at the bottom of the cylinder 1.
A check valve 10 is provided that allows only the flow of hydraulic oil to and from it.

【0012】一方、油室5はロジック弁12を備えた通
路13を介して油溜室9に接続される。
On the other hand, the oil chamber 5 is connected to the oil reservoir 9 via a passage 13 having a logic valve 12.

【0013】ロジック弁12の詳細は図2に示される。
ロジック弁12はシリンダ1の先端に取り付けたケーシ
ング14に油室5に連通するポート15を形成し、ポー
ト15に形成したシート16にポペット17が着座する
もので、ポペット17の側方に通路13が開口する。油
室5の作動油はポペット17のリフトにより連通するポ
ート15と通路13を介して油溜室9に流入する。
Details of the logic valve 12 are shown in FIG.
The logic valve 12 is such that a port 15 communicating with the oil chamber 5 is formed in a casing 14 attached to the tip of the cylinder 1, and a poppet 17 is seated on a seat 16 formed in the port 15, and a passage 13 is provided on the side of the poppet 17. Opens. The hydraulic oil in the oil chamber 5 flows into the oil sump chamber 9 via the port 15 and the passage 13 which are communicated by the lift of the poppet 17.

【0014】ポペット17はスプリング18によりシー
ト16に向けて付勢される。また、ポペット17の先端
にはオリフィス19が形成される。このオリフィス19
は油室5とポペット16の後方に通路13から遮断する
ようにして形成された背圧室22とを連通し、ポペット
17に背圧を及ぼすようになっている。
The poppet 17 is biased toward the seat 16 by a spring 18. An orifice 19 is formed at the tip of the poppet 17. This orifice 19
Communicates the oil chamber 5 and a back pressure chamber 22 formed behind the poppet 16 so as to be blocked from the passage 13, and exerts a back pressure on the poppet 17.

【0015】背圧室22は途中に電磁比例圧力制御弁2
1を設けた迂回通路20を介してポペット17の下流側
の通路13に接続される。電磁比例圧力制御弁21は背
圧室22の圧力を入力信号に比例した圧力に制御するバ
ルブである。
The back pressure chamber 22 has an electromagnetic proportional pressure control valve 2 in the middle thereof.
It is connected to the passage 13 on the downstream side of the poppet 17 via the bypass passage 20 provided with 1. The electromagnetic proportional pressure control valve 21 is a valve that controls the pressure in the back pressure chamber 22 to a pressure proportional to the input signal.

【0016】次に作用を説明するこのダンパにおいては
ピストン3が伸長、収縮いずれに作動する場合も作動油
は油室5から油溜室9に流出する。
In this damper, the operation of which will be described below, the hydraulic oil flows from the oil chamber 5 to the oil reservoir 9 regardless of whether the piston 3 is extended or contracted.

【0017】また、ロジック弁12のポペット17には
油室5の圧力と、これに対抗する背圧室22の背圧並び
にスプリング7の圧力が作用し、これらの力のバランス
に応じてリフトする。すなわち、油室5の圧力と背圧室
22の背圧との間にはオリフィス19を流通する作動油
の圧力損失に相当する圧力差が生じ、この圧力差がオリ
フィス19の流量増加によりスプリング7の閉弁力を上
回ることでポペット17がリフトする。
The poppet 17 of the logic valve 12 is acted on by the pressure of the oil chamber 5, the back pressure of the back pressure chamber 22 and the pressure of the spring 7 which oppose it, and lifts according to the balance of these forces. .. That is, a pressure difference corresponding to the pressure loss of the working oil flowing through the orifice 19 is generated between the pressure of the oil chamber 5 and the back pressure of the back pressure chamber 22, and this pressure difference increases the flow rate of the orifice 19 to cause the spring 7 The poppet 17 is lifted when the valve closing force is exceeded.

【0018】したがって、ピストン3が低速で摺動する
場合には、ポペット17はリフトせず、油室5から油溜
室9への流出作動油はオリフィス19と電磁比例圧力制
御弁21を通って迂回通路20を流通する。電磁比例圧
力制御弁21はこの流出圧力を入力信号に対応して制御
し、ダンパはこの流出圧力に応じた減衰力を発生させ
る。つまり、ダンパの発生減衰力は電磁比例圧力制御弁
21により直接的に制御される。
Therefore, when the piston 3 slides at a low speed, the poppet 17 does not lift, and the hydraulic oil flowing out from the oil chamber 5 to the oil reservoir 9 passes through the orifice 19 and the electromagnetic proportional pressure control valve 21. It circulates in the bypass passage 20. The electromagnetic proportional pressure control valve 21 controls this outflow pressure in response to the input signal, and the damper generates a damping force according to this outflow pressure. That is, the damping force generated by the damper is directly controlled by the electromagnetic proportional pressure control valve 21.

【0019】一方、ピストン3が高速で摺動すると、オ
リフィス19の流量が増加し、油室5の圧力と背圧室2
2の背圧との圧力差の増大によりポペット17がスプリ
ング7に抗してリフトする。
On the other hand, when the piston 3 slides at a high speed, the flow rate of the orifice 19 increases and the pressure in the oil chamber 5 and the back pressure chamber 2 increase.
The poppet 17 lifts against the spring 7 due to the increase in the pressure difference from the back pressure of 2.

【0020】これにより、油室5の作動油はポペット1
7の周囲を通って通路13に流出する。この状態での発
生減衰力はポペット17のリフト量により決まるが、こ
のリフト量は次のような特性を持つ。
As a result, the hydraulic oil in the oil chamber 5 is the poppet 1
It flows through the periphery of 7 into the passage 13. The damping force generated in this state is determined by the lift amount of the poppet 17, and this lift amount has the following characteristics.

【0021】すなわち、電磁比例圧力制御弁21の制御
圧力を低下させると、オリフィス19の流量が増え、油
室5の圧力とポペット17の背圧との圧力差が増大する
ためにポペット17のリフト量は増大する。
That is, when the control pressure of the electromagnetic proportional pressure control valve 21 is lowered, the flow rate of the orifice 19 increases and the pressure difference between the pressure of the oil chamber 5 and the back pressure of the poppet 17 increases, so that the lift of the poppet 17 is increased. The quantity increases.

【0022】逆に、電磁比例圧力制御弁21の制御圧力
を上昇させると、オリフィス19の流量が減少し、ポペ
ット17のリフト量は小さくなる。
On the contrary, when the control pressure of the electromagnetic proportional pressure control valve 21 is increased, the flow rate of the orifice 19 is decreased and the lift amount of the poppet 17 is decreased.

【0023】したがって、ポペット17がリフトして油
室5の作動油が主としてロジック弁12を経由して通路
13へ流れる場合であってもダンパの発生減衰力は電磁
圧力制御弁21により間接的に制御されるのであり、油
室5の圧力は電磁比例圧力制御弁21の制御圧力にオリ
フィス19の圧力損失分を加えた圧力に保持される。
Therefore, even when the poppet 17 is lifted and the hydraulic oil in the oil chamber 5 mainly flows to the passage 13 via the logic valve 12, the damping force generated by the damper is indirectly controlled by the electromagnetic pressure control valve 21. The pressure in the oil chamber 5 is maintained at the pressure obtained by adding the pressure loss of the orifice 19 to the control pressure of the electromagnetic proportional pressure control valve 21.

【0024】このようにして、電磁圧力制御弁21への
入力信号によりダンパの発生減衰力を任意に変化させる
ことができる。また、油室5と油溜室9の間に大流量が
流れる時でも流量の大半はロジック弁12を経由し、電
磁圧力制御弁21を経由する流量は少量である。したが
って、ダンパ本体1の容量に関係なく、電磁比例圧力制
御弁21は小容量でよい。
In this way, the generated damping force of the damper can be arbitrarily changed by the input signal to the electromagnetic pressure control valve 21. Further, even when a large flow rate flows between the oil chamber 5 and the oil reservoir chamber 9, most of the flow rate passes through the logic valve 12 and the flow rate through the electromagnetic pressure control valve 21 is small. Therefore, the electromagnetic proportional pressure control valve 21 may have a small capacity regardless of the capacity of the damper body 1.

【0025】[0025]

【発明の効果】以上のように本発明は、ダンパの伸縮に
伴う流通作動油の通路を流通圧力に応じて開閉するポペ
ットを設け、ポペットの上流側とポペットに背圧を及ぼ
す背圧室とをオリフィスで連通し、背圧室を電磁比例圧
力制御弁を介してポペットの下流側に接続したので、電
磁比例圧力制御弁の制御圧力に応じてポペットのリフト
量が変化し、リフト量に応じた減衰力が発生する。
As described above, according to the present invention, the poppet for opening and closing the passage of the circulating hydraulic fluid according to the expansion and contraction of the damper is provided in accordance with the circulating pressure, and the upstream side of the poppet and the back pressure chamber for exerting a back pressure on the poppet are provided. , And the back pressure chamber was connected to the downstream side of the poppet via the electromagnetic proportional pressure control valve, so the lift amount of the poppet changes according to the control pressure of the electromagnetic proportional pressure control valve, and it depends on the lift amount. A damping force is generated.

【0026】このため、小流量の電磁比例圧力制御弁を
用いて大容量ダンパの発生減衰力を制御することがで
き、減衰力可変型ダンパの製造コストを低減する効果が
ある。
Therefore, the generated damping force of the large capacity damper can be controlled using the small flow rate electromagnetic proportional pressure control valve, which has the effect of reducing the manufacturing cost of the damping force variable damper.

【図面の簡単な説明】[Brief description of drawings]

【図1】本発明の実施例を示す減衰力調整式ダンパの縦
断面図である。
FIG. 1 is a vertical cross-sectional view of a damping force adjustable damper showing an embodiment of the present invention.

【図2】図1の中のロジック弁の拡大図である。FIG. 2 is an enlarged view of the logic valve in FIG.

【符号の説明】[Explanation of symbols]

1 ダンパ本体 12 ロジック弁 13 通路 17 ポペット 18 スプリング 19 オリフィス 20 迂回通路 21 電磁比例圧力制御弁 22 背圧室 1 Damper Main Body 12 Logic Valve 13 Passage 17 Poppet 18 Spring 19 Orifice 20 Detour Passage 21 Electromagnetic Proportional Pressure Control Valve 22 Back Pressure Chamber

Claims (1)

【特許請求の範囲】[Claims] 【請求項1】 ダンパ本体の伸縮に応じて作動油を流通
させる通路と、この通路を作動油の流通圧力に応じて開
閉するポペットと、ポペットを閉鎖方向に付勢するスプ
リングと、前記通路のポペット上流側とポペットに背圧
を及ぼす背圧室とを連通するオリフィスと、背圧室を前
記通路のポペット下流側に接続する迂回通路と、背圧室
の圧力を入力信号に応じて制御する電磁比例圧力制御弁
とを備えたことを特徴とする減衰力可変型ダンパ。
1. A passage through which hydraulic oil flows in response to expansion and contraction of a damper body, a poppet that opens and closes this passage according to circulation pressure of hydraulic oil, a spring that biases the poppet in a closing direction, and a passage of the passage. An orifice that connects the upstream side of the poppet and a back pressure chamber that exerts a back pressure on the poppet, a bypass passage that connects the back pressure chamber to the downstream side of the poppet of the passage, and the pressure of the back pressure chamber is controlled according to an input signal. A damping force variable damper comprising an electromagnetic proportional pressure control valve.
JP34596591A 1991-12-27 1991-12-27 Variable damping force type damper Pending JPH05180261A (en)

Priority Applications (1)

Application Number Priority Date Filing Date Title
JP34596591A JPH05180261A (en) 1991-12-27 1991-12-27 Variable damping force type damper

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
JP34596591A JPH05180261A (en) 1991-12-27 1991-12-27 Variable damping force type damper

Publications (1)

Publication Number Publication Date
JPH05180261A true JPH05180261A (en) 1993-07-20

Family

ID=18380212

Family Applications (1)

Application Number Title Priority Date Filing Date
JP34596591A Pending JPH05180261A (en) 1991-12-27 1991-12-27 Variable damping force type damper

Country Status (1)

Country Link
JP (1) JPH05180261A (en)

Cited By (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2007177884A (en) * 2005-12-28 2007-07-12 Soki Hs Kk Hydraulic shock absorber for vehicle
JP2011185392A (en) * 2010-03-10 2011-09-22 Kyb Co Ltd Damping valve
JP2012013120A (en) * 2010-06-30 2012-01-19 Kyb Co Ltd Damping valve
JP2012013117A (en) * 2010-06-30 2012-01-19 Kyb Co Ltd Damping valve
JP2012013119A (en) * 2010-06-30 2012-01-19 Kyb Co Ltd Damping valve
JP2012013118A (en) * 2010-06-30 2012-01-19 Kyb Co Ltd Damping valve
CN102401068A (en) * 2010-06-30 2012-04-04 萱场工业株式会社 Orifice Valve
EP4071379A4 (en) * 2019-12-06 2023-03-01 Hitachi Astemo, Ltd. Shock absorber

Cited By (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2007177884A (en) * 2005-12-28 2007-07-12 Soki Hs Kk Hydraulic shock absorber for vehicle
JP2011185392A (en) * 2010-03-10 2011-09-22 Kyb Co Ltd Damping valve
JP2012013120A (en) * 2010-06-30 2012-01-19 Kyb Co Ltd Damping valve
JP2012013117A (en) * 2010-06-30 2012-01-19 Kyb Co Ltd Damping valve
JP2012013119A (en) * 2010-06-30 2012-01-19 Kyb Co Ltd Damping valve
JP2012013118A (en) * 2010-06-30 2012-01-19 Kyb Co Ltd Damping valve
CN102401068A (en) * 2010-06-30 2012-04-04 萱场工业株式会社 Orifice Valve
EP4071379A4 (en) * 2019-12-06 2023-03-01 Hitachi Astemo, Ltd. Shock absorber

Similar Documents

Publication Publication Date Title
KR100228152B1 (en) Hydraulic damper of damping force adjusting type
KR101453090B1 (en) Damping force adjusting hydraulic shock absorber
KR100745004B1 (en) Damping force adjustable hydraulic buffer
KR100204943B1 (en) Adjustable damping force hydrauric shockabsorber
JP4048512B2 (en) Damping force adjustable hydraulic shock absorber
US3795255A (en) Load control and holding valve
JPH0356334B2 (en)
JP2003166585A (en) Attenuating force adjustable hydraulic damper
KR20000052553A (en) Hydraulic damper of damping force adjusting type
JP3972276B2 (en) Damping force adjustable hydraulic shock absorber
JPH05180261A (en) Variable damping force type damper
JPH01216106A (en) Fluid safety brake valve gear
JP3338531B2 (en) Damping force adjustable damper
US6038957A (en) Control valves
US4345736A (en) Solenoid operated valve and dashpot assembly
US4542678A (en) Control arrangement for hydraulic motor
US3474708A (en) Valve assembly for fluid motors and the like
US4471940A (en) Dashpot assembly
JP4048507B2 (en) Damping force adjustable hydraulic shock absorber
JPH109327A (en) Damping force regulating type hydraulic shock absorber
JP3265523B2 (en) Damping force adjustable hydraulic shock absorber
CN100489358C (en) High differential pressure high accuracy cage type pressure regulating device
JP2001108125A (en) Valve device
US5156080A (en) Control valve for a hydraulic elevator
JP2001041272A (en) Damping force adjustment type hydraulic buffer