JPS61157835A - Accumulator - Google Patents
AccumulatorInfo
- Publication number
- JPS61157835A JPS61157835A JP59279219A JP27921984A JPS61157835A JP S61157835 A JPS61157835 A JP S61157835A JP 59279219 A JP59279219 A JP 59279219A JP 27921984 A JP27921984 A JP 27921984A JP S61157835 A JPS61157835 A JP S61157835A
- Authority
- JP
- Japan
- Prior art keywords
- chamber
- piston
- discharge port
- accumulator
- oil
- 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
Links
Classifications
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
- F16D48/00—External control of clutches
- F16D48/02—Control by fluid pressure
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
- F16D25/00—Fluid-actuated clutches
- F16D25/12—Details not specific to one of the before-mentioned types
- F16D25/14—Fluid pressure control
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
- F16D48/00—External control of clutches
- F16D48/02—Control by fluid pressure
- F16D2048/0203—Control by fluid pressure with an accumulator; Details thereof
Landscapes
- Engineering & Computer Science (AREA)
- General Engineering & Computer Science (AREA)
- Physics & Mathematics (AREA)
- Fluid Mechanics (AREA)
- Mechanical Engineering (AREA)
- Supply Devices, Intensifiers, Converters, And Telemotors (AREA)
- Hydraulic Clutches, Magnetic Clutches, Fluid Clutches, And Fluid Joints (AREA)
Abstract
Description
【発明の詳細な説明】 ［産業上の利用分野コ 本発明は、流体を蓄圧するアキュムレータに関する。[Detailed description of the invention] [Industrial application fields] The present invention relates to an accumulator that accumulates fluid pressure.
［従来の技術］
例えば第３図に示す如く、摩擦係合装ｊｆｉ１００の摩
擦係合要素１１０の係合および解放は油圧サーボ１２０
に作動油の供給および排出を行なうことにより行なわれ
、係合時急激な係合が行なわれないよう油圧サーボ１２
０に作動油を供給する油路１３０に作動油の供給流量を
制御するオリフィス２００および作動油を蓄圧して油圧
サーボ１２０に供給される油圧の上昇を緩かに行うアキ
ュムレータ１が設けられていた。従来のアキュムレータ
１はシリンダ室１１を郭定し、該シリンダ室１１内に流
体の給排を行なう給排口２０、前記シリンダ室１１内の
流体を排出する排出口３０を有したハウジング１０と、
第１の位置の側にアキュムレータ室Ａ１第２の位置の側
に排油室Ｂを郭定する隔壁４０、および該隔壁４０を前
記シリンダ室１１内で前記給排口２０を有する側の第１
の位置と前記排出口３０を有する側の第２の位置との間
に摺動自在に支持する筒状部５０からなるピストン６０
と、該ピストン６０を前記第１の位置へ向けて付勢する
ばね７０とからなり、摩擦係合要素１１０の係合達成時
間をさらに大きくする場合、アキュムレータ１のアキュ
ムレータ室Ａの貯圧容積を大きくするか、またはオリフ
ィス２００の径をさらに小さくするなどの手段が用いら
れていた。[Prior Art] For example, as shown in FIG.
This is done by supplying and discharging hydraulic oil to and from the hydraulic servo 12 to prevent sudden engagement.
An orifice 200 that controls the supply flow rate of hydraulic oil and an accumulator 1 that accumulates pressure of hydraulic oil and gently increases the hydraulic pressure supplied to the hydraulic servo 120 are provided in the oil passage 130 that supplies hydraulic oil to the hydraulic servo 120. . A conventional accumulator 1 includes a housing 10 defining a cylinder chamber 11, having a supply/discharge port 20 for supplying and discharging fluid into the cylinder chamber 11, and a discharge port 30 for discharging fluid from the cylinder chamber 11.
A partition wall 40 defines an accumulator chamber A on the first position side and an oil drain chamber B on the second position side, and the partition wall 40 is connected to a first partition wall 40 in the cylinder chamber 11 on the side having the supply/discharge port 20.
and a second position on the side having the discharge port 30.
and a spring 70 that biases the piston 60 toward the first position.If the time required to achieve engagement of the friction engagement element 110 is further increased, the storage pressure volume of the accumulator chamber A of the accumulator 1 is increased. Means such as increasing the diameter of the orifice 200 or further reducing the diameter of the orifice 200 have been used.
［発明が解決しようとする問題点］
上記に示す従来の技術では摩擦係合要素１１０の係合達
成時間を大きくするべくオリフィス２００の径を小さく
すると次の問題点を有していた。[Problems to be Solved by the Invention] The conventional technology described above has the following problem when the diameter of the orifice 200 is made smaller in order to increase the time required to achieve engagement of the frictional engagement element 110.
イ）小径のオリフィス２００を形成する生産性の限度が
あり、極めて小径のオリフィス２００は困難である。b) There is a limit to the productivity of forming an orifice 200 with a small diameter, and it is difficult to form an orifice 200 with an extremely small diameter.
口）摩擦係合要素１１０の係合完了後、オリフィス２０
０から油圧サーボ１２０内に作動油が到達するまでに発
生する作動油の漏れ（例えば図中回転シール材１３１ａ
、 １３１ｂによる漏れなど）にオリフィス２００によ
る供給油量が追従できず、油圧サーボ内の油圧が減圧し
、摩擦係合要素の係合が不安定になりやすい。(portion) After the engagement of the frictional engagement element 110 is completed, the orifice 20
Leakage of hydraulic oil that occurs from zero to hydraulic oil reaching inside the hydraulic servo 120 (for example, the rotary seal material 131a in the figure)
, 131b, etc.), the amount of oil supplied by the orifice 200 cannot follow, and the hydraulic pressure in the hydraulic servo decreases, which tends to make the engagement of the frictional engagement element unstable.
ハ）油温の変化による作動油の粘性変化により作動油の
オリフィス２００の流通抵抗が大幅に異なるため、油温
の変化によって摩擦係合要素１１０の係合作動が変動し
やすい。c) Since the flow resistance of the hydraulic oil through the orifice 200 changes significantly due to a change in the viscosity of the hydraulic oil due to a change in oil temperature, the engagement operation of the frictional engagement element 110 is likely to fluctuate due to a change in oil temperature.
二）オリフィス２００に異物が詰り易い。2) The orifice 200 is easily clogged with foreign matter.
またアキュムレータ１の７キユムレータ室Ａの貯圧容積
を大きくするとハウジング１０が大型化されアキュムレ
ータ１を含む装置が大きくされる問題点を有していた。Furthermore, if the pressure storage capacity of the seven accumulator chambers A of the accumulator 1 is increased, the housing 10 becomes larger and the device including the accumulator 1 becomes larger.
本発明の目的はアキュムレータの小型化およびアキュム
レータの蓄圧達成時間を長く設定することの容易なアキ
ュムレータの提供にある。An object of the present invention is to provide an accumulator that can be miniaturized and that allows the accumulator to easily set a long pressure accumulation time.
［問題点を解決するための手段］
本発明のアキュムレータは、上記問題点を解決すべく、
シリンダ室を郭定し、該シリンダ室内に流体の給排を行
なう給排口、前記シリンダ室内の流体を排出する排出口
を有したハウジングと、第１の位置の側にアキュムレー
タ室、第２の位置の側に排油室を郭定する隔壁、および
該隔壁を前記シリンダ室内で前記給排口を有する側の第
１の位置と前記排出口を有する側の第２の位置との間に
摺動自在に支持する筒状部からなるピストンと、該ピス
トンを前記第１の位置へ向けて付勢するばねとからなる
アキュムレータにおいて、前記シリンダ室の前記第２の
位置の側の側壁に前記ピストンが前記第１の位置の側に
位置するとき、前記給排口と連通する油路と前記排出口
が前記排油室を介して連通ずる排油室連通口を設け、前
記ピストンが前記第２の位置の側に位置する時、前記ピ
ストンの前記筒状部が前記排油室と前記排油室連通口を
塞ぐよう設けたことを構成とする。[Means for solving the problems] In order to solve the above problems, the accumulator of the present invention has the following features:
A housing defining a cylinder chamber, having a supply/discharge port for supplying and discharging fluid into the cylinder chamber, and a discharge port for discharging the fluid in the cylinder chamber, an accumulator chamber on the side of the first position, and a second housing. a partition wall defining an oil drain chamber on a side of the cylinder chamber, and the partition wall is slidable between a first position on the side having the supply/discharge port and a second position on the side having the discharge port in the cylinder chamber; In the accumulator, the accumulator includes a piston formed of a cylindrical portion that is movably supported, and a spring that urges the piston toward the first position, wherein the piston is attached to a side wall of the cylinder chamber on the side of the second position. is located on the side of the first position, an oil drain chamber communication port is provided through which an oil passage communicating with the supply/discharge port and the discharge port communicate with each other via the oil drain chamber, and the piston is located at the second position. The cylindrical portion of the piston is provided to close the oil drain chamber and the oil drain chamber communication port when the piston is located at the position.
［作用および発明の効果］
上記構成よりなる本発明のアキュムレータは、シリンダ
室の前記第２の位置の側の側壁に前記ピストンが前記第
１の位置の側に位置するとき、前記給排口と連通する油
路と前記排出口が前記排油室を介して連通ずる排油室連
通口を設け、前記ピストンが前記第２の位置の側に位置
する時、前記ピストンの前記筒状部が前記排油室と前記
排油室連通口とを塞ぐよう設けることによりアキュムレ
ータを大型化することなく、あるいは油圧サーボに供給
する作動油の供給流屋を制御するオリフィスを上述の問
題点の生じにくい比較的大きな径に設定してアキュムレ
ータ室の蓄圧達成時間を長く設定できる。[Operations and Effects of the Invention] The accumulator of the present invention having the above-mentioned configuration has an air supply/discharge port formed in the side wall of the cylinder chamber on the second position side when the piston is located on the first position side. An oil drain chamber communication port is provided through which an oil passage and the drain port communicate with each other via the oil drain chamber, and when the piston is located at the second position, the cylindrical portion of the piston By providing the oil drain chamber and the communication port of the oil drain chamber to be blocked, the accumulator does not need to be enlarged, or an orifice that controls the flow chamber of the hydraulic oil supplied to the hydraulic servo can be used to avoid the above-mentioned problems. By setting the diameter to a larger diameter, the time required to achieve pressure accumulation in the accumulator chamber can be set longer.
［実施例］
つぎに本発明のアキュムレータを図に示す実施例に基づ
き説明する。[Example] Next, an accumulator of the present invention will be explained based on an example shown in the drawings.
第１図は本発明のアキュムレータの第１実施例を示す概
略図である。FIG. 1 is a schematic diagram showing a first embodiment of an accumulator of the present invention.
自動変速機内に適用され、動力の伝達および遮断を行な
う摩擦係合装置１００の摩擦係合要素１１０の係合およ
び解放は油圧サーボ１２０に作動油を供給、排出を行な
うことによりピストン１４０が駆動されて行なわれ、油
圧サーボ１２０への作動油の給排を行なう油路１３０に
は油圧サーボ１２０への作動油の供給流量の制御を行な
うオリフィス２００と、油圧サーボ１２０に供給される
作動油を蓄圧し、摩擦係合要素１１０の係合および解放
を円滑に行なう本発明の適用を受けるアキュムレータ１
が設けられている。アキュムレータ１は内部に筒形状の
シリンダ室１１を形成し、シリンダ室１１の一方端でシ
リンダ室１１内と油路１３０とを連通し、シリンダ室１
１内に油圧サーボ１２０への作動油の給排とともに作動
油の給排を行なう給排口２０、シリンダ室１１の給排口
２０の開口側とは反対側の他方端に設けられ、シリンダ
室１１内の作動油を排出する排出口３０、および該排出
口３０側のシリンダ室１１の側壁に設けられ、前記給排
口２０同様油路１３０と連通する排油室連通口８０が設
けられたハウジング１０と、シリンダ室１１内で前記給
排口２０を有する側の図示矢印ａ１の位置の側に作動油
の蓄圧を行なうアキュムレータ室Ａおよび前記排出口３
０を有する側の図示矢印ｂ１の位置のがわに排油室Ｂを
郭定する隔壁４０．および咳隔Ｍ４０をシリンダ室１１
内の図示矢印ａ１の位置を図示矢印ｂ１の位置と間を摺
動自在に支持し、ピストン６０の隔壁４０が図示矢印ａ
１の位置の側に位置する時、前記排油室連通口８０と前
記排出口３０とが排油室Ｂを介して連通され、ピストン
６０の隔壁４０が図示矢印ｂ１の位置の側に位置する時
、排油室連通口８０の開口部が塞がれ排油室Ｂと排油室
連通口８０とが連通しないようランド５１を有する筒状
部５０からなるピストン６０と、該ピストン６０の隔壁
４０を常に図示矢印ａ１の位置の側へ向けて付勢するば
ね７０とからなり、油路１３０と排油室連通口８０とを
連通する油路８１には排油室連通口８０への流量を制御
するオリフィス８２が介されている。The friction engagement element 110 of the friction engagement device 100, which is applied in an automatic transmission and transmits and cuts off power, is engaged and released by supplying and discharging hydraulic fluid to a hydraulic servo 120, thereby driving the piston 140. The oil passage 130 that supplies and discharges hydraulic oil to the hydraulic servo 120 has an orifice 200 that controls the flow rate of hydraulic oil supplied to the hydraulic servo 120, and an orifice 200 that stores the hydraulic oil that is supplied to the hydraulic servo 120. Accumulator 1 to which the present invention is applied, which smoothly engages and disengages frictional engagement element 110
is provided. The accumulator 1 has a cylindrical cylinder chamber 11 formed therein, and communicates the inside of the cylinder chamber 11 with an oil passage 130 at one end of the cylinder chamber 11.
A supply/discharge port 20 for supplying and discharging hydraulic oil to and from the hydraulic servo 120 is provided in the cylinder chamber 11 at the other end of the cylinder chamber 11 opposite to the opening side of the supply/discharge port 20. 11, and an oil drain chamber communication port 80 which is provided on the side wall of the cylinder chamber 11 on the side of the discharge port 30 and communicates with the oil passage 130 like the supply/discharge port 20. A housing 10, an accumulator chamber A for accumulating hydraulic oil pressure on the side of the cylinder chamber 11 having the supply/discharge port 20 at the position indicated by the arrow a1 in the figure, and the discharge port 3.
A partition wall 40.0 defining an oil drain chamber B on the side indicated by the arrow b1 in the figure. and the gap M40 in the cylinder chamber 11
The partition wall 40 of the piston 60 is slidably supported between the position of the arrow a1 in the figure and the position of the arrow b1 in the figure, and the partition wall 40 of the piston 60 is
1, the oil drain chamber communication port 80 and the discharge port 30 communicate with each other via the oil drain chamber B, and the partition wall 40 of the piston 60 is located on the side of the illustrated arrow b1. At this time, the opening of the oil drain chamber communication port 80 is closed and the piston 60 is composed of a cylindrical portion 50 having a land 51 so that the oil drain chamber B and the oil drain chamber communication port 80 do not communicate with each other, and a partition wall of the piston 60. The oil passage 81 that communicates the oil passage 130 and the oil drain chamber communication port 80 has a flow rate to the oil drain chamber communication port 80. An orifice 82 is provided to control the flow.
上記よりなるアキュムレータ１は、摩擦係合装置１００
の摩擦係合要素１１０を係合すべく油路１３０に作動油
の供給を受けると、油圧サーボ１２０に作動油が蓄圧さ
れてピストン１４０が摩擦係合要素１１０側に摺動する
とともに、油路１３０゛より給排口２０を介してアキュ
ムレータ室Ａ内に作動油の蓄圧が開始される。ピストン
６０の隔壁４０が図示矢印ａ１の位置の側に位置する時
は排油室連通口８０は筒状部５０のランド５１に塞がれ
ないため油路１３０と排出口３０とは油路８１、オリフ
ィス８２、排油室連通口８０および排油室Ｂを介して連
通される。これによりオリフィス２００を介して油路１
３０に供給された作動油の一部は排出口３０より排出さ
れるため油圧サーボ１２０の蓄圧が遅延される。アキュ
ムレータ室Ａ内の作動油の蓄圧が大きくなりピストン６
０の隔壁４０が図示矢印ｂ１の位置の側に測置されると
排油室連通口８０は筒状部５０のランド５１に塞がれる
ため油路１３０に供給された作動油はアキュムレータ室
Ａおよび油圧サーボ１２０のみに供給され、摩擦係合要
素１１Ｇはピストン１４０に強く付勢され強固に係合さ
れる。The accumulator 1 configured as described above includes a friction engagement device 100
When hydraulic oil is supplied to the oil passage 130 to engage the frictional engagement element 110, hydraulic oil is accumulated in the hydraulic servo 120, the piston 140 slides toward the frictional engagement element 110, and the oil passage From 130°, pressure accumulation of hydraulic oil starts in the accumulator chamber A through the supply/discharge port 20. When the partition wall 40 of the piston 60 is located on the side indicated by the arrow a1 in the figure, the oil drain chamber communication port 80 is not blocked by the land 51 of the cylindrical portion 50, so the oil passage 130 and the discharge port 30 are connected to the oil passage 81. , an orifice 82, an oil drain chamber communication port 80, and an oil drain chamber B. This allows the oil passage 1 to pass through the orifice 200.
A part of the hydraulic oil supplied to the hydraulic servo 120 is discharged from the discharge port 30, so that the pressure accumulation in the hydraulic servo 120 is delayed. The pressure of the hydraulic oil in the accumulator chamber A increases and the piston 6
When the partition wall 40 of No. 0 is placed on the side indicated by the arrow b1 in the figure, the oil drain chamber communication port 80 is blocked by the land 51 of the cylindrical portion 50, so that the hydraulic oil supplied to the oil passage 130 flows into the accumulator chamber A. and is supplied only to the hydraulic servo 120, and the frictional engagement element 11G is strongly urged and firmly engaged with the piston 140.
第２図は本発明の第２実施例を示す概略図である。FIG. 2 is a schematic diagram showing a second embodiment of the present invention.
本実施例はシリンダ室１１とピストン６０の筒状部５０
の間に背圧室９０を設けるとともにピストン６０の隔壁
４０が図示（ａ）に示す如く図示矢印ａ１の位置の側に
位置する時、排油室Ｂと油路１３０とをオリフィス８２
Ａ 、 ８２Ｂを介して連通する２つの排油室連通口８
０Ａ 、 ８０Ｂおよび該排油連通口８０Ｂと背圧室９
０を連通ずる背圧ボート８０Ｃを設けたもので、排油室
連通口８０Ａ 、 ８０Ｂはピストン６０の隔壁４ｏが
図示矢印ａ１の位置から図示矢印ｂ１の位置に移動する
間に、図示矢印ａ１の位置の側の排油室連通口８０Ａが
筒状部５０のランド５１で塞がれると同時にオリフィス
８２Ａを介して油路１３０より供給される油圧が背圧ボ
ート８０Ｃを介して背圧室９０に背圧が作用し、排油室
連通０８０Ｂを介してのみ油路１３０と排出口３０とが
連通ずる。ピストン６０の隔壁４０が図示（ｂ）に示す
如く図示矢印ｂ１の位置の側に位置する時、排油室連通
口８０Ｂは筒状部５０のランド５１に塞がれるよう設け
られたものである。In this embodiment, the cylinder chamber 11 and the cylindrical portion 50 of the piston 60 are
A back pressure chamber 90 is provided between the oil drain chamber B and the oil passage 130, and when the partition wall 40 of the piston 60 is located on the side of the arrow a1 as shown in FIG.
Two oil drain chamber communication ports 8 communicating via A and 82B
0A, 80B and the drain oil communication port 80B and back pressure chamber 9
0 is provided, and the oil drain chamber communication ports 80A and 80B are provided with a back pressure boat 80C that communicates with the At the same time as the oil drain chamber communication port 80A on the position side is closed by the land 51 of the cylindrical portion 50, the hydraulic pressure supplied from the oil passage 130 via the orifice 82A is transferred to the back pressure chamber 90 via the back pressure boat 80C. Back pressure acts, and the oil passage 130 and the discharge port 30 communicate only through the oil drain chamber communication 080B. When the partition wall 40 of the piston 60 is located on the side indicated by the arrow b1 as shown in FIG. .
第１図は本発明の第１実施例を示す概略断面図、第２図
は本発明の第２実施例を示す概略断面図、第３図は従来
のアキュムレータを示す概略断面図である。
図中 １・・・アキュムレータ １０−・・ハウジング
１１・・・シリンダ室 ２０・・・給排口 ３０・・・
排出口 ４０・・・隔壁 ５０・・・筒状部 ５１・・
・ランド ６０−・・ピストン７０・・・ばね ８０．
８０＾、８０Ｂ・・・排油室連通口 ８１．１３０−・
・油路 ８２．２００・・・オリフィス ９０・・・背
圧室１００・・・摩擦係合袋＠ Ａ・・・アキュムレー
タ室Ｂ・・・排油室FIG. 1 is a schematic sectional view showing a first embodiment of the present invention, FIG. 2 is a schematic sectional view showing a second embodiment of the invention, and FIG. 3 is a schematic sectional view showing a conventional accumulator. In the figure 1...Accumulator 10-...Housing 11...Cylinder chamber 20...Inlet/discharge port 30...
Discharge port 40...Partition wall 50...Cylindrical part 51...
・Land 60-...Piston 70...Spring 80.
80^, 80B...Oil drain chamber communication port 81.130-.
・Oil passage 82.200... Orifice 90... Back pressure chamber 100... Friction engagement bag @ A... Accumulator chamber B... Oil drain chamber
Claims (1)
排を行なう給排口、前記シリンダ室内の流体を排出する
排出口を有したハウジングと、第１の位置の側にアキュ
ムレータ室、第２の位置の側に排油室を郭定する隔壁、
および該隔壁を前記シリンダ室内で前記給排口を有する
側の第１の位置と前記排出口を有する側の第２の位置と
の間に摺動自在に支持する筒状部からなるピストンと、
該ピストンを前記第１の位置へ向けて付勢するばねとか
らなるアキュムレータにおいて、 前記シリンダ室の前記第２の位置の側の側壁に前記ピス
トンが前記第１の位置の側に位置するとき、前記給排口
と連通する油路と前記排出口が前記排油室を介して連通
する排油室連通口を設け、前記ピストンが前記第２の位
置の側に位置する時、前記ピストンの前記筒状部が前記
排油室と前記排油室連通口を塞ぐよう設けたことを特徴
とするアキュムレータ。[Scope of Claims] 1) A housing defining a cylinder chamber, having a supply/discharge port for supplying and discharging fluid into the cylinder chamber, a discharge port for discharging the fluid in the cylinder chamber, and a housing in a first position. a bulkhead defining an accumulator chamber on the side and an oil drain chamber on the side of the second position;
and a piston comprising a cylindrical portion that slidably supports the partition wall between a first position on the side having the supply/discharge port and a second position on the side having the discharge port in the cylinder chamber;
and a spring that biases the piston toward the first position, when the piston is located on the side wall of the cylinder chamber on the second position side, when the piston is located on the first position side, An oil drain chamber communication port is provided through which an oil passage communicating with the supply/discharge port and the discharge port communicate with each other via the oil drain chamber, and when the piston is located on the second position side, the piston An accumulator characterized in that a cylindrical portion is provided to close the oil drain chamber and the oil drain chamber communication port.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP59279219A JPS61157835A (en) | 1984-12-28 | 1984-12-28 | Accumulator |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP59279219A JPS61157835A (en) | 1984-12-28 | 1984-12-28 | Accumulator |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| JPS61157835A true JPS61157835A (en) | 1986-07-17 |
Family
ID=17608085
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP59279219A Pending JPS61157835A (en) | 1984-12-28 | 1984-12-28 | Accumulator |
Country Status (1)
| Country | Link |
|---|---|
| JP (1) | JPS61157835A (en) |
Cited By (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| EP1353076A2 (en) * | 2002-04-11 | 2003-10-15 | A-Dec, Inc. | Control system for a chair |
| JP2014508374A (en) * | 2010-12-15 | 2014-04-03 | アーベーベー・テクノロジー・アーゲー | Storage module for hydraulic storage energy spring mechanism |
Citations (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPS57192628A (en) * | 1981-05-20 | 1982-11-26 | Daikin Mfg Co Ltd | Hydraulic modulator for clutch |
-
1984
- 1984-12-28 JP JP59279219A patent/JPS61157835A/en active Pending
Patent Citations (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPS57192628A (en) * | 1981-05-20 | 1982-11-26 | Daikin Mfg Co Ltd | Hydraulic modulator for clutch |
Cited By (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| EP1353076A2 (en) * | 2002-04-11 | 2003-10-15 | A-Dec, Inc. | Control system for a chair |
| EP1353076A3 (en) * | 2002-04-11 | 2006-09-13 | A-Dec, Inc. | Control system for a chair |
| JP2014508374A (en) * | 2010-12-15 | 2014-04-03 | アーベーベー・テクノロジー・アーゲー | Storage module for hydraulic storage energy spring mechanism |
| US9620302B2 (en) | 2010-12-15 | 2017-04-11 | Abb Schweiz Ag | Storage module for a hydraulic stored-energy spring mechanism |
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