JPS5973602A - Pressure compensating device for oil chamber on load bearing side of load bearing hydraulic cylinder - Google Patents
Pressure compensating device for oil chamber on load bearing side of load bearing hydraulic cylinderInfo
- Publication number
- JPS5973602A JPS5973602A JP18502382A JP18502382A JPS5973602A JP S5973602 A JPS5973602 A JP S5973602A JP 18502382 A JP18502382 A JP 18502382A JP 18502382 A JP18502382 A JP 18502382A JP S5973602 A JPS5973602 A JP S5973602A
- Authority
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- Japan
- Prior art keywords
- pressure
- oil
- load
- oil chamber
- hydraulic cylinder
- 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.)
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Abstract
Description
【発明の詳細な説明】
本発明は、負荷全担持する油圧シリンダの負荷担持側油
室の圧力補償装置に関するものである。DETAILED DESCRIPTION OF THE INVENTION The present invention relates to a pressure compensation device for a load-carrying side oil chamber of a hydraulic cylinder that carries a full load.
ｉ２
本発明が適用される油圧シリンダは、伸長動作側圧油室
と縮小動作側油呈全有しｃｎら両油呈の給排回路への作
動油の給排並びに給排停止を油圧制御装置で制御するこ
とで、伸縮駆動並びに負荷全担持した状態で停止するこ
とのできる油圧シリンダであり、これを第１図に基づき
より具体的に説明すると第１図において、油圧シリンダ
１は。i2 The hydraulic cylinder to which the present invention is applied has a pressure oil chamber on the extension side and an oil chamber on the contraction side. It is a hydraulic cylinder that can be controlled to extend and contract, and can be stopped while carrying a full load.This will be explained in more detail based on FIG. 1. In FIG. 1, a hydraulic cylinder 1 is shown.
シリンダ２Ｉ ピストンロッド３．およびピストンロッ
ド３基端に止着されシリンダ２内に油密摺動自在に嵌挿
さ′ｎたピストン４から構成されている。Cylinder 2I Piston rod 3. The piston 4 is fixed to the base end of the piston rod 3 and is slidably inserted into the cylinder 2 in an oil-tight manner.
前記ピストン４は、シリンダ２内全伸長動作９１Ｉｌ出
油室５と縮小動作側油室６に区画している。油圧シリン
ダ１の伸長動作側圧油室５および縮小動作５および縮小
動作側圧油Ｎ６に夫々接続された給排回路８および給排
回路９、油圧発生装置１０奢こ接続された供給回路１１
．および油槽１２に接続された排出回路１３０間に設け
らｎている。第１図の場合この油圧制御装置７は、四方
向三位置油圧切換升＆ ３
１４と曲記給排回路８に設けたカウンタバランスバルブ
（又はホールディングバルブ）１５で構成されている。The piston 4 is divided into an oil chamber 5 for full extension operation 91Il in the cylinder 2 and an oil chamber 6 for contraction operation. A supply/discharge circuit 8 and a supply/discharge circuit 9 connected to the extension operation side pressure oil chamber 5, the contraction operation 5, and the contraction operation side pressure oil N6 of the hydraulic cylinder 1, respectively, and the supply circuit 11 connected to the hydraulic pressure generator 10.
．． and a discharge circuit 130 connected to the oil tank 12. In the case of FIG. 1, this hydraulic control device 7 is composed of a four-way three-position hydraulic switching box &3 14 and a counterbalance valve (or holding valve) 15 provided in the recording supply/discharge circuit 8.
カウンタバランスバルブ（又ハホールディングバルブ）
１５は、四方向三位置油圧切換升１４から油圧シリンダ
１方向への作動油の流れは自由であるが１反対方向の流
れは給排回路９内の油圧が上昇したときのみ許容される
ようになっている。Counter balance valve (also known as holding valve)
15 is a four-way three-position hydraulic switching box 14 that allows hydraulic oil to freely flow in one direction to the hydraulic cylinder, but allows flow in the opposite direction only when the oil pressure in the supply/discharge circuit 9 increases. It has become.
Ｆは、油圧シリンダ１によシ担持された負荷である。油
圧シリンダ１は、油圧制御装置７の四方向三位性油圧切
換：ｔＰ１４’ｋ １位置に操作することで伸長駆動、
四方向三位性油圧切換；ｔＰ１４’ｋ １１位置に操作
することで縮小駆動、四方向三位置油圧切換弁１４？セ
ンタ位＠０にすることで負荷Ｆを担持した状態で停止す
るようになっている。F is the load carried by the hydraulic cylinder 1. The hydraulic cylinder 1 is extended and driven by operating the hydraulic control device 7 to the four-way three-position hydraulic switching: tP14'k 1 position.
4-way 3-position hydraulic switching; tP14'k Reduction drive by operating to 11 position, 4-way 3-position hydraulic switching valve 14? By setting the center position @0, the motor stops while carrying the load F.
この種の油圧シリンダ１は、こｎ’に伸長して長時間停
止させた場合、突発的に縮小することがあった。すなわ
ち、油圧シリンダ１の負荷Ｆ’ｊ担持する側の伸長動作
側圧油室５（以下の説明では。When this type of hydraulic cylinder 1 is extended to n' and stopped for a long time, it may suddenly contract. That is, the extension operation side pressure oil chamber 5 on the side that carries the load F'j of the hydraulic cylinder 1 (in the following description).
負荷Ｆを担持する側の油室を負荷担持側油室という。）
内の油温かシリンダ２にあるいはシリンダ２を伝って外
気に放出され、漸次油温が低下しこれに伴って負荷担持
側油室５に充填されている作動油の体積が減少する。ま
た、油圧シリンダ１の摺動部等からの作動油の洩出によ
り負荷相持側油室５の作動油の量が減少する。負荷相持
側油室５の作動油の体積又は量の減少は負荷相持側油室
５内の油圧全低下させ、負荷相持側油室５内の油圧によ
る負荷相持力（負荷担持側油室５の作動油の圧力×ピス
トン４の受圧面積）全減少きせる。一方油圧シリンダ１
のピストン４とシリンダ２間。The oil chamber on the side that carries the load F is called a load-carrying side oil chamber. )
The oil temperature inside the cylinder 2 is discharged to the outside air through the cylinder 2, and the oil temperature gradually decreases, and the volume of the hydraulic oil filled in the load-carrying side oil chamber 5 decreases accordingly. Furthermore, due to leakage of hydraulic oil from the sliding parts of the hydraulic cylinder 1, the amount of hydraulic oil in the load-bearing side oil chamber 5 decreases. A decrease in the volume or amount of the hydraulic oil in the load-bearing side oil chamber 5 causes the total oil pressure in the load-bearing side oil chamber 5 to decrease, and the load-bearing force (of the load-bearing side oil chamber 5) due to the oil pressure in the load-bearing side oil chamber 5 decreases. Hydraulic oil pressure x pressure receiving area of piston 4) total reduction. On the other hand, hydraulic cylinder 1
between piston 4 and cylinder 2.
ピストンロッド３とシリンダ２問および当該油圧シリン
ダが組み込まれる機械部分には摩擦抵抗が存在している
ので、上記のように油圧番こよる負荷し、負荷Ｆ’ｊ停
止状態に保持するのであるが、油圧番こよる負荷担持力
の減少が一定以上となると最早や上記摩擦抵抗による負
荷相持力でに袖い切れず、油圧シリンダ１は負荷Ｆによ
り急激に縮小すること（こなる。このような現象は、突
発的に発生＆ ５
するものであり、その発生全予測し得ないものであった
ため極めて危険なものであった。Since there is frictional resistance in the piston rod 3, the two cylinders, and the mechanical parts in which the hydraulic cylinder is installed, the hydraulic pressure is applied as described above, and the load F'j is maintained at a stopped state. When the load-carrying force due to the hydraulic pressure decreases beyond a certain level, the load-carrying force due to the frictional resistance can no longer be used up, and the hydraulic cylinder 1 suddenly contracts due to the load F. The phenomenon occurred suddenly and was completely unpredictable, making it extremely dangerous.
本発明は、油圧シリンダが負荷全担持して停止している
停止状態において、油圧シリンダの負荷担持側油室の作
動油の油圧が、当該作動油の油温低下による体積の減少
又は洩出による油量の減少によって低下しようとしたと
き、負荷担持側油室へ圧油を供給することで負荷担持側
油室の油圧全補償する新規な負荷を相持する油圧シリン
ダの負荷相持側油室の圧力補償装置？提供しようとする
ものである。ｊなわち、本発明に係る負荷ケ担持する油
圧シリンダの負荷相持側油室の圧力補償装置は、伸長動
作側圧油室と縮小動作側圧油塑全府伸縮駆動並びに負荷
を担持した状態で停止することができる油圧シリンダに
おける負荷担持側油室の圧力補償装置であって、蓄圧器
と、この蓄圧器を前記油圧シリンダの負荷担持側油室又
は当該負荷担持側油室へ接続された前記給排回路へ連通
状ｌａ６
に接続する状態と、過圧］用路へ接続する状態との間で
切替可能なバルブ装置で構成したことケ特徴とするもの
である。The present invention provides that, in a stopped state in which the hydraulic cylinder is stopped while carrying the entire load, the hydraulic pressure of the hydraulic oil in the load-carrying side oil chamber of the hydraulic cylinder is reduced due to a volume reduction or leakage due to a drop in the oil temperature of the hydraulic oil. When the oil volume is about to drop due to a decrease in oil volume, supplying pressure oil to the load-carrying side oil chamber fully compensates for the oil pressure in the load-carrying side oil chamber.The pressure in the load-carrying side oil chamber of the hydraulic cylinder that supports the new load. Compensator? This is what we are trying to provide. In other words, the pressure compensation device of the load-bearing side oil chamber of the load-carrying hydraulic cylinder according to the present invention stops with the extension operation side pressure oil chamber and the contraction operation side pressure oil chamber all extended and contracted, and with the load being supported. A pressure compensating device for a load-carrying side oil chamber in a hydraulic cylinder, comprising: a pressure accumulator; The present invention is characterized in that it is constructed with a valve device that can be switched between a state in which it is connected to the circuit in communication form la6 and a state in which it is connected to the overpressure channel.
以下本発明の実施例全第２図以下に基づいて詳細に説明
する。第１図で用い前述した符号１〜１５およびＦは以
下の説明（こおいて同義であるのでその説明全省略する
。Embodiments of the present invention will be described in detail below with reference to FIG. 2 and below. Reference numerals 1 to 15 and F used in FIG. 1 and described above will be explained below (since they have the same meaning, their explanations will be omitted entirely).
第２図番こおいて、１６は蓄圧器、１７はパルプ装置で
ある。パルプ装置１７は、蓄圧器１６に接続さｎた保圧
回路１８、油圧シリンダ１の負荷相持側油室５に接続さ
れた油路１９および過圧（ロ）路２０の間に介装されて
おシ、蓄圧器１６全油圧シリンダ１の負荷相持側油室５
に接続さ扛た給排回路８へ連通状に接続する状態（図示
１位置）と、蓄圧器１６會逃圧回路へ接続する状態（図
示■位置）との間で切替可能に構成している。本発明の
負荷？担持する油圧シリンダの負荷相持側油室の圧力補
償装置は、上記蓄圧器１６とパルプ装置１７で構成して
いる。In the second figure, 16 is a pressure accumulator, and 17 is a pulp device. The pulp device 17 is interposed between a pressure holding circuit 18 connected to the pressure accumulator 16, an oil passage 19 connected to the load supporting side oil chamber 5 of the hydraulic cylinder 1, and an overpressure passage 20. Pressure accumulator 16 Full hydraulic cylinder 1 load side oil chamber 5
It is configured to be switchable between a state in which it is connected in communication with the supply/discharge circuit 8 connected to the pressure accumulator 16 (position 1 in the figure) and a state in which it is connected to the pressure relief circuit of the pressure accumulator 16 (position ■ in the figure). . Load of the invention? The pressure compensator for the load-bearing side oil chamber of the hydraulic cylinder carried therein is composed of the pressure accumulator 16 and the pulp device 17.
次に作用全説明する。油圧制御装置７の四方向三位酸油
圧切換弁１４葡操作し、油圧シリンダ１金１１ｏ、
７
負荷Ｆ（こ抗する方向あるいは負荷Ｆに順な方向へ伸縮
駆動するときに、バルブ装置１７’に１位置に操作し、
油圧シリンダ１の負荷相持側油室５に接続する給排回路
８と蓄圧器１６ヲ連通状に接続する。Next, the entire operation will be explained. Operate the four-way three-position hydraulic switching valve 14 of the hydraulic control device 7, and operate the hydraulic cylinder 1 metal 11o,
7 Load F (when expanding and contracting in the direction against or in the direction of load F, operate the valve device 17' to the 1 position,
The supply/discharge circuit 8 connected to the load-bearing side oil chamber 5 of the hydraulic cylinder 1 and the pressure accumulator 16 are connected in communication.
このようにすると、油圧シリンダ１の伸縮駆動中に負荷
相持０１１１油室５に発生する油圧が、ｊ０１路１９゜
バルブ装置１７および保圧囲路１８を経て蓄圧器］６に
蓄圧される。In this way, the hydraulic pressure generated in the load-bearing oil chamber 5 during expansion and contraction of the hydraulic cylinder 1 is accumulated in the pressure accumulator 6 via the j01 path 19° valve device 17 and the pressure enclosure 18.
次に、ｌ…圧制御装置７の四方白玉位置油圧切換て停止
状態（こある油圧シリンダ１の負荷相持側油室５の圧力
が油温低下あるいに油の洩出により低下しようとすると
、蓄圧器１６から保圧回路１８．バルブ装置１７．油路
１９．給排（ロ）路８全通って負荷担持側油室５へ圧油
が補給されるので油圧シリンダ１の負荷相持側油室５の
内圧は、負荷Ｆを担持するのに必要な圧力に保た扛るも
のである。Next, the four-way white ball position hydraulic pressure of the l...pressure control device 7 is switched to a stopped state (when the pressure in the load-bearing side oil chamber 5 of the hydraulic cylinder 1 is about to decrease due to a drop in oil temperature or oil leakage, Pressure oil is supplied from the pressure accumulator 16 to the load carrying side oil chamber 5 through all of the pressure holding circuit 18, valve device 17, oil passage 19 and supply/discharge (B) passage 8, so that the load carrying side oil chamber 5 of the hydraulic cylinder 1 is supplied with pressure oil. The internal pressure 5 is maintained at a pressure necessary to support the load F.
油圧シリンダ１によって担持される負荷Ｆｖｉｌ−変更
したときは、バルブ装置ＩＱ−［位置に操作し。When changing the load Fvil carried by the hydraulic cylinder 1, operate the valve device IQ-[position].
蓄圧器１６會保圧回路１８およびバルブ装＠１７を経て
地圧回路２０に接続し、蓄圧器１６の圧力全解放した上
で、あらためて上記の操作？するものである。Connect the pressure accumulator 16 to the earth pressure circuit 20 via the pressure holding circuit 18 and the valve system @17, release the pressure of the pressure accumulator 16 completely, and then repeat the above operation. It is something to do.
なお、蓄圧器１６の容量は、油圧シリンダ１が負荷全担
持して停止状態に保たれる時間を考慮して初かしめ充分
大きなものに設にしておけは良いのであるが、補給蓋に
は自ずと限度がある。蓄圧器１６に畜圧さｔ″Ｌ７？：
圧油が低下し、この蓄圧器１６がら油圧シリンダ１の負
荷相持側油室５への補給が行わＴ′Ｌなくなった場合に
は、蓄圧器１６へ再蓄圧する必要があるが、この場合に
は、油圧制御弁７の四方白玉位置油圧切換５ｆ１１４？
ｉ” １位置方向（油圧シリンダ１を負荷番こ拡して伸
長駆動する方向）へ操作し油圧シリンダ１を微少量ＦＬ
Ａ動すれば良い。またこの拘蓄圧は、油路１９に、現在
圧力を指示する指針ａと、この指針ａが篩田方向に移動
するときにのみ指針ａに随行して油路１９の葦ｗ６圧カ
（＋Ｍｋ指示すると共を二手１１にて復帰可能な指針す
全有する出力計２１全取り付け（第２図々示）、この圧
力計２１の指針すに回路１９の最高圧力（この最高圧力
は。Note that the capacity of the pressure accumulator 16 should be set to be large enough for the initial crimping, considering the time during which the hydraulic cylinder 1 carries the full load and is kept in a stopped state. There are limits. Accumulated pressure in pressure accumulator 16 t''L7?:
When the pressure oil decreases and the pressure oil chamber 5 of the hydraulic cylinder 1 is replenished from this pressure accumulator 16 to T'L, it is necessary to re-accumulate the pressure in the pressure accumulator 16. Is the four-way white ball position hydraulic switching 5f114 of the hydraulic control valve 7?
i" Operate in the 1 position direction (the direction in which hydraulic cylinder 1 is expanded by the load number and driven to extend) and move hydraulic cylinder 1 to a very small amount FL.
All you have to do is move A. In addition, this accumulated pressure is determined by a pointer a indicating the current pressure in the oil path 19, and a pointer a that follows the pointer a only when this pointer a moves in the direction of the sieve field. Then, the output meter 21, which has a pointer that can be reset with two hands 11, is fully installed (shown in Figure 2), and the pointer of this pressure gauge 21 is at the maximum pressure in the circuit 19 (this maximum pressure is determined).
屋 ９
油圧シリンダ１會伸長又は縮小動させたときの負荷担持
側油室５の圧力値である。）を指示させておき、油路１
９の現在ｆ＋ｋが所定以上低下したこと全指針ａで読み
取扛るようにし、その上で油圧制御装置ＪＬ７の四方向
三位置油圧切換升１４會１位置方向（油圧シリンダ１會
負荷！に抗して伸長駆動する方向トレ少ｉｔ操作して給
排回路へ圧油ケ徐々に供給して再蓄圧する◎この供給を
、前記圧力計の指針ａが、指針すに到達する直前まで行
うのである。9 This is the pressure value in the load carrying side oil chamber 5 when the hydraulic cylinder 1 is extended or contracted. ), and then connect oil path 1.
9, the current f+k has decreased by more than a predetermined value, so that it can be read with all the indicators a, and then the hydraulic control device JL7's four-way three-position hydraulic switching square 14 position 1 direction (hydraulic cylinder 1 load! Pressurized oil is gradually supplied to the supply/discharge circuit by a small amount of operation in the direction of extension drive, and the pressure is re-accumulated. This supply is continued until just before the pointer a of the pressure gauge reaches the pointer.
このようにするときは、再蓄圧番こ際して油圧シリンダ
ｌｋ停止状態に保ったま＼蓄圧器２１Ｇこ再蓄圧ができ
るものである。When doing this, the pressure can be stored again in the pressure accumulator 21G while keeping the hydraulic cylinder lk in a stopped state.
上記実施？ＩＪ＋こおいては、油路１９を、油田シリン
ダ１の負荷相持０１１ｊ油室５に接＠きれた給排回路８
に接続しているが、給排回路８への接続は油圧制商１装
置１ｆｆｆｉ７Ｇこおけるカウンタバランスバルブ１５
の前段でめっても良いし、またこの油路１９に、油圧シ
リンダ１の負荷相持側油室５に直接接続しても良いこと
勿論である。Is the above implemented? In IJ+, the supply/discharge circuit 8 connects the oil passage 19 to the load supporting 011j oil chamber 5 of the oil field cylinder 1.
However, the connection to the supply/discharge circuit 8 is the counter balance valve 15 in the hydraulic pressure regulator 1 equipment 1fffi7G.
Of course, the oil passage 19 may be directly connected to the load-bearing side oil chamber 5 of the hydraulic cylinder 1.
本発明の、負荷紮担持する油田シリンダの負荷ＩＯ
担持１１１１ｊ油蔓の圧力補償装置が適用さ粗る油圧シ
リンダに、旨四で説明したとおりのものであり、上記実
凡例ではこの油田シリンダを冒塘で説明した条件に、ｍ
丁汎用的なものとして８５？、明しているが。The pressure compensating device for the load carrying 1111j oil field cylinder of the present invention is applied to the hydraulic cylinder as explained in Section 4, and in the above example, this oil field cylinder is not affected. Under the conditions explained in Tong, m
85 as a general purpose item? , but it is clear.
ご
主こで本発明が適用さｔしる油圧シリンダの使途の具体
的−例全説明しておく。それは、クレーンのブーム伸縮
用の油圧シリンダでおる。第３図に示すようにクレーン
の伸縮ブーム２２は、？＆端廁の外側ブーム２３．外側
ブーム２３内へ伸縮自在昏こ嵌挿した先端側の内側ブー
ム２４．および外側プーム２３と内側ブーム２４ｒｌＪ
］◆こ介装され外側ブーム２３昏二対して内側ブーム２
４を伸縮駆動並びに停止する油圧シリンダ１′で構成さ
れている。この伸縮ブーム２２はブーム起伏用油田シリ
ンダ２５により起伏操作される。I will now explain all the specific examples of uses of the hydraulic cylinder to which the present invention is applied. It is a hydraulic cylinder that extends and retracts the crane's boom. As shown in FIG. 3, the telescopic boom 22 of the crane is ? & Outer boom 23. The inner boom 24 on the tip side is telescopically inserted into the outer boom 23. and outer pool 23 and inner boom 24rlJ
] ◆Inner boom 2 is installed as opposed to outer boom 23.
4 is comprised of a hydraulic cylinder 1' that telescopically drives and stops the motor. This telescopic boom 22 is hoisted by a boom hoisting oil field cylinder 25.
クレーン作業は、伸縮ブーム２２の先端に荷重ｗ２吊下
して、伸縮ブーム２２ヲ伸縮および停止、ブームを起伏
操作することでなされるものであるが。Crane work is carried out by suspending a load w2 from the tip of the telescopic boom 22, extending/contracting and stopping the telescopic boom 22, and raising and lowering the boom.
この種の油圧シリンダ１′は極めて長尺であるため。This type of hydraulic cylinder 1' is extremely long.
その伸長動作側圧油室の油温低下あるいに油洩れによる
突発的な縮小量が大きくなり、極めて危険Ａｌｌ
なものであった。本発明ｔこの油圧シリンダ１′に採用
するとき、そｎだけに大きな効果が期待できるものであ
る。The amount of sudden contraction due to a drop in oil temperature or oil leakage in the extension side pressure oil chamber was extremely dangerous. When the present invention is adopted in this hydraulic cylinder 1', great effects can be expected.
いずれ番こしても本発明は１以上の如く栴成し作用する
ものでめるから、負荷を担持して停止状態にある油圧シ
リンダか、突発的に負荷により駆動するの全未然に防止
し得るものでめるから、安全ｔ−確保する上で極めて大
きな効果に！するものでめる。In any case, since the present invention is constructed and operated in one or more ways, it is possible to completely prevent a hydraulic cylinder that is in a stopped state while carrying a load from being suddenly driven by a load. Because you can use it, it has a huge effect on ensuring safety! Find something to do.
縞１図および第を図に１本発明の負荷を担持する油田シ
リンダの負衝担持餉油寥の圧力袖憤装賑が適用式れる油
圧シリンダの説明図、第２図−一←―は本発明の負荷を
担持する油圧シリンダの負荷担持１１ｔｌｊ油昆の圧力
補償装置の説明用油圧回路図である。
油圧シリ／り１１． 伸長動作側圧油−；５゜縮小動作
側圧油室ｉ６． 給糾、叫路ｉ ８ 、：、 、、、、
９゜油圧制御鉄敏茎７． 蓄圧器ｉ１６゜
過圧沖１路；２０． パルプ装置蕃１７不１１Fig. 1 and Fig. 1 are explanatory diagrams of a hydraulic cylinder to which the load-carrying oil field cylinder of the present invention can be applied, and Fig. It is a hydraulic circuit diagram for explaining the pressure compensator of the load-carrying hydraulic cylinder of the invention. Hydraulic pump/removal 11. Extension action side pressure oil -; 5° contraction action side pressure oil chamber i6. Supplementary, shouting route i 8, :, ,,,,,
9゜Hydraulic control iron stem 7. Pressure accumulator i16° overpressure offshore 1st route; 20. Pulp equipment 17th and 11th
Claims (1)
る油圧シリンダにおける負荷担持側油室の圧力補償装置
であって、蓄圧器と、この蓄圧器全前記油圧シリンダの
負荷担持側油室又は当該負荷担持側油室へ接続された前
記給排回路へ連通状に接続する状態と、過圧回路へ接続
する状態との間で切替可能なパルプ装置で構成したこと
全特徴とする負荷全担持する油圧シリンダの負荷担持側
油室の圧力補償装置。[Claims] It has both an extension side pressure oil chamber and a contraction side oil chamber. A pressure compensator for a load-carrying side oil chamber in a hydraulic cylinder that is line-driven and can be stopped with the entire load being carried, comprising a pressure accumulator, the pressure accumulator, and the load-carrying side oil chamber of the hydraulic cylinder or the load. Hydraulic pressure capable of supporting the entire load, comprising a pulp device that can be switched between a state in which it is connected in communication with the supply/discharge circuit connected to the oil chamber on the supporting side and a state in which it is connected to the overpressure circuit. Pressure compensation device for the oil chamber on the load-carrying side of the cylinder.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP18502382A JPS5973602A (en) | 1982-10-20 | 1982-10-20 | Pressure compensating device for oil chamber on load bearing side of load bearing hydraulic cylinder |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP18502382A JPS5973602A (en) | 1982-10-20 | 1982-10-20 | Pressure compensating device for oil chamber on load bearing side of load bearing hydraulic cylinder |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| JPS5973602A true JPS5973602A (en) | 1984-04-25 |
Family
ID=16163421
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP18502382A Pending JPS5973602A (en) | 1982-10-20 | 1982-10-20 | Pressure compensating device for oil chamber on load bearing side of load bearing hydraulic cylinder |
Country Status (1)
| Country | Link |
|---|---|
| JP (1) | JPS5973602A (en) |
Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US7089734B2 (en) | 2000-05-25 | 2006-08-15 | J.C. Bamford Excavators Limited | Hydraulic system for wheeled loader |
Citations (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPS50127069A (en) * | 1974-01-24 | 1975-10-06 | ||
| JPS5334071A (en) * | 1976-09-13 | 1978-03-30 | Hitachi Ltd | Oilhydraulic system |
-
1982
- 1982-10-20 JP JP18502382A patent/JPS5973602A/en active Pending
Patent Citations (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPS50127069A (en) * | 1974-01-24 | 1975-10-06 | ||
| JPS5334071A (en) * | 1976-09-13 | 1978-03-30 | Hitachi Ltd | Oilhydraulic system |
Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US7089734B2 (en) | 2000-05-25 | 2006-08-15 | J.C. Bamford Excavators Limited | Hydraulic system for wheeled loader |
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