JPH01261503A - Two speed lift mechanism for industrial vehicle - Google Patents
Two speed lift mechanism for industrial vehicleInfo
- Publication number
- JPH01261503A JPH01261503A JP8485988A JP8485988A JPH01261503A JP H01261503 A JPH01261503 A JP H01261503A JP 8485988 A JP8485988 A JP 8485988A JP 8485988 A JP8485988 A JP 8485988A JP H01261503 A JPH01261503 A JP H01261503A
- Authority
- JP
- Japan
- Prior art keywords
- valve
- pressure
- speed
- low
- lift 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.)
- Granted
Links
- 239000003921 oil Substances 0.000 claims description 30
- 239000010720 hydraulic oil Substances 0.000 claims description 10
- 238000010586 diagram Methods 0.000 description 3
- 239000012530 fluid Substances 0.000 description 3
- 230000007123 defense Effects 0.000 description 1
Landscapes
- Operation Control Of Excavators (AREA)
- Forklifts And Lifting Vehicles (AREA)
- Fluid-Pressure Circuits (AREA)
Abstract
Description
【発明の詳細な説明】
（産業上の利用分野）
本弁明は、フォークリフトやショベルローダ等のような
産業車両に係り、詳しくは低圧用ポンプと高圧用ポンプ
の２台の油圧ポンプを用いて、リフトシリンダを負荷の
大きさに対応して高速と低速とで上昇作動させるだめの
２スピードリフト礪構に関する。Detailed Description of the Invention (Field of Industrial Application) This defense relates to industrial vehicles such as forklifts and shovel loaders, and more specifically, uses two hydraulic pumps, a low-pressure pump and a high-pressure pump. This invention relates to a two-speed lift structure for lifting a lift cylinder at high speed and low speed depending on the magnitude of load.
（従来の技術）
従来、この種の２スピードリフト機構は、第３図に示す
如く構成されている。図示のように、低圧入容量ポンプ
３１及び高圧小容量ポンプ３２から送られた吐出油は、
２スピードバルブ３３で合流し、ここでリフトシリンダ
３４の負荷の高低に応じて低圧大容量ポンプ３１の吐出
油をコントロールバルブ３５へ送るかタンク３６へドレ
ーンするかを制御するようになっている。すなわち、２
スピードバルブ３３はパイロット操作式であって、回路
内圧力が設定圧以下（低負荷時）では、リリーフバルブ
３７の閉止によりｌ／］換弁３８をＡ位置に切換えて２
台のポンプ３１，３２の合δ１叶出量でリフトシリンダ
３４を高速作動させ、設定圧以上（高負荷時）ではリリ
ーフバルブ３７の開放によって切換弁３８をＢ位置に切
換えて低圧大容量ポンプ３１の吐出油をタンク３６ヘド
レーンさせ、高圧小容量ポンプ３２の吐出油でリフトシ
リンダ３４を低速作動させるようになついる。(Prior Art) Conventionally, this type of two-speed lift mechanism has been constructed as shown in FIG. As shown in the figure, the discharge oil sent from the low pressure input capacity pump 31 and the high pressure small capacity pump 32 is
They meet at a two-speed valve 33, where it is controlled whether the oil discharged from the low-pressure large-capacity pump 31 is sent to a control valve 35 or drained to a tank 36 depending on the level of load on the lift cylinder 34. That is, 2
The speed valve 33 is pilot operated, and when the pressure in the circuit is below the set pressure (during low load), the relief valve 37 is closed and the l/] switching valve 38 is switched to the A position.
The lift cylinder 34 is operated at high speed with a combined output of δ1 of the pumps 31 and 32, and when the pressure exceeds the set pressure (during high load), the relief valve 37 is opened and the switching valve 38 is switched to the B position. The discharged oil is drained to the tank 36, and the lift cylinder 34 is operated at a low speed with the discharged oil of the high pressure small capacity pump 32.
（発明が解決しようとする課題）
ところが、上述した従来例ではリフトシリンダ３４に作
用する負荷の程度（積荷の＠吊）がリリーフバルブ３７
の設定圧前後に相当する場合には、リフトシリンダ３４
が上昇すると、そのときの回路内の圧力変動によりリリ
ーフバルブ３７が開閉作動する、つまり切換弁３８がＡ
位置とＢ位置との間で反復的に切換作動されるので、リ
フトシリンダ３４の上が速度が変動し、その衝撃で積荷
が不安定となるという問題がある。(Problem to be Solved by the Invention) However, in the conventional example described above, the degree of load (lifting of the load) acting on the lift cylinder 34 is
If the set pressure is around the set pressure, the lift cylinder 34
When A rises, the relief valve 37 opens and closes due to the pressure fluctuation in the circuit at that time, that is, the switching valve 38 opens and closes.
Since the switching operation is repeated between the position and the B position, there is a problem in that the speed of the top of the lift cylinder 34 fluctuates, and the load becomes unstable due to the impact.
そこで本発明は、以上の問題に鑑み、リフトシリンダの
上昇速度の切換えを安全かつ確実に行ない得る産業車両
の２スピードリフト機構を提供することを、その目的と
する。SUMMARY OF THE INVENTION In view of the above problems, an object of the present invention is to provide a two-speed lift mechanism for an industrial vehicle that can safely and reliably switch the lifting speed of a lift cylinder.
（課題を解決するための手段）
上記課題を解決するために本発明は、低圧用と高圧用の
２台の油圧ポンプを用いて、低負荷時には低圧用のポン
プに高圧用のポンプを加えた吐出端でリフトシリンダを
作用させ、高負荷時には高圧用のポンプの吐出端でリフ
トシリンダを作用させる産業車両の２スピードリフト機
構において、前記高圧用ポンプの吐出油を直接コントロ
ールバルブに導く構成とする一方、低圧用ポンプの吐出
油をフローデバイダにより優先流れと２スピードバルブ
に通じる余剰流れとに分流し、２スピードバルブは逆止
弁を経て前記高圧用ポンプの吐出油と合流する流れと、
切換弁とリリーフバルブとからなるアンローディングバ
ルブに至る流れとに分岐する構成とし、さらにアンロー
ディングバルブは、回路内圧力がリリーフバルブの設定
圧を越えたときには開放作動して低圧用ポンプの吐出油
をタンクにドレーンし、回路内圧力がリリーフバルブの
設定圧以下でかつ２スピードバルブ側への作動油流れが
ない場合には閉止作動する構成としたことを要旨とする
。(Means for Solving the Problems) In order to solve the above problems, the present invention uses two hydraulic pumps, one for low pressure and one for high pressure, and when the load is low, a pump for high pressure is added to the pump for low pressure. In a two-speed lift mechanism for an industrial vehicle in which a lift cylinder is operated at a discharge end, and when the load is high, the lift cylinder is operated at a discharge end of a high-pressure pump, the discharge oil of the high-pressure pump is directly guided to a control valve. On the other hand, the discharge oil of the low pressure pump is divided by a flow divider into a priority flow and a surplus flow leading to a 2-speed valve, and the 2-speed valve has a flow that merges with the discharge oil of the high pressure pump via a check valve;
The flow is branched into an unloading valve consisting of a switching valve and a relief valve, and the unloading valve is opened when the pressure in the circuit exceeds the set pressure of the relief valve, and the discharge oil of the low-pressure pump is The gist of this invention is to drain the valve into a tank, and close the valve when the pressure in the circuit is lower than the set pressure of the relief valve and there is no flow of hydraulic fluid to the 2-speed valve side.
（作用）
従って、回路内圧力がリリーフバルブの設定圧よりも低
い低負荷時にはアンローディングバルブは開じており、
このときは高圧用ポンプと低圧用ポンプとの吐出油量で
リフトシリンダが高速上界される。一方、高０荷時には
回路内圧力がリリーフバルブの設定圧を越えることに伴
ってアンローディングバルブがアンロード側に切換えら
れ、低圧用ポンプの作動油がタンクヘトレーンされるた
め、リフトシリンダは高圧用ポンプの吐出油で低速上昇
される。しかして、アンローディングバルブは一旦アン
ロード側に切換えられると、回路内圧力がリリーフバル
ブの設定圧以下でかつ２スピードバルブ側への作動油流
れが無くならない限り、その状態を維持するため、たと
え負荷の程度がリリーフバルブの設定圧付近に相当する
場合であっても、リフトシリンダの上昇速度は低速に維
持されることになる。(Function) Therefore, at low load when the pressure in the circuit is lower than the set pressure of the relief valve, the unloading valve is open.
At this time, the lift cylinder is raised at high speed by the amount of oil discharged by the high pressure pump and the low pressure pump. On the other hand, at high zero load, the unloading valve is switched to the unloading side as the pressure in the circuit exceeds the set pressure of the relief valve, and the hydraulic oil of the low pressure pump is transferred to the tank, so the lift cylinder is under high pressure. It is raised at low speed by the oil discharged from the pump. However, once the unloading valve is switched to the unloading side, it will maintain that state as long as the pressure in the circuit is below the set pressure of the relief valve and the flow of hydraulic oil to the 2-speed valve side is stopped. Even if the degree of load corresponds to the vicinity of the set pressure of the relief valve, the lifting speed of the lift cylinder will be maintained at a low speed.
（実施例）
以下、本発明の実施例を図面に基づいて４休的に説明す
る。図示のように、高圧小容偵ポンプ１は管路２を経て
リフトシリンダ制御用のコントロールバルブ３に接続さ
れ、全吐出油がコントロールバルブ３に送られるように
なっている。なお、コントロールバルブ３は管路４，５
によりリフ１〜シリンダ６のボＩ〜ム側ならびにロッド
側と接続されている。一方、低圧大容量ポンプ７は管路
８を経てフローデバイダ９に接続されており、このフロ
ーデバイダ９によってその吐出油が優先管路１０と余剰
油管路１１とに分流されるようにイ１っている。すなわ
ら、第２図に示すようにエンジンのアイドル運転から所
定回転数までの低回転域では作動油は全て優先管路１０
側へ流れ、この低回転域を越える高回転時には余剰分の
作動油が２スピードバルブ１２側へ流れるように設定さ
れている。(Example) Hereinafter, an example of the present invention will be described in detail based on the drawings. As shown in the figure, the high-pressure small pump 1 is connected via a conduit 2 to a control valve 3 for controlling a lift cylinder, so that all discharged oil is sent to the control valve 3. In addition, the control valve 3 is connected to the pipes 4 and 5.
It is connected to the body side and rod side of the rift 1 to the cylinder 6. On the other hand, the low-pressure large-capacity pump 7 is connected to a flow divider 9 through a pipe 8, and the flow divider 9 divides the discharged oil into a priority pipe 10 and a surplus oil pipe 11. ing. In other words, as shown in Figure 2, in the low rotation range from engine idling to a predetermined rotation speed, all hydraulic fluid flows through the priority pipe 10.
When the rotation speed exceeds this low rotation range, excess hydraulic oil is set to flow toward the two-speed valve 12 side.
なお、優先管路１０は、たとえばパワーステアリング回
路として利用される。Note that the priority conduit 10 is used, for example, as a power steering circuit.
しかして、２スピードバルブ１２は逆止弁１３と、アン
ローディングバルブ１４とからなり、余剰油管路１１か
ら流入した作動油を、逆止弁１３に至る流れと、アンロ
ーディングバルブ１４に至る流れとに分岐する構成とし
てあり、そして逆止弁１３側へ送られた作動油は管路１
７を経て前記高圧小容量ポンプ１の吐出油と合流してコ
ントロールバルブ３へ供給される。The two-speed valve 12 is composed of a check valve 13 and an unloading valve 14, and the hydraulic oil flowing from the surplus oil pipe line 11 is divided into a flow reaching the check valve 13 and a flow reaching the unloading valve 14. The hydraulic oil sent to the check valve 13 side is routed through pipe 1.
7, joins the discharge oil of the high pressure small capacity pump 1, and is supplied to the control valve 3.
一方、アンローディングバルブ１４は２位置型の切換弁
１５とリリーフバルブ１６とから構成され、それら両弁
１５，１６はそれぞれパイロット圧によって操作される
ようになっている。１なわら、切換弁１５はパイロワ１
〜ライン１８．１９を介して開き方向と閉じ方向との両
側にパイロット圧を受けており、またリリーフバルブ１
６は切換弁１５の閉じ側と共通のパイロットライン１９
を介してパイロット圧を受けている。なお、共通のパイ
ロットライン１９には絞り２０が、また切換弁１５の入
口側には絞り２１がそれぞれ挿入されるとともに、切換
弁１５の出口側は管路２２を介してタンク２３に接続さ
れている。さらにパイロットライン１９はり換弁１５が
開き位置に切換えられたときには、絞り２０よりも下流
においてバイパス通路２４を介してタンク２３に連通ず
るようになっている。On the other hand, the unloading valve 14 is composed of a two-position switching valve 15 and a relief valve 16, and both valves 15 and 16 are operated by pilot pressure, respectively. 1, the switching valve 15 is the Pyrower 1.
- Receives pilot pressure via lines 18 and 19 on both sides in the opening and closing directions, and the relief valve 1
6 is a pilot line 19 common to the closing side of the switching valve 15
Receives pilot pressure via. Note that a throttle 20 is inserted into the common pilot line 19 and a throttle 21 is inserted into the inlet side of the switching valve 15, and the outlet side of the switching valve 15 is connected to a tank 23 via a conduit 22. There is. Further, when the pilot line 19 and the switching valve 15 are switched to the open position, the pilot line 19 communicates with the tank 23 via the bypass passage 24 downstream of the throttle 20.
本実施例は上述のように構成したものであるから、コン
トロールバルブ３を上が側へ切換操作したときのリフト
シリンダ６へ送られる作動油の流中は第２図に示す通り
となる。すなわち、エンジンによって駆動される高圧小
容量ポンプ１からの吐出油は常に管路２を経て直接コン
トロールバルブ３へ送られるが、低圧入容量ポンプ７の
吐出油はエンジンの低回転域にはその全量が優先管路１
０側へ流れるため、このときのリフトシリンダ６への送
油聞は高圧小容量ポンプ１からの吐出油だけである。Since this embodiment is constructed as described above, the flow of hydraulic oil sent to the lift cylinder 6 when the control valve 3 is switched to the upper side is as shown in FIG. In other words, the oil discharged from the high-pressure small capacity pump 1 driven by the engine is always sent directly to the control valve 3 via the pipe 2, but the oil discharged from the low-pressure input capacity pump 7 is not in its entirety during the low rotation range of the engine. is priority pipe 1
Since the oil flows to the 0 side, the oil delivered to the lift cylinder 6 at this time is only the oil discharged from the high pressure small capacity pump 1.
これに対し、エンジンの高回転時には低圧大容量ポンプ
７の吐出油はその余剰分が２スピードバルブ１２へ流れ
る。そして、回路内圧力がリリーフバルブ１６の設定圧
よりも低いとき、つまりリフｌ−シリンダ６に作用する
負荷が小さい低負荷時には、アンローディングバルブ１
４の切換弁１５及びリリーフバルブ１６が共に閉止状態
を保持するので、作動油は逆止弁１３、管路１８を経て
へ圧小容吊ポンプ１の吐出油と合流する。従って、この
ときは高圧小容量ポンプ１の吐出油季に低圧入容量ポン
プ７の吐出油量（優先流量を除く）がリフトシリンダ６
に送られるので、リフトシリンダ６は高速で上界される
。On the other hand, when the engine rotates at high speed, the excess oil discharged from the low-pressure large-capacity pump 7 flows to the two-speed valve 12. When the pressure in the circuit is lower than the set pressure of the relief valve 16, that is, when the load acting on the relief cylinder 6 is low, the unloading valve 1
Since both the switching valve 15 and the relief valve 16 of No. 4 are kept closed, the hydraulic oil passes through the check valve 13 and the pipe line 18 and joins the discharge oil of the small volume lifting pump 1. Therefore, at this time, the amount of oil discharged from the low pressure input capacity pump 7 (excluding the priority flow rate) is the same as the amount of oil discharged from the lift cylinder 6 when the high pressure small capacity pump 1 discharges oil.
, so the lift cylinder 6 is raised at high speed.
一方、高負荷時には回路内圧力がリリーフバルブ１６の
設定圧を越えるため、パイロットライン１９を経て作用
するパイロット圧によってリリーフバルブ１６が開き、
この開放作動によってパスロフトライン１９側の圧力が
パイロットライン１８側の圧力より下がるため、切換弁
１５が開き側に切換えられる。すなわら、アンローディ
ングバルブ１４が作動して低圧大容量ポンプ７から２ス
ピードバルブ１２へ送られる作動油は全て切換弁１５か
ら管路２２を経てタンク２０へ戻されることになるので
、ことのきはリフトシリンダ６は高圧小容量ポンプ１か
らの吐出油によって低速で上昇される。On the other hand, when the load is high, the pressure in the circuit exceeds the set pressure of the relief valve 16, so the relief valve 16 opens due to the pilot pressure acting through the pilot line 19.
Due to this opening operation, the pressure on the pass loft line 19 side becomes lower than the pressure on the pilot line 18 side, so the switching valve 15 is switched to the open side. In other words, all the hydraulic fluid sent from the low-pressure large-capacity pump 7 to the two-speed valve 12 when the unloading valve 14 operates is returned from the switching valve 15 to the tank 20 via the pipe 22, so that Then, the lift cylinder 6 is lifted at a low speed by the oil discharged from the high-pressure, small-capacity pump 1.
そして、切換弁１５が開き側に切換わると、パイロット
ライン１９はバイパス通路２４を杆てタンク２３に連通
するため、パイロットライン１８側の圧力がパイロット
ライン１９側の圧力より低い状態に維持され、切換弁１
５は開いたままとなる。すなわら、アンローディングバ
ルブ１４は−Ｈアンロード側に作動したときは、回路内
圧力がリリーフバルブ１６の設定圧以下でかつエンジン
の低回転により２スピードバルブ１２側への作動油流れ
が全く無くならないと復帰しない。従って、リフトシリ
ンダ６の上昇作動時において内向がリリーフバルブ１Ｇ
の設定圧前後に相当するものであったとしても、リフト
シリンダ６は安定した低速度で上昇される。When the switching valve 15 is switched to the open side, the pilot line 19 passes through the bypass passage 24 and communicates with the tank 23, so the pressure on the pilot line 18 side is maintained lower than the pressure on the pilot line 19 side. Switching valve 1
5 remains open. That is, when the unloading valve 14 operates to the -H unload side, the pressure in the circuit is lower than the set pressure of the relief valve 16 and the engine speed is low, so no hydraulic oil flows to the 2-speed valve 12 side. It won't come back unless it goes away. Therefore, when the lift cylinder 6 is raised, the inward direction is the relief valve 1G.
Even if the pressure is around the set pressure, the lift cylinder 6 is lifted at a stable low speed.
なお、本発明の２スピードリフト機構の適用範囲はフォ
ークリフトに限定り”るものではなく、産業車両におい
てリフトシリンダを高速と低速との２段にｉｔ、Ｉ＋御
する必要にあるものであれば適用可能である。また、高
圧用と低圧用のポンプ１．７の容Ｂは同じであっても差
支えない。The scope of application of the two-speed lift mechanism of the present invention is not limited to forklifts, but can be applied to any industrial vehicle in which it is necessary to control the lift cylinder in two stages, high speed and low speed. It is possible.Also, the capacity B of the high-pressure pump 1.7 and the low-pressure pump 1.7 may be the same.
（発明の効宋）
以上詳述したように、本発明の２スピードリフト橢構に
よれば、リフトシリンダの上界速度が一旦低速に切換ね
ると、エンジン回転を低速に落とさない限り低速状態を
維持できるので、リフトシリンダにリリーフバルブの設
定圧付近に相当する荷重が作用した場合の従来問題であ
るリフトシリンダの上昇速度の変動を防止して安定した
上昇作動を得ることができ、作業の安全性を図る上で大
きく役立つものである。(Effect of the Invention) As detailed above, according to the two-speed lift structure of the present invention, once the upper limit speed of the lift cylinder is switched to a low speed, the low speed state will be maintained unless the engine rotation is reduced to a low speed. This makes it possible to prevent fluctuations in the lifting speed of the lift cylinder, which is a conventional problem when a load equivalent to the set pressure of the relief valve is applied to the lift cylinder, and to obtain stable lifting operation, improving work safety. It is very useful for understanding gender.
第１図は本発明の実施例を示す油圧回路図、第２図はリ
フトシリンダに対する作動油流遭を示す線図、第３図は
従来例を示す油圧回路図である。
１・・・高圧小官Φポンプ
３・・・コントロールバルブ
６・・・リフトシリンダ
７・・・低圧大容量ポンプ
９・・・７０−デバイダ
１２・・・２スピードバルブ
１３・・・逆止弁
１４・・・アンローディングバルブ
１５・・・切換弁
１６・・・リリーフバルブFIG. 1 is a hydraulic circuit diagram showing an embodiment of the present invention, FIG. 2 is a line diagram showing hydraulic oil flowing into a lift cylinder, and FIG. 3 is a hydraulic circuit diagram showing a conventional example. 1...High pressure small official Φ pump 3...Control valve 6...Lift cylinder 7...Low pressure large capacity pump 9...70-divider 12...2 Speed valve 13...Check valve 14...Unloading valve 15...Switching valve 16...Relief valve
Claims (1)
時には低圧用のポンプに高圧用のポンプを加えた吐出量
でリフトシリンダを作用させ、高負荷時には高圧用のポ
ンプの吐出量でリフトシリンダを作用させる産業車両の
２スピードリフト機構において、前記高圧用ポンプの吐
出油を直接コントロールバルブに導く構成とする一方、
低圧用ポンプの吐出油をフローデバイダにより優先流れ
と２スピードバルブに通じる余剰流れとに分流し、２ス
ピードバルブは逆止弁を経て前記高圧用ポンプの吐出油
と合流する流れと、切換弁とリリーフバルブとからなる
アンローディングバルブに至る流れとに分岐する構成と
し、さらにアンローディングバルブは、回路内圧力がリ
リーフバルブの設定圧を越えたときには開放作動して低
圧用ポンプの吐出油をタンクにドレーンし、回路内圧力
がリリーフバルブの設定圧以下でかつ２スピードバルブ
側への作動油流れがない場合には閉止作動する構成とし
た産業車両の２スピードリフト機構。Using two hydraulic pumps, one for low pressure and one for high pressure, the lift cylinder operates with the discharge volume of the low pressure pump plus the high pressure pump when the load is low, and the discharge volume of the high pressure pump when the load is high. In a two-speed lift mechanism of an industrial vehicle that operates a lift cylinder, the discharge oil of the high-pressure pump is directly guided to a control valve, and
The discharge oil of the low-pressure pump is divided by a flow divider into a priority flow and a surplus flow leading to a two-speed valve, and the two-speed valve separates the flow that passes through a check valve and joins the discharge oil of the high-pressure pump, and a switching valve. The flow is branched into an unloading valve consisting of a relief valve and an unloading valve, and when the pressure in the circuit exceeds the set pressure of the relief valve, the unloading valve is opened and the oil discharged from the low-pressure pump is transferred to the tank. A 2-speed lift mechanism for an industrial vehicle configured to drain and close when the pressure in the circuit is lower than the set pressure of a relief valve and there is no flow of hydraulic oil to the 2-speed valve side.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP63084859A JP2586563B2 (en) | 1988-04-06 | 1988-04-06 | 2-speed lift mechanism for industrial vehicles |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP63084859A JP2586563B2 (en) | 1988-04-06 | 1988-04-06 | 2-speed lift mechanism for industrial vehicles |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| JPH01261503A true JPH01261503A (en) | 1989-10-18 |
| JP2586563B2 JP2586563B2 (en) | 1997-03-05 |
Family
ID=13842535
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP63084859A Expired - Lifetime JP2586563B2 (en) | 1988-04-06 | 1988-04-06 | 2-speed lift mechanism for industrial vehicles |
Country Status (1)
| Country | Link |
|---|---|
| JP (1) | JP2586563B2 (en) |
Cited By (7)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP2007290806A (en) * | 2006-04-24 | 2007-11-08 | Furukawa Unic Corp | Pressure oil supply quantity control device of on-vehicle crane |
| JP2008279530A (en) * | 2007-05-09 | 2008-11-20 | Sumitomo Metal Mining Co Ltd | Manipulator device |
| JP2010076937A (en) * | 2008-09-01 | 2010-04-08 | Nissan Motor Co Ltd | Hydraulic circuit device of industrial vehicle |
| US8454319B2 (en) | 2006-11-09 | 2013-06-04 | Furukawa Unic Corporation | Pressurized-oil supply amount control device for vehicle-mounted crane |
| JP2016125559A (en) * | 2014-12-26 | 2016-07-11 | 株式会社クボタ | Hydraulic system for work machine and work machine with this hydraulic system |
| CN107725504A (en) * | 2017-09-21 | 2018-02-23 | 林德（中国）叉车有限公司 | A kind of hydraulic system and hydraulic control method that suitable performance is provided for load |
| CN113565817A (en) * | 2021-06-29 | 2021-10-29 | 英轩重工有限公司 | Unloading valve and loader hydraulic multi-pump confluence system thereof |
Citations (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPS5025571A (en) * | 1973-07-04 | 1975-03-18 | ||
| JPS5129301U (en) * | 1974-08-28 | 1976-03-03 | ||
| JPS6076552U (en) * | 1983-10-31 | 1985-05-29 | カヤバ工業株式会社 | Hydraulic circuit for self-propelled vehicles |
-
1988
- 1988-04-06 JP JP63084859A patent/JP2586563B2/en not_active Expired - Lifetime
Patent Citations (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPS5025571A (en) * | 1973-07-04 | 1975-03-18 | ||
| JPS5129301U (en) * | 1974-08-28 | 1976-03-03 | ||
| JPS6076552U (en) * | 1983-10-31 | 1985-05-29 | カヤバ工業株式会社 | Hydraulic circuit for self-propelled vehicles |
Cited By (7)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP2007290806A (en) * | 2006-04-24 | 2007-11-08 | Furukawa Unic Corp | Pressure oil supply quantity control device of on-vehicle crane |
| US8454319B2 (en) | 2006-11-09 | 2013-06-04 | Furukawa Unic Corporation | Pressurized-oil supply amount control device for vehicle-mounted crane |
| JP2008279530A (en) * | 2007-05-09 | 2008-11-20 | Sumitomo Metal Mining Co Ltd | Manipulator device |
| JP2010076937A (en) * | 2008-09-01 | 2010-04-08 | Nissan Motor Co Ltd | Hydraulic circuit device of industrial vehicle |
| JP2016125559A (en) * | 2014-12-26 | 2016-07-11 | 株式会社クボタ | Hydraulic system for work machine and work machine with this hydraulic system |
| CN107725504A (en) * | 2017-09-21 | 2018-02-23 | 林德（中国）叉车有限公司 | A kind of hydraulic system and hydraulic control method that suitable performance is provided for load |
| CN113565817A (en) * | 2021-06-29 | 2021-10-29 | 英轩重工有限公司 | Unloading valve and loader hydraulic multi-pump confluence system thereof |
Also Published As
| Publication number | Publication date |
|---|---|
| JP2586563B2 (en) | 1997-03-05 |
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