JP2003049781A - Hydraulic device - Google Patents

Hydraulic device

Info

Publication number
JP2003049781A
JP2003049781A JP2001235748A JP2001235748A JP2003049781A JP 2003049781 A JP2003049781 A JP 2003049781A JP 2001235748 A JP2001235748 A JP 2001235748A JP 2001235748 A JP2001235748 A JP 2001235748A JP 2003049781 A JP2003049781 A JP 2003049781A
Authority
JP
Japan
Prior art keywords
hydraulic
interlocking
control valve
area
lever
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
JP2001235748A
Other languages
Japanese (ja)
Inventor
Eiji Shibahara
英二 芝原
Original Assignee
Shimadzu Corp
株式会社島津製作所
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
Application filed by Shimadzu Corp, 株式会社島津製作所 filed Critical Shimadzu Corp
Priority to JP2001235748A priority Critical patent/JP2003049781A/en
Publication of JP2003049781A publication Critical patent/JP2003049781A/en
Pending legal-status Critical Current

Links

Classifications

    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15BSYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B21/00Common features of fluid actuator systems; Fluid-pressure actuator systems or details thereof, not covered by any other group of this subclass
    • F15B21/04Special measures taken in connection with the properties of the fluid
    • F15B21/041Removal or measurement of solid or liquid contamination, e.g. filtering
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15BSYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00Circuits for servomotor systems
    • F15B2211/60Circuit components or control therefor
    • F15B2211/615Filtering means

Abstract

PROBLEM TO BE SOLVED: To provide a hydraulic device capable of reducing shock on starting. SOLUTION: The opening of a control valve 52 is changed via an interlocking mechanism 62 in response to the turning angle of an operation lever 4 in an ON area A- ON so that a working fluid discharged from a hydraulic pump 2 must not be immediately supplied to an external actuator even when an electric motor 1 is started.

Description

【発明の詳細な説明】 【0001】 【発明の属する技術分野】本発明は、電動機、液圧ポン
プ、タンク等を備え、電動機を作動させることによって
外部アクチュエータに作動流体を供給することのできる
液圧装置に関する。 【0002】 【従来の技術】この種の液圧装置は、従来、操作レバー
の操作により電動機をオンオフ駆動して液圧ポンプを回
転させ、この液圧ポンプから吐出する作動流体をシリン
ダ等の外部アクチュエータに供給するようにしている。 【0003】 【発明が解決しようとする課題】ところが、電動機の始
動時に液圧ポンプから作動流体が一挙に吐出し、前記シ
リンダ等に流れ込んでショックが生じる場合がある。か
かる不具合に対し、例えば電動機をインバータ駆動する
などして、操作レバーのオン方向への操作量に応じて徐
々に電動モータの回転数を制御するようなことも考えら
れるが、この種の液圧装置が配備される環境が厳しいこ
とやコスト面、あるいは電動機に流れる大電流を制御し
た場合の動作信頼性等を考慮するとこのような電気的な
制御方法はあまり好ましいものではない。 【0004】そこで本発明は、上記問題を簡単かつ確実
な構成により解決すべく、外部アクチュエータに作動液
を供給するための制御弁を、電動機の作動用操作レバー
に機械的に連動させ、電動機を作動させた時点では液圧
ポンプから吐出した流体がタンクに流れ、そこからの操
作レバーの操作量に応じてアクチュエータへ供給される
流体流量が増大するようにしたものである。 【0005】 【課題を解決するための手段】すなわち、本発明に係る
液圧装置は、オンオフ動作する電動機と、この電動機に
より駆動されて吐出口から流体を吐出する液圧ポンプ
と、タンクと、所定のオン領域に回動操作すると前記電
動機を作動させ、前記オン領域と隣接して設定されたオ
フ領域に回動操作すると前記電動機を停止させる操作レ
バーと、前記液圧ポンプの吐出口と前記タンクとを連通
する連通経路と、この連通経路上に設けられて前記操作
レバーの回動軸線と直交する方向に進退移動し、その通
過流量を制御する制御弁と、前記操作レバーのオン領域
における回動動作を前記制御弁の進退移動に連動させる
連動機構とを具備することを特徴とする。 【0006】このようなものであれば、操作レバーのオ
ン領域における回動角度に応じて制御弁の開度を変化さ
せ、電動機を始動させても液圧ポンプから吐出される作
動流体がすぐには外部アクチュエータには供給されない
ようにすることができるので、電動機始動時に、外部ア
クチュエータに作動流体が一挙に供給されることにより
生じるショック等を抑止することができる。 【0007】また、電動機を作動させるための操作レバ
ーを、連動機構を利用して制御弁の操作にも共用してい
るので、部品点数の削減が図れるうえ、コスト、信頼性
等の面で優れたものとすることができる。 【0008】加えて、制御弁が、操作レバーの回動軸線
と異なる方向に進退動作するので、この制御弁の配置位
置の自由度が増大し、装置のコンパクト化が可能とな
る。 【0009】 【発明の実施の形態】以下、本発明の実施の形態につい
て説明する。 【0010】図1、図2は、この実施の形態における液
圧装置100を示した全体図である。この液圧装置10
0は、テールゲート車等の産業車両に用いられるものであって、電動機1と液圧ポンプ2(同図中は図示されない)とをアダプタプレート7を介して連結し、このアダプタプレート7に、タンク3、各種弁50、51,5 0 is used for industrial vehicles such as tailgate vehicles, and the electric motor 1 and the hydraulic pump 2 (not shown in the figure) are connected to the adapter plate 7 via an adapter plate 7. Tank 3, various valves 50, 51, 5
2、出力ポートP2等の液圧関連部材の他、電動機1用のスイッチSWやこのスイッチSWを入切するための操作レバー4を取り付けて、一体的な構造としたものである。 2. In addition to hydraulic pressure-related members such as the output port P2, a switch SW for the electric motor 1 and an operation lever 4 for turning on / off the switch SW are attached to form an integrated structure. 【0011】そして、図3、図4等に示すように、液圧ポンプ2の吐出口P1が、アダプタプレート7内に設けた主流体経路R0を介して、外部アクチュエータ(図示しない)に接続される出力ポートP2に連通するようにしている。 Then, as shown in FIGS. 3 and 4, the discharge port P1 of the hydraulic pump 2 is connected to an external actuator (not shown) via a main fluid path R0 provided in the adapter plate 7. It communicates with the output port P2. この主流体経路R0上には、外部アクチュエータからポンプ吐出口P1に流体が逆流するのを防止する主チェック弁50を設けている。 A main check valve 50 is provided on the main fluid path R0 to prevent the fluid from flowing back from the external actuator to the pump discharge port P1. 【0012】また、アダプタプレート7内には、この主流体経路R0からタンク3に至る2つの分岐流体経路(第1分岐経路R1及び連通経路たる第2分岐経路R Further, in the adapter plate 7, two branched fluid paths (the first branch path R1 and the second branch path R which is a communication path) from the main fluid path R0 to the tank 3 are included.
2)を並列的に設けるとともに、これら各分岐経路R 2) is provided in parallel, and each of these branch paths R
1、R2上にそれぞれ第1制御弁51及び第2制御弁5 1st control valve 51 and 2nd control valve 5 on R2, respectively
2を配設している。 2 is arranged. なお、請求項1記載の「連通経路」 The "communication route" according to claim 1.
は前記第2分岐経路R2に、また「制御弁」は前記第2 Is in the second branch path R2, and the "control valve" is in the second branch path R2.
制御弁52に相当する。 It corresponds to the control valve 52. 【0013】第1分岐経路R1は、主流体経路R0における前記主チェック弁50の下流から分岐してアダプタプレート7に設けたタンクポートP3に連通するものである。 The first branch path R1 branches from the downstream of the main check valve 50 in the main fluid path R0 and communicates with the tank port P3 provided on the adapter plate 7. また、その経路R1上に設けてなる第1制御弁5 Further, the first control valve 5 provided on the path R1
1は、ボール511をバネ512によりシート513に押しつけ付勢してタンクポートP3に向かう流体の流れを阻止するチェック弁タイプのものである。 Reference numeral 1 denotes a check valve type in which the ball 511 is pressed against the seat 513 by the spring 512 and urged to block the flow of the fluid toward the tank port P3. 【0014】第2分岐経路R2は、主流体経路R0における前記主チェック弁50の上流から分岐して前記タンクポートP3に連通するものである。 The second branch path R2 branches from the upstream of the main check valve 50 in the main fluid path R0 and communicates with the tank port P3. また、その経路R In addition, the route R
2上に設けてなる第2制御弁52は、円錐面を有するポペット521をバネ522によりシート523に押しつけ付勢してタンクポートP3に向かう流体の流れを阻止するやはりチェック弁タイプのものである。 The second control valve 52 provided on the second control valve 52 is also a check valve type that blocks the flow of fluid toward the tank port P3 by pressing the poppet 521 having a conical surface against the seat 523 by the spring 522. .. 【0015】一方、操作レバー4は、レバー本体41 On the other hand, the operating lever 4 is the lever body 41.
と、このレバー本体41に直交するように結合された回動軸42とからなるもので、この回動軸42をアダプタプレート7に設けた軸受孔71に嵌合させることにより、このアダプタプレート7に対し回動可能に取り付けてある。 And a rotating shaft 42 coupled so as to be orthogonal to the lever body 41. By fitting the rotating shaft 42 into a bearing hole 71 provided in the adapter plate 7, the adapter plate 7 is formed. It is rotatably attached to the. そしてその操作レバー4を、図2に示す所定のオン領域A_ON内に回動操作すると、前記スイッチS Then, when the operating lever 4 is rotated into the predetermined on region A_ON shown in FIG. 2, the switch S
Wをオン状態にして電動機1を作動させ、前記オン領域A_ONと隣接したオフ領域A_OF側に回動操作すると該スイッチSWをオフ状態にして電動機1を停止させるように設定してある。 When W is turned on to operate the electric motor 1 and the motor 1 is rotated to the off region A_OF side adjacent to the on region A_ON, the switch SW is turned off and the electric motor 1 is stopped. 【0016】しかして本実施形態では、更にこの操作レバー4の回動動作を、前記第1制御弁51の開閉動作に変換する第1連動機構61と、前記第2制御弁52の開閉動作に変換する第2連動機構62とを設けている。 However, in the present embodiment, the rotation operation of the operation lever 4 is further converted into the opening / closing operation of the first control valve 51 by the first interlocking mechanism 61 and the opening / closing operation of the second control valve 52. A second interlocking mechanism 62 for conversion is provided. なお、請求項1記載の「連動機構」は前記第2連動機構6 The "interlocking mechanism" according to claim 1 is the second interlocking mechanism 6.
2に相当する。 Corresponds to 2. 【0017】詳述すれば、第1連動機構61は、前記回動軸42の先端から軸線L1を一致させて一体に突出したねじ棒611と、このねじ棒611から軸線L1を一致させて更に一体に延出させた円柱状の押し部材612 More specifically, in the first interlocking mechanism 61, the screw rod 611 protruding integrally from the tip of the rotating shaft 42 with the axis L1 aligned with the screw rod 611 is further aligned with the axis L1 from the screw rod 611. Cylindrical push member 612 extended integrally
とを備え、前記ねじ棒611をアダプタプレート7に設けた雌ネジ孔613に螺合させてなるものである。 The screw rod 611 is screwed into the female screw hole 613 provided in the adapter plate 7. 【0018】そして、前記オフ領域A_OFにおける前記オン領域A_ONとの境界部分である中立位置A_M Then, in the off region A_OF, the neutral position A_M which is the boundary portion with the on region A_ON.
に操作レバー4を位置させると、この押し部材612の先端が、第1制御弁51のボール511から離間するか、又はボール511がシート513から離れない程度に接触した状態となって、この第1制御弁51が閉止し得るように設定してある。 When the operating lever 4 is positioned at the position, the tip of the pushing member 612 is separated from the ball 511 of the first control valve 51, or the ball 511 is in contact with the seat 513 to the extent that the ball 511 is not separated from the seat 513. 1 The control valve 51 is set so that it can be closed. 一方、この操作レバー4を中立位置A_Mからオフ領域A_OF側に向かって回すことにより、ねじ棒611が内部にねじ込まれ、押し部材612により前記ボール511がシート513から離間させる向きに動かされて第1制御弁51が開成されるように設定してある。 On the other hand, by turning the operating lever 4 from the neutral position A_M toward the off region A_OF side, the screw rod 611 is screwed inside, and the pushing member 612 moves the ball 511 away from the seat 513. 1 The control valve 51 is set to be opened. 【0019】第2連動機構62は、前記ねじ棒611と押し部材612との間に一体に設けたカム部材621 The second interlocking mechanism 62 is a cam member 621 integrally provided between the screw rod 611 and the push member 612.
と、このカム部材621に先端が当接するように、前記第2制御弁52のポペット521から一体に突出させた円柱状の従動部材622とを備えてなる。 A columnar driven member 622 that is integrally projected from the poppet 521 of the second control valve 52 so that the tip of the cam member 621 is in contact with the cam member 621. 前記カム部材621は、断面を楕円形としてその表面がカム面62a The cam member 621 has an elliptical cross section and its surface is a cam surface 62a.
を形成するようにしたものである。 Is made to form. 一方、従動部材62 On the other hand, the driven member 62
2は、その先端をこのカム面62aに摺動させて進退移動するもので、その進退移動方向が、前記回動軸42、 Reference numeral 2 denotes a moving forward / backward movement by sliding the tip thereof on the cam surface 62a, and the forward / backward movement direction is the rotation shaft 42.
ねじ棒611、あるいは押し部材612の軸線L1方向と直交するように構成している。 It is configured to be orthogonal to the axis L1 direction of the screw rod 611 or the push member 612. 【0020】そして、操作レバー4を前記中立位置A_ Then, the operating lever 4 is placed in the neutral position A_.
Mに位置させると、カム面62aの楕円長径部分に対応する部位が従動部材622側を向き、この従動部材62 When positioned at M, the portion corresponding to the elliptical major axis portion of the cam surface 62a faces the driven member 622 side, and the driven member 62
2の先端をバネ力に逆らって押してポペット521をシート523から離間させるようにしている。 The tip of 2 is pushed against the spring force to separate the poppet 521 from the seat 523. また、この操作レバー4を中立位置A_Mからオン領域A_ON側に向かって回すことにより、カム面62aの楕円短径部分に対応する部位が従動部材622側を向き、回動端において、従動部材622の先端がカム面62aから離間するか、又はポペット521がシート523から離れない程度に接触した状態となって第2制御弁52が閉止し得るように設定している。 Further, by turning the operating lever 4 from the neutral position A_M toward the on-region A_ON side, the portion corresponding to the elliptical minor axis portion of the cam surface 62a faces the driven member 622 side, and the driven member 622 at the rotating end. The second control valve 52 is set so that the tip of the cam surface 62a can be separated from the cam surface 62a or the poppet 521 can be in contact with the seat 523 so as not to be separated from the seat 523. 【0021】次にこのように構成した本液圧装置100 Next, the hydraulic device 100 configured as described above.
の作用について説明する。 The action of is described. 【0022】操作レバー4が中立位置A_Mにある状態では、カム面62aの長径部分に対応する部位が従動部材622側を向くため、第2制御弁52は、そのポペット521はシート522から離れた全開状態となって、 In the state where the operating lever 4 is in the neutral position A_M, the portion corresponding to the major axis portion of the cam surface 62a faces the driven member 622 side, so that the poppet 521 of the second control valve 52 is separated from the seat 522. Fully open
この第2分岐経路R2を連通状態にする。 The second branch path R2 is put into a communicating state. 【0023】そこで操作レバー4を中立位置A_Mを越えてオン領域A_ON側に回すと、スイッチSWがオン状態となって電動機1が作動し、液圧ポンプ2が回転するが、中立位置A_Mを越えた直近の領域では、第2制御弁52が略全開状態であるため、液圧ポンプ2から吐出した流体は、第2分岐経路R2、タンク3ポートを介してタンク3に戻る。 Then, when the operating lever 4 is turned beyond the neutral position A_M to the on area A_ON side, the switch SW is turned on, the electric motor 1 is operated, and the hydraulic pump 2 is rotated, but the neutral position A_M is exceeded. In the most recent region, since the second control valve 52 is in a substantially fully open state, the fluid discharged from the hydraulic pump 2 returns to the tank 3 via the second branch path R2 and the tank 3 port. 【0024】そこから更に操作レバー4をオン領域A_ From there, the operating lever 4 is further turned on. Area A_
ON側に回していくと、電動機1は作動状態のまま、カム面62aの短径部分に対応する部位が、レバー回動角度に応じて徐々に従動部材622側を向いていくため、 When the motor 1 is turned to the ON side, the portion corresponding to the short diameter portion of the cam surface 62a gradually faces the driven member 622 side according to the lever rotation angle while the electric motor 1 remains in the operating state.
第2制御弁52のポペット521が徐々にシート522 Poppet 521 of the second control valve 52 gradually becomes seat 522
に接近してその開度が減じられる。 The opening is reduced as it approaches. 【0025】そして、この第2制御弁52を流れる作動流体の圧力損失が、外部アクチュエータ(例えばシリンダ)からの負荷により生じる出力ポート圧力よりも大きくなると、液圧ポンプ2から吐出された作動流体が、主チェック弁50のボールを押し上げ、出力ポートP2から外部アクチュエータに供給されることとなる。 Then, when the pressure loss of the working fluid flowing through the second control valve 52 becomes larger than the output port pressure generated by the load from the external actuator (for example, the cylinder), the working fluid discharged from the hydraulic pump 2 is released. , The ball of the main check valve 50 is pushed up and supplied to the external actuator from the output port P2. 【0026】さらに操作レバー4をオン領域A_ONの回動端にまで回すと、第2制御弁52は完全に閉止状態となり、液圧ポンプ2から吐出された作動流体の全量が、出力ポートP2から外部アクチュエータに供給されることとなる。 When the operating lever 4 is further turned to the rotating end of the on region A_ON, the second control valve 52 is completely closed, and the total amount of the working fluid discharged from the hydraulic pump 2 is discharged from the output port P2. It will be supplied to the external actuator. 【0027】つまり、操作レバー4のオン領域回動端方向への回動角度に応じて第2制御弁52の開度が徐々に小さくなっていき、外部アクチュエータへの供給流量が徐々に増大することとなる。 That is, the opening degree of the second control valve 52 gradually decreases according to the rotation angle of the operating lever 4 toward the on-region rotation end direction, and the supply flow rate to the external actuator gradually increases. It will be. 【0028】一方、操作レバー4を中立位置A_Mに戻すと、電動機1のスイッチSWがオフとなり、液圧ポンプ2が停止して作動流体の供給がストップする。 On the other hand, when the operating lever 4 is returned to the neutral position A_M, the switch SW of the electric motor 1 is turned off, the hydraulic pump 2 is stopped, and the supply of the working fluid is stopped. この状態では、第1制御弁51、及び主チェック弁50が閉止状態であるから、外部アクチュエータから流体が戻ることはない。 In this state, since the first control valve 51 and the main check valve 50 are in the closed state, the fluid does not return from the external actuator. 【0029】ここから、操作レバー4を中立位置A_M From here, the operating lever 4 is placed in the neutral position A_M.
を越えてオフ領域A_OF側に回すと、ねじ棒611がねじ孔613のピッチに応じて内方にねじ込まれ、このねじ棒611に連結された押し部材612が第1制御弁51のボール511をシート513から離間させる。 When the screw rod 611 is turned inward according to the pitch of the screw hole 613, the push member 612 connected to the screw rod 611 pushes the ball 511 of the first control valve 51 into the off region A_OF side. Separate from sheet 513. そして、このボール511とシート513との隙間から流体がタンク3に戻り、外部アクチュエータである例えばシリンダが縮むこととなる。 Then, the fluid returns to the tank 3 from the gap between the ball 511 and the seat 513, and the external actuator, for example, the cylinder contracts. 第1制御弁51の開度は、 The opening degree of the first control valve 51 is
このボール511とシート513との隙間距離で定まるが、この隙間距離は、操作レバー4の回動角度に応じたものであるため、この回動角度を調整することにより、 It is determined by the gap distance between the ball 511 and the seat 513, but since this gap distance depends on the rotation angle of the operating lever 4, by adjusting this rotation angle,
タンク3へ戻る流量を変化させてシリンダの縮む速度を調整することができることとなる。 It is possible to adjust the contraction speed of the cylinder by changing the flow rate returning to the tank 3. 【0030】したがって、本実施形態に係る液圧装置1 Therefore, the hydraulic pressure device 1 according to the present embodiment
00によれば、電動機1を始動させた場合に、最初は必ず第2制御弁52が開いて、液圧ポンプ2から吐出される作動流体がすぐには外部アクチュエータには供給されず、その後の操作レバー4のオン領域A_ONにおける回動角度に応じて第2制御弁52の開度が変化し、外部アクチュエータに供給される作動流体の流量をコントロールできることとなる。 According to 00, when the electric motor 1 is started, the second control valve 52 is always opened at first, and the working fluid discharged from the hydraulic pump 2 is not immediately supplied to the external actuator, and thereafter. The opening degree of the second control valve 52 changes according to the rotation angle of the operating lever 4 in the on region A_ON, and the flow rate of the working fluid supplied to the external actuator can be controlled. そのため、電動機1の始動時、 Therefore, when the motor 1 is started,
すなわち液圧ポンプ2の始動時に、外部アクチュエータに作動流体が一挙に供給されることにより生じるショック等を抑止することができる。 That is, when the hydraulic pump 2 is started, it is possible to suppress a shock or the like caused by the hydraulic fluid being supplied to the external actuator all at once. 【0031】また、電動機1のスイッチSWを操作するための操作レバー4を、第1、第2連動機構61、62 Further, the operation lever 4 for operating the switch SW of the electric motor 1 is provided with the first and second interlocking mechanisms 61 and 62.
を介して第1、第2制御弁52の操作にも共通して用いるようにしているので、部品点数の削減が図れ、また、 Since it is commonly used for the operation of the first and second control valves 52, the number of parts can be reduced and the number of parts can be reduced.
外部アクチュエータへの供給流量や戻り流量を、機械的に簡単な構造で制御できるので、コスト、信頼性等の面で優れたものとすることができる。 Since the supply flow rate and the return flow rate to the external actuator can be controlled by a mechanically simple structure, it can be made excellent in terms of cost, reliability, and the like. 【0032】加えて、第1制御弁51が前記操作レバー4の回動軸42の延長線上に設けられ、その軸線L1に沿って進退移動するものであるのに対し、第2制御弁5 In addition, the first control valve 51 is provided on an extension line of the rotation shaft 42 of the operating lever 4, and moves forward and backward along the axis L1.
2が該回動軸線L1と直交する方向に進退動作するので、この第2制御弁52の配置位置の自由度が増大し、 Since 2 moves in and out in the direction orthogonal to the rotation axis L1, the degree of freedom in the arrangement position of the second control valve 52 increases.
装置のコンパクト化が可能となる。 The device can be made compact. 【0033】なお、本発明は上記実施形態に限られるものではない。 The present invention is not limited to the above embodiment. 例えば、図5に示すようにポペットの代わりにボールBBとロッドLLを使用しても良いし、またねじ棒の断面も楕円に限らず、要は回転により制御弁を進退させることのできるカム面が形成されればよい。 For example, as shown in FIG. 5, a ball BB and a rod LL may be used instead of the poppet, and the cross section of the screw rod is not limited to an ellipse. In short, a cam surface capable of advancing and retreating the control valve by rotation. Should be formed. その他、連動機構の構造は他にも考えられるし、装置の外形や各部材の配置位置など、種々変形が可能であるのは言うまでもない。 In addition, the structure of the interlocking mechanism can be considered, and it goes without saying that various modifications such as the outer shape of the device and the arrangement position of each member can be made. 【0034】 【発明の効果】以上に詳述した本発明によれば、操作レバーのオン領域における回動角度に応じて制御弁の開度を変化させ、電動機を始動させても液圧ポンプから吐出される作動流体がすぐには外部アクチュエータには供給されないようにすることができるので、電動機始動時、 According to the present invention described in detail above, the opening degree of the control valve is changed according to the rotation angle in the on region of the operating lever, and even if the electric motor is started, the hydraulic pump can be used. Since the discharged working fluid can be prevented from being immediately supplied to the external actuator, when the motor is started,
すなわち液圧ポンプ始動時に、外部アクチュエータに作動流体が一挙に供給されることにより生じるショック等を抑止することができる。 That is, when the hydraulic pump is started, it is possible to suppress a shock or the like caused by the working fluid being supplied to the external actuator at once. 【0035】また、電動機を作動させるための操作レバーを、連動機構を利用して制御弁の操作にも共用しているので、部品点数の削減が図れるうえ、コスト、信頼性等の面で優れたものとすることができる。 Further, since the operation lever for operating the electric motor is also shared for the operation of the control valve by using the interlocking mechanism, the number of parts can be reduced and the cost, reliability, etc. are excellent. Can be considered. 【0036】加えて、制御弁が、操作レバーの回動軸線と異なる方向に進退動作するので、この制御弁の配置位置の自由度が増大し、装置のコンパクト化が可能となる。 In addition, since the control valve moves forward and backward in a direction different from the rotation axis of the operating lever, the degree of freedom in the arrangement position of the control valve is increased, and the device can be made compact. Description: BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a liquid having an electric motor, a hydraulic pump, a tank, etc., which can supply a working fluid to an external actuator by operating the electric motor. Pressure device. 2. Description of the Related Art Conventionally, a hydraulic device of this type is operated by turning an electric motor on and off by operating an operating lever to rotate a hydraulic pump, and a working fluid discharged from the hydraulic pump is supplied to an external device such as a cylinder. It is supplied to the actuator. However, when the electric motor is started, the hydraulic fluid may be discharged at once from the hydraulic pump and flow into the cylinder or the like to cause a shock. In response to such a problem, for example, it is conceivable to gradually control the rotation speed of the electric motor according to the operation amount of the operation lever in the ON direction by, for example, d Description: BACKGROUND OF THE tetrahydrofuran 1. Field of the Invention The present invention relates to a liquid having an electric motor, a hydraulic pump, a tank, etc., which can supply a working fluid to an external actuator by operating the electric motor. Pressure device. 2. Description of the Related Art Conventionally, a hydraulic device of this type is operated by turning an electric motor on and off by operating an operating lever to rotate a hydraulic pump, and a working fluid discharged from the hydraulic pump is supplied To an external device such as a cylinder. It is supplied to the actuator. However, when the electric motor is started, the hydraulic fluid may be discharged at once from the hydraulic pump and flow into the cylinder or the like to cause a shock. In response to such a problem, for example, it is conceivable to gradually control the rotation speed of the electric motor according to the operation amount of the operation lever in the ON direction by, for example, d riving the electric motor with an inverter. Such an electric control method is not very preferable in consideration of the severe environment in which the device is provided, cost, operation reliability when controlling a large current flowing through the electric motor, and the like. In order to solve the above problem with a simple and reliable structure, the present invention mechanically interlocks a control valve for supplying a hydraulic fluid to an external actuator with an operation lever for operating the electric motor, and At the time of operation, the fluid discharged from the hydraulic pump flows into the tank, and the flow rate of the fluid supplied to the actuator increases in accordance with the operation amount of the operation lever therefrom. That is, a hydraulic device according to the present invention comprises an electric motor that is turned on and off, a hydraulic pump that is driven by the electric motor to discharge fluid from a discharge port, a tank, An ope riving the electric motor with an inverter. Such an electric control method is not very preferred in consideration of the severe environment in which the device is provided, cost, operation reliability when controlling a large current flowing through the electric motor, and the like. order to solve the above problem with a simple and reliable structure, the present invention mechanically interlocks a control valve for supplying a hydraulic fluid to an external inverter with an operation lever for operating the electric motor, and At the time of operation, the fluid discharged From the hydraulic pump flows into the tank, and the flow rate of the fluid supplied to the inverter increases in accordance with the operation amount of the operation lever appropriately. That is, a hydraulic device according to the present invention an electric motor that is turned on and off, a hydraulic pump that is driven by the electric motor to discharge fluid from a discharge port, a tank, An ope ration lever that turns the motor when rotated to a predetermined ON region and stops the motor when turned to an OFF region set adjacent to the ON region; a discharge port of the hydraulic pump; A communication path communicating with the tank, a control valve provided on the communication path, which moves forward and backward in a direction orthogonal to the rotation axis of the operation lever, and controls a flow rate thereof; and An interlocking mechanism for interlocking the turning operation with the forward / backward movement of the control valve. With such a configuration, the opening degree of the control valve is changed in accordance with the rotation angle of the operation lever in the ON region, so that even when the electric motor is started, the working fluid discharged from the hydraulic pump is immediately supplied. Can be prevented from being supplied to the external actuator, so that a shock or the like caused by the supply of the working fluid to the external act ration lever that turns the motor when rotated to a predetermined ON region and stops the motor when turned to an OFF region set adjacent to the ON region; a discharge port of the hydraulic pump; A communication path communicating with the tank, a control valve provided on the communication path, which moves forward and backward in a direction orthogonal to the rotation axis of the operation lever, and controls a flow rate thereof; and An interlocking mechanism for interlocking the turning operation with the forward / backward movement of the control valve. With such a configuration, the opening degree of the control valve is changed in accordance with the rotation angle of the operation lever in the ON region, so that even when the electric motor is started, the working fluid discharged from the hydraulic pump is immediately supplied . Can be prevented from being supplied to the external actuator, so that a shock or the like caused by the supply of the working fluid to the external act uator at once at the time of starting the electric motor can be suppressed. Further, since the operating lever for operating the electric motor is also used for operating the control valve by using the interlocking mechanism, the number of parts can be reduced, and the cost and reliability are excellent. It can be. In addition, since the control valve moves back and forth in a direction different from the rotation axis of the operation lever, the degree of freedom of the arrangement position of the control valve is increased, and the apparatus can be made compact. An embodiment of the present invention will be described below. FIGS. 1 and 2 are overall views showing a hydraulic device 100 according to this embodiment. This hydraulic device 10 uator at once at the time of starting the electric motor can be suppressed. Further, since the operating lever for operating the electric motor is also used for operating the control valve by using the interlocking mechanism, the number of parts can be reduced, and the cost and reliability are excellent. It can be. In addition, since the control valve moves back and forth in a direction different from the rotation axis of the operation lever, the degree of freedom of the arrangement position of the control valve is increased, and The apparatus can be made compact. An embodiment of the present invention will be described below. FIGS. 1 and 2 are overall views showing a hydraulic device 100 according to this embodiment. This hydraulic device 10
Numeral 0 is used for an industrial vehicle such as a tailgate vehicle, and connects the electric motor 1 and the hydraulic pump 2 (not shown in the figure) via an adapter plate 7. Tank 3, various valves 50, 51, 5 Numeral 0 is used for an industrial vehicle such as a tailgate vehicle, and connects the electric motor 1 and the hydraulic pump 2 (not shown in the figure) via an adapter plate 7. Tank 3, various valves 50, 51, 5
2. A switch SW for the electric motor 1 and an operation lever 4 for turning the switch SW on and off are mounted in addition to hydraulic pressure-related members such as the output port P2 to form an integral structure. As shown in FIGS. 3 and 4, the discharge port P1 of the hydraulic pump 2 is connected to an external actuator (not shown) via a main fluid path R0 provided in the adapter plate 7. Connected to the output port P2. A main check valve 50 is provided on the main fluid path R0 to prevent fluid from flowing back from the external actuator to the pump discharge port P1. In the adapter plate 7, two branch fluid paths (a first branch path R1 and a second branch path R as a communication path) from the main fluid path R0 to the tank 3 are provided. 2. A switch SW for the electric motor 1 and an operation lever 4 for turning the switch SW on and off are mounted in addition to hydraulic pressure-related members such as the output port P2 to form an integral structure. As shown in FIGS. 3 and 4, the discharge port P1 of the hydraulic pump 2 is connected to an external actuator (not shown) via a main fluid path R0 provided in the adapter plate 7. Connected to the output port P2. A main check valve 50 is provided on the main fluid path R0 to prevent fluid from flowing back from the external actuator to the pump discharge port P1. In the adapter plate 7, two branch fluid paths (a first branch path R1 and a second branch path R as a communication path) from the main fluid path R0 to the tank 3 are provided.
2) are provided in parallel, and each of these branch paths R 2) are provided in parallel, and each of these branch paths R
1, a first control valve 51 and a second control valve 5 on R2, respectively. 1, a first control valve 51 and a second control valve 5 on R2, respectively.
2 are arranged. The “communication route” according to claim 1 2 are arranged. The “communication route” according to claim 1
Is in the second branch path R2, and the “control valve” is in the second branch path R2. Is in the second branch path R2, and the “control valve” is in the second branch path R2.
It corresponds to the control valve 52. The first branch path R1 branches from the main fluid path R0 downstream of the main check valve 50 and communicates with a tank port P3 provided in the adapter plate 7. In addition, the first control valve 5 provided on the route R1 It corresponds to the control valve 52. The first branch path R1 branches from the main fluid path R0 downstream of the main check valve 50 and communicates with a tank port P3 provided in the adapter plate 7. In addition, the first control valve 5 provided on the route R1
Reference numeral 1 denotes a check valve type in which a ball 511 is pressed against a seat 513 by a spring 512 to urge the ball 511 to prevent the flow of fluid toward the tank port P3. The second branch path R2 branches from the main fluid path R0 upstream of the main check valve 50 and communicates with the tank port P3. Also, the route R Reference numeral 1 epitaxial a check valve type in which a ball 511 is pressed against a seat 513 by a spring 512 to urge the ball 511 to prevent the flow of fluid toward the tank port P3. The second branch path R2 branches from the main fluid path R0 upstream of the main check valve 50 and communicates with the tank port P3. Also, the route R
The second control valve 52 provided on the second valve 2 is also a check valve type in which a poppet 521 having a conical surface is pressed against a seat 523 by a spring 522 so as to urge the poppet 521 to block the flow of fluid toward the tank port P3. . On the other hand, the operation lever 4 is The second control valve 52 provided on the second valve 2 is also a check valve type in which a poppet 521 having a conical surface is pressed against a seat 523 by a spring 522 so as to urge the poppet 521 to block the flow of fluid toward the tank port P3 .. On the other hand, the operation lever 4 is
And a rotating shaft 42 which is connected to the lever body 41 so as to be orthogonal to the lever body 41. By fitting the rotating shaft 42 into a bearing hole 71 provided in the adapter plate 7, Is mounted so as to be rotatable. When the operation lever 4 is rotated into a predetermined ON area A_ON shown in FIG. And a rotating shaft 42 which is connected to the lever body 41 so as to be orthogonal to the lever body 41. By fitting the rotating shaft 42 into a bearing hole 71 provided in the adapter plate 7, Is mounted so as to be rotating. When the operation lever 4 is rotated into a predetermined ON area A_ON shown in FIG.
When the W is turned on, the motor 1 is operated, and when the motor 1 is turned to the off area A_OF side adjacent to the on area A_ON, the switch SW is turned off and the motor 1 is stopped. In the present embodiment, however, the turning operation of the operation lever 4 is further converted into a first interlocking mechanism 61 for converting the opening and closing operation of the first control valve 51 and an opening and closing operation of the second control valve 52. And a second interlocking mechanism 62 for conversion. It should be noted that the “interlocking mechanism” according to claim 1 is the second interlocking mechanism 6. When the W is turned on, the motor 1 is operated, and when the motor 1 is turned to the off area A_OF side adjacent to the on area A_ON, the switch SW is turned off and the motor 1 is stopped. In the present embodiment And a second interlocking, however, the turning operation of the operation lever 4 is further converted into a first interlocking mechanism 61 for converting the opening and closing operation of the first control valve 51 and an opening and closing operation of the second control valve 52. And a second interlocking mechanism 62 for conversion. It should be noted that the “interlocking mechanism” according to claim 1 is the second interlocking mechanism 6.
Equivalent to 2. More specifically, the first interlocking mechanism 61 further aligns the axis L1 from the tip of the rotary shaft 42 with the screw rod 611 integrally protruding therefrom, and further aligns the axis L1 from the screw rod 611 with the axis L1. A cylindrical pushing member 612 that is integrally extended. Equivalent to 2. More specifically, the first interlocking mechanism 61 further aligns the axis L1 from the tip of the rotary shaft 42 with the screw rod 611 therefore preferably, and further aligns the axis L1 from the screw rod 611 with the axis L1. A cylindrical pushing member 612 that is internally extended.
The screw rod 611 is screwed into a female screw hole 613 provided in the adapter plate 7. Then, a neutral position A_M which is a boundary portion between the off-region A_OF and the on-region A_ON. The screw rod 611 is screwed into a female screw hole 613 provided in the adapter plate 7. Then, a neutral position A_M which is a boundary portion between the off-region A_OF and the on-region A_ON.
When the operation lever 4 is positioned at the position, the tip of the pushing member 612 is separated from the ball 511 of the first control valve 51 or comes into contact with the ball 511 to such an extent that the ball 511 does not separate from the seat 513. It is set so that one control valve 51 can be closed. On the other hand, by turning the operation lever 4 from the neutral position A_M toward the off region A_OF, the screw rod 611 is screwed into the inside, and the ball 511 is moved by the pushing member 612 in a direction to separate the ball 511 from the seat 513. One control valve 51 is set to be opened. The second interlocking mechanism 62 includes a cam member 621 integrally provided between the screw rod 611 and the pushing member 612. When the operation lever 4 is positioned at the position, the tip of the pushing member 612 is separated from the ball 511 of the first control valve 51 or comes into contact with the ball 511 to such an extent that the ball 511 does not separate from The seat 513. It is set so that one control valve 51 can be closed. On the other hand, by turning the operation lever 4 from the neutral position A_M toward the off region A_OF, the screw rod 611 is screwed into the inside, and The ball 511 is moved by the pushing member 612 in a direction to separate the ball 511 from the seat 513. One control valve 51 is set to be opened. The second interlocking mechanism 62 includes a cam member 621 provided between the screw rod 611 and the pushing member 612.
And a columnar driven member 622 integrally protruding from the poppet 521 of the second control valve 52 so that the distal end abuts on the cam member 621. The cam member 621 has an elliptical cross section and a cam surface 62a. And a columnar driven member 622 constitutes from the poppet 521 of the second control valve 52 so that the distal end abuts on the cam member 621. The cam member 621 has an elliptical cross section and a cam surface 62a.
Is formed. On the other hand, the driven member 62 Is formed. On the other hand, the driven member 62
2 moves forward and backward by sliding its tip against the cam surface 62a. 2 moves forward and backward by sliding its tip against the cam surface 62a.
The screw rod 611 or the pushing member 612 is configured to be orthogonal to the direction of the axis L1. Then, the operating lever 4 is moved to the neutral position A_ The screw rod 611 or the pushing member 612 is configured to be orthogonal to the direction of the axis L1. Then, the operating lever 4 is moved to the neutral position A_
M, the portion of the cam surface 62a corresponding to the major axis of the ellipse faces the driven member 622 side. M, the portion of the cam surface 62a corresponding to the major axis of the ellipse faces the driven member 622 side.
2 is pushed against the spring force to separate the poppet 521 from the sheet 523. Further, by turning the operation lever 4 from the neutral position A_M toward the ON region A_ON, the portion corresponding to the elliptical minor diameter portion of the cam surface 62a faces the driven member 622 side, and at the rotation end, the driven member 622 The second control valve 52 is set to be closed such that the tip of the second control valve 52 is separated from the cam surface 62a or is brought into contact with the poppet 521 so as not to be separated from the seat 523. Next, the present hydraulic apparatus 100 constructed as described above 2 is pushed against the spring force to separate the poppet 521 from the sheet 523. Further, by turning the operation lever 4 from the neutral position A_M toward the ON region A_ON, the portion corresponding to the elliptical minor diameter portion of the cam surface 62a faces the driven member 622 side, and at the rotation end, the driven member 622 The second control valve 52 is set to be closed such that the tip of the second control valve 52 is separated from the cam surface 62a or is brought into contact with the poppet 521 so as not to be separated from the seat 523. Next, the present hydraulic apparatus 100 constructed as described above
The operation of will be described. When the operation lever 4 is in the neutral position A_M, the portion corresponding to the long diameter portion of the cam surface 62a faces the driven member 622 side, so that the poppet 521 of the second control valve 52 is separated from the seat 522. It becomes fully open, The operation of will be described. When the operation lever 4 is in the neutral position A_M, the portion corresponding to the long diameter portion of the cam surface 62a faces the driven member 622 side, so that the poppet 521 of the second control valve 52 is separated from the seat 522. It becomes fully open,
This second branch route R2 is brought into a communicating state. When the operation lever 4 is turned to the ON area A_ON side beyond the neutral position A_M, the switch SW is turned on, the electric motor 1 is operated, and the hydraulic pump 2 is rotated. In the immediate area, the second control valve 52 is almost fully open, so the fluid discharged from the hydraulic pump 2 returns to the tank 3 via the second branch path R2 and the tank 3 port. Then, the operation lever 4 is further moved to the ON area A_ This second branch route R2 is brought into a communicating state. When the operation lever 4 is turned to the ON area A_ON side beyond the neutral position A_M, the switch SW is turned on, the electric motor 1 is operated, and the hydraulic pump 2 In the immediate area, the second control valve 52 is almost fully open, so the fluid discharged from the hydraulic pump 2 returns to the tank 3 via the second branch path R2 and the tank 3 port. Then, the operation lever 4 is further moved to the ON area A_
As the motor 1 is turned to the ON side, the portion corresponding to the short diameter portion of the cam surface 62a gradually faces the driven member 622 side according to the lever rotation angle while the electric motor 1 is in the operating state. As the motor 1 is turned to the ON side, the portion corresponding to the short diameter portion of the cam surface 62a gradually faces the driven member 622 side according to the lever rotation angle while the electric motor 1 is in the operating state.
The poppet 521 of the second control valve 52 gradually becomes the seat 522. The poppet 521 of the second control valve 52 gradually becomes the seat 522.
And its opening is reduced. When the pressure loss of the working fluid flowing through the second control valve 52 becomes larger than the output port pressure caused by the load from the external actuator (for example, a cylinder), the working fluid discharged from the hydraulic pump 2 is discharged. , The ball of the main check valve 50 is pushed up and supplied to the external actuator from the output port P2. When the operating lever 4 is further turned to the turning end of the ON area A_ON, the second control valve 52 is completely closed, and the total amount of working fluid discharged from the hydraulic pump 2 is reduced from the output port P2. It will be supplied to the external actuator. That is, the opening of the second control valve 52 gradually decreases in accordance with the rotation angle of the operation lever 4 toward the ON-region rotation end, and the flow rate supplied to the external actuator gradually increases. It will be. On the other hand, when the operati And its opening is reduced. When the pressure loss of the working fluid flowing through the second control valve 52 becomes larger than the output port pressure caused by the load from the external actuator (for example, a cylinder), the working fluid discharged from the hydraulic pump 2 is discharged., The ball of the main check valve 50 is pushed up and supplied to the external actuator from the output port P2. When the operating lever 4 is further turned to the turning end of the ON area A_ON, the second control valve 52 is completely closed, and the total amount of working fluid discharged from the hydraulic pump 2 is reduced from the output port P2. It will be supplied to the external actuator. That is, the opening of the second control valve 52 gradually decreases It will be. On the other hand, when the operati in accordance with the rotation angle of the operation lever 4 toward the ON-region rotation end, and the flow rate supplied to the external actuator gradually increases. ng lever 4 is returned to the neutral position A_M, the switch SW of the electric motor 1 is turned off, the hydraulic pump 2 is stopped, and the supply of the working fluid is stopped. In this state, since the first control valve 51 and the main check valve 50 are closed, the fluid does not return from the external actuator. From here, the operation lever 4 is moved to the neutral position A_M. ng lever 4 is returned to the neutral position A_M, the switch SW of the electric motor 1 is turned off, the hydraulic pump 2 is stopped, and the supply of the working fluid is stopped. In this state, since the first control valve 51 And the main check valve 50 are closed, the fluid does not return from the external actuator. From here, the operation lever 4 is moved to the neutral position A_M.
When the screw rod 611 is turned to the off area A_OF side over the screw hole 613, the screw 611 is screwed inward according to the pitch of the screw hole 613, and the pushing member 612 connected to the screw rod 611 pushes the ball 511 of the first control valve 51. It is separated from the sheet 513. Then, the fluid returns to the tank 3 from the gap between the ball 511 and the seat 513, and the external actuator, for example, the cylinder contracts. The opening of the first control valve 51 is When the screw rod 611 is turned to the off area A_OF side over the screw hole 613, the screw 611 is screwed inward according to the pitch of the screw hole 613, and the pushing member 612 connected to the screw rod 611 pushes the ball 511 Of the first control valve 51. It is separated from the sheet 513. Then, the fluid returns to the tank 3 from the gap between the ball 511 and the seat 513, and the external screw, for example, the cylinder contracts. The opening of the first control valve 51 is
The gap distance is determined by the gap distance between the ball 511 and the seat 513. Since the gap distance depends on the rotation angle of the operation lever 4, by adjusting this rotation angle, The gap distance is determined by the gap distance between the ball 511 and the seat 513. Since the gap distance depends on the rotation angle of the operation lever 4, by adjusting this rotation angle,
By changing the flow rate returning to the tank 3, the speed at which the cylinder contracts can be adjusted. Therefore, the hydraulic device 1 according to the present embodiment By changing the flow rate returning to the tank 3, the speed at which the cylinder contracts can be adjusted. Therefore, the hydraulic device 1 according to the present embodiment
According to 00, when the electric motor 1 is started, the second control valve 52 is always opened at first, and the working fluid discharged from the hydraulic pump 2 is not immediately supplied to the external actuator. The opening degree of the second control valve 52 changes according to the rotation angle of the operation lever 4 in the ON region A_ON, and the flow rate of the working fluid supplied to the external actuator can be controlled. Therefore, when starting the electric motor 1, According to 00, when the electric motor 1 is started, the second control valve 52 is always opened at first, and the working fluid discharged from the hydraulic pump 2 is not immediately supplied to the external actuator. The opening degree of the second control valve 52 changes according to the rotation angle of the operation lever 4 in the ON region A_ON, and the flow rate of the working fluid supplied to the external actuator can be controlled. Therefore, when starting the electric motor 1,
That is, when the hydraulic pump 2 is started, it is possible to suppress a shock or the like caused by supplying the working fluid to the external actuator at once. The operation lever 4 for operating the switch SW of the electric motor 1 is moved by the first and second interlocking mechanisms 61 and 62. That is, when the hydraulic pump 2 is started, it is possible to suppress a shock or the like caused by supplying the working fluid to the external actuator at once. The operation lever 4 for operating the switch SW of the electric motor 1 is moved by the first and second interlocking mechanisms 61 and 62.
, So that it can be used commonly for the operation of the first and second control valves 52, so that the number of parts can be reduced. , So that it can be used commonly for the operation of the first and second control valves 52, so that the number of parts can be reduced.
Since the supply flow rate and the return flow rate to the external actuator can be controlled with a mechanically simple structure, it is possible to improve cost, reliability and the like. In addition, the first control valve 51 is provided on an extension of the rotation shaft 42 of the operation lever 4 and moves forward and backward along the axis L1. Since the supply flow rate and the return flow rate to the external actuator can be controlled with a mechanically simple structure, it is possible to improve cost, reliability and the like. In addition, the first control valve 51 is provided on an extension of the rotation shaft 42 of the operation lever 4 and moves forward and backward along the axis L1.
2 moves forward and backward in a direction orthogonal to the rotation axis L1, so that the degree of freedom in the arrangement position of the second control valve 52 increases, 2 moves forward and backward in a direction orthogonal to the rotation axis L1, so that the degree of freedom in the arrangement position of the second control valve 52 increases,
The device can be made compact. The present invention is not limited to the above embodiment. For example, as shown in FIG. 5, a ball BB and a rod LL may be used in place of the poppet, and the cross section of the threaded rod is not limited to an ellipse. May be formed. In addition, other structures of the interlocking mechanism are conceivable, and it goes without saying that various modifications such as the outer shape of the apparatus and the arrangement position of each member are possible. According to the present invention described in detail above, the opening of the control valve is changed in accordance with the turning angle of the operating lever in the ON region, so that even when the electric motor is started, the operation of the hydraulic pump is stopped. Since it is possible to prevent the discharged working fluid from being immediately supplied to the external actuator, The device can be made compact. The present invention is not limited to the above embodiment. For example, as shown in FIG. 5, a ball BB and a rod LL may be used in place of the poppet, and the cross section of the threaded rod is not limited to an ellipse. May be formed. In addition, other structures of the interlocking mechanism are conceivable, and it goes without saying that various modifications such as the outer shape of the apparatus and the arrangement position of each member are possible According to the present invention described in detail above, the opening of the control valve is changed in accordance with the turning angle of the operating lever in the ON region, so that even when the electric motor is started, the operation of the delivery pump is stopped. Since it is possible to prevent the ellipsed working fluid from being immediately supplied to the external actuator,
That is, when the hydraulic pump is started, a shock or the like caused by supplying the working fluid to the external actuator at once can be suppressed. Further, since the operating lever for operating the electric motor is also used for operating the control valve by using the interlocking mechanism, the number of parts can be reduced, and the cost and reliability are excellent. It can be. In addition, since the control valve moves back and forth in a direction different from the rotation axis of the operation lever, the degree of freedom of the arrangement position of the control valve is increased, and the apparatus can be made compact. That is, when the hydraulic pump is started, a shock or the like caused by supplying the working fluid to the external actuator at once can be suppressed. Further, since the operating lever for operating the electric motor is also used for operating the control valve by using the interlocking mechanism, the number of parts can be reduced, and the cost and reliability are excellent. It can be. In addition, since the control valve moves back and forth in a direction different from the rotation axis of the operation lever, the degree of freedom of the arrangement position of the control valve is increased, and the apparatus can be made compact.

【図面の簡単な説明】 【図1】本発明の一実施形態における液圧装置の正面
図。 【図2】同実施形態における液圧装置の側面図。 【図3】同実施形態における液圧装置の液圧回路図。 【図4】同実施形態における液圧装置の内部構造を示す
概略縦断面図。 【図5】本発明の他の実施形態における液圧装置の内部
構造を示す概略縦断面図。 【符号の説明】 1・・・電動機 P1・・・吐出口 2・・・液圧ポンプ 3・・・タンク A_ON・・・オン領域 A_OF・・・オフ領域 4・・・操作レバー R3・・・連通経路(第2分岐経路) L1・・・回動軸線 52・・・制御弁(第2制御弁) 62・・・連動機構(第2連動機構)
BRIEF DESCRIPTION OF THE DRAWINGS FIG. 1 is a front view of a hydraulic device according to an embodiment of the present invention. FIG. 2 is a side view of the hydraulic device in the embodiment. FIG. 3 is a hydraulic circuit diagram of the hydraulic device according to the embodiment. FIG. 4 is a schematic longitudinal sectional view showing the internal structure of the hydraulic device in the embodiment. FIG. 5 is a schematic longitudinal sectional view showing the internal structure of a hydraulic device according to another embodiment of the present invention. [Description of Signs] 1 ... Electric motor P1 ... Discharge port 2 ... Hydraulic pump 3 ... Tank A_ON ... On area A_OF ... Off area 4 ... Operation lever R3 ... Communication path (second branch path) L1 ... rotation axis 52 ... control valve (second control valve) 62 ... interlocking mechanism (second interlocking mechanism)

Claims (1)

  1. 【特許請求の範囲】 【請求項1】電動機と、 この電動機により駆動されて吐出口から流体を吐出する
    液圧ポンプと、 タンクと、 所定のオン領域に回動操作すると前記電動機を作動さ
    せ、前記オン領域とは別に設定されたオフ領域に回動操
    作すると前記電動機を停止させる操作レバーと、 前記液圧ポンプの吐出口と前記タンクとを連通する連通
    経路と、 前記操作レバーの回動軸線と異なる方向に進退動作し、
    前記連通経路を通過する流体の流量を制御する制御弁と、 前記操作レバーのオン領域における回動動作を前記制御弁の進退動作に連動させる連動機構とを具備することを特徴とする液圧装置。 A hydraulic device including a control valve that controls the flow rate of a fluid passing through the communication path, and an interlocking mechanism that links the rotation operation of the operating lever in the on region with the advancing / retreating operation of the control valve. .. Claims: 1. An electric motor, a hydraulic pump driven by the electric motor to discharge a fluid from a discharge port, a tank, and a rotary operation to a predetermined on area activates the electric motor. An operation lever that stops the electric motor when rotated to an off area that is set separately from the on area; a communication path that communicates a discharge port of the hydraulic pump with the tank; and a rotation axis of the operation lever. Move in different directions from Claims: 1. An electric motor, a hydraulic pump driven by the electric motor to discharge a fluid from a discharge port, a tank, and a rotary operation to a predetermined on area activates the electric motor. An operation lever that stops the electric motor. When rotated to an off area that is set separately from the on area; a communication path that communicates a discharge port of the hydraulic pump with the tank; and a rotation axis of the operation lever. Move in different directions from
    A hydraulic valve, comprising: a control valve that controls a flow rate of a fluid passing through the communication path; and an interlocking mechanism that interlocks a rotation operation of the operation lever in an ON region with an advance / retreat operation of the control valve. . A flow valve, comprising: a control valve that controls a flow rate of a fluid passing through the communication path; and an interlocking mechanism that interlocks a rotation operation of the operation lever in an ON region with an advance / retreat operation of the control valve ..
JP2001235748A 2001-08-03 2001-08-03 Hydraulic device Pending JP2003049781A (en)

Priority Applications (1)

Application Number Priority Date Filing Date Title
JP2001235748A JP2003049781A (en) 2001-08-03 2001-08-03 Hydraulic device

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
JP2001235748A JP2003049781A (en) 2001-08-03 2001-08-03 Hydraulic device

Publications (1)

Publication Number Publication Date
JP2003049781A true JP2003049781A (en) 2003-02-21

Family

ID=19067143

Family Applications (1)

Application Number Title Priority Date Filing Date
JP2001235748A Pending JP2003049781A (en) 2001-08-03 2001-08-03 Hydraulic device

Country Status (1)

Country Link
JP (1) JP2003049781A (en)

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP1628020A3 (en) * 2004-08-17 2008-09-03 Jungheinrich Aktiengesellschaft Fluid circuit and industrial truck with fluid circuit

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP1628020A3 (en) * 2004-08-17 2008-09-03 Jungheinrich Aktiengesellschaft Fluid circuit and industrial truck with fluid circuit

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