JPS58131405A - Driving unit for hydraulic motor - Google Patents
Driving unit for hydraulic motorInfo
- Publication number
- JPS58131405A JPS58131405A JP57013121A JP1312182A JPS58131405A JP S58131405 A JPS58131405 A JP S58131405A JP 57013121 A JP57013121 A JP 57013121A JP 1312182 A JP1312182 A JP 1312182A JP S58131405 A JPS58131405 A JP S58131405A
- Authority
- JP
- Japan
- Prior art keywords
- hydraulic motor
- pressure
- passage
- supply
- valve
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
- Pending
Links
- 230000007935 neutral effect Effects 0.000 abstract description 6
- 239000012530 fluid Substances 0.000 abstract 1
- 230000007423 decrease Effects 0.000 description 4
- 238000005086 pumping Methods 0.000 description 3
- 238000010586 diagram Methods 0.000 description 2
- 230000000694 effects Effects 0.000 description 2
- 239000003638 chemical reducing agent Substances 0.000 description 1
- 230000006866 deterioration Effects 0.000 description 1
- 210000000554 iris Anatomy 0.000 description 1
- 238000004904 shortening Methods 0.000 description 1
- XLYOFNOQVPJJNP-UHFFFAOYSA-N water Substances O XLYOFNOQVPJJNP-UHFFFAOYSA-N 0.000 description 1
Classifications
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16H—GEARING
- F16H61/00—Control functions within control units of change-speed- or reversing-gearings for conveying rotary motion ; Control of exclusively fluid gearing, friction gearing, gearings with endless flexible members or other particular types of gearing
- F16H61/38—Control of exclusively fluid gearing
- F16H61/40—Control of exclusively fluid gearing hydrostatic
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
- F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
- F15B11/00—Servomotor systems without provision for follow-up action; Circuits therefor
- F15B11/02—Systems essentially incorporating special features for controlling the speed or actuating force of an output member
- F15B11/04—Systems essentially incorporating special features for controlling the speed or actuating force of an output member for controlling the speed
- F15B11/044—Systems essentially incorporating special features for controlling the speed or actuating force of an output member for controlling the speed by means in the return line, i.e. "meter out"
- F15B11/0445—Systems essentially incorporating special features for controlling the speed or actuating force of an output member for controlling the speed by means in the return line, i.e. "meter out" with counterbalance valves, e.g. to prevent overrunning or for braking
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
- F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
- F15B2211/00—Circuits for servomotor systems
- F15B2211/30—Directional control
- F15B2211/305—Directional control characterised by the type of valves
- F15B2211/30525—Directional control valves, e.g. 4/3-directional control valve
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
- F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
- F15B2211/00—Circuits for servomotor systems
- F15B2211/40—Flow control
- F15B2211/405—Flow control characterised by the type of flow control means or valve
- F15B2211/40515—Flow control characterised by the type of flow control means or valve with variable throttles or orifices
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
- F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
- F15B2211/00—Circuits for servomotor systems
- F15B2211/40—Flow control
- F15B2211/415—Flow control characterised by the connections of the flow control means in the circuit
- F15B2211/41527—Flow control characterised by the connections of the flow control means in the circuit being connected to an output member and a directional control valve
- F15B2211/41536—Flow control characterised by the connections of the flow control means in the circuit being connected to an output member and a directional control valve being connected to multiple ports of an output member
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
- F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
- F15B2211/00—Circuits for servomotor systems
- F15B2211/40—Flow control
- F15B2211/42—Flow control characterised by the type of actuation
- F15B2211/428—Flow control characterised by the type of actuation actuated by fluid pressure
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
- F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
- F15B2211/00—Circuits for servomotor systems
- F15B2211/50—Pressure control
- F15B2211/505—Pressure control characterised by the type of pressure control means
- F15B2211/50509—Pressure control characterised by the type of pressure control means the pressure control means controlling a pressure upstream of the pressure control means
- F15B2211/50545—Pressure control characterised by the type of pressure control means the pressure control means controlling a pressure upstream of the pressure control means using braking valves to maintain a back pressure
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
- F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
- F15B2211/00—Circuits for servomotor systems
- F15B2211/70—Output members, e.g. hydraulic motors or cylinders or control therefor
- F15B2211/705—Output members, e.g. hydraulic motors or cylinders or control therefor characterised by the type of output members or actuators
- F15B2211/7058—Rotary output members
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
- F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
- F15B2211/00—Circuits for servomotor systems
- F15B2211/80—Other types of control related to particular problems or conditions
- F15B2211/86—Control during or prevention of abnormal conditions
- F15B2211/8609—Control during or prevention of abnormal conditions the abnormal condition being cavitation
Landscapes
- Engineering & Computer Science (AREA)
- General Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- Physics & Mathematics (AREA)
- Fluid Mechanics (AREA)
- Operation Control Of Excavators (AREA)
- Safety Valves (AREA)
- Fluid-Pressure Circuits (AREA)
Abstract
Description
【発明の詳細な説明】
本発明はクローラ式車輛等の走行駆動用油圧モータの駆
動装置に関する。DETAILED DESCRIPTION OF THE INVENTION The present invention relates to a drive device for a hydraulic motor for driving a crawler vehicle or the like.
従来、油圧モータと油圧ポンプおよびタンクとをｉ１通
する一対の給排路を有し、該一対の給排路の途中にカウ
ンターバランス弁および方向切換弁を設けた油圧モータ
の駆動装置が知られており、クローラ式車輛婢の低速走
行駆動に用いられている。油圧シ１ベル等のクローラ式
車輛等は近年走行の高速化が望まれており、かつ高速化
しても車輪停止時の操作フィーリングを損なわない油圧
量−夕の駆動装置が請求されている◇高速化した場合、
停止に伴う車体の慣性力が大きくなるので、停止時の装
置内圧力変化を滑らかにし操作フィーリングを良くする
ためには、停止時までの時間を長くする（カウンターバ
ランス弁のスプールの移動時間を長くすることくより得
られる）会費がある。しかしながら、該時間を長くする
と油圧モータの慣性力増大に伴うポンプ作用時、油圧モ
ータへの供給側となっていた給排路にキャビテーション
が発生し、騒音が増大するとともに油圧モータの性能お
よび耐久性を低下させるのである。また、キャビテーシ
ョンを肪止するために１停止時までの時間を燗くする（
カウンターバランス弁の移動時間を短くすることによシ
得られる）ことも考えられるが、この場合には急激に停
止するので、シ四ツクが発生し操作フィーリングが患〈
なるのである。Hitherto, a hydraulic motor drive device has been known which has a pair of supply/discharge passages that connect the hydraulic motor, a hydraulic pump, and a tank, and a counterbalance valve and a directional switching valve are provided in the middle of the pair of supply/discharge passages. It is used for low-speed driving of crawler vehicles. In recent years, crawler-type vehicles such as hydraulic cylinders have been desired to run at higher speeds, and there is also a demand for a drive system with a hydraulic pressure that does not impair the operating feeling when the wheels are stopped even at higher speeds◇ If the speed is increased,
The inertial force of the vehicle body increases when the vehicle stops, so in order to smooth out the pressure change inside the device and improve the operating feeling when the vehicle stops, the time until the vehicle stops is increased (by increasing the travel time of the counterbalance valve spool). There is a membership fee (you can get more from it by making it longer). However, if this time is increased, cavitation will occur in the supply/discharge path that is the supply side to the hydraulic motor when the pump operates due to the increase in inertia of the hydraulic motor, increasing noise and reducing the performance and durability of the hydraulic motor. This results in a decrease in Also, to prevent cavitation, the time until the first stop is increased (
It is possible that this could be achieved by shortening the travel time of the counterbalance valve, but in this case, it would stop suddenly, resulting in shuffling and the operation feeling would be affected.
It will become.
本発明は以上の欠点に鑑みなされ友ものであり、一対の
給排路の一方側の圧力が負圧に＆っ走時、一対の給排路
を連通させる切換弁を備えるととによって、クロー２式
車輛等の走行の高速化（油圧モータの高速化）に伴う車
輌停止時のキャビテーションを防止し、かつ操作フィー
リングをも満足する油圧モータの駆動装置を提供するこ
とを目的とする。The present invention has been developed in view of the above drawbacks, and includes a switching valve that allows the pair of supply and discharge passages to communicate with each other when the pressure on one side of the pair of supply and discharge passages becomes negative pressure. It is an object of the present invention to provide a hydraulic motor drive device that prevents cavitation when the vehicle is stopped due to the speeding up of a Type 2 vehicle (higher speed of the hydraulic motor) and also provides a satisfactory operating feeling.
以下図面を参照して本発明の詳細な説明する。The present invention will be described in detail below with reference to the drawings.
本発明の第１実施例を示す第１図および第２図において
、（１） （３）ＪＩｉ、油圧モータ （５）と油圧ポ
ンプ（７）およびタンク（９）とを連通ずる一対の給排
路である。1 and 2 showing the first embodiment of the present invention, (1) (3) JIi, a pair of supply/discharge ports that communicate the hydraulic motor (5) with the hydraulic pump (7) and tank (9). It is a road.
（１１）は、（４）０３）Ωの三位型状態に切換えられ
る手動方向切換弁であシ、その（ａ） Ｔｏ） （ｅ）
（ｄ）ボートが一対の給排路（１） （５）に接続され
ている。(11) is a manual directional valve that is switched to the three-position state of (4)03)Ω, its (a) To) (e)
(d) A boat is connected to a pair of supply and discharge channels (1) and (5).
（１５）は、（Ｄ）（ト）（ト）の三位型状態に切換え
られるカウンターバランス弁であシ、その本体（１５）
は、一対の給排路（１） （５）Ｋ接続される一対の第
１通路（１７）（１９）および一対の第２通路（２１）
（２５） 、第１通路（１７） （１９）から第
２通路（２１） （２５）への圧油０流れのみを許容
するチェック弁体（２５） （２７）およびスプリン
グ（２９） （５１）からなるチェック弁（３３）
（３５）、その移動により１ｓ１通路（１７） （
１９）および第２通路（２１） （２３）を連通を九
は遮断するスプール（５７）、スプール（５７）を収納
する収納孔（５９） 、スプール（３７）を圧油の供給
が無い時中立位置に保持するスプリング（４１） （
４３）、スプール端面部に圧油を導入する第１パイロッ
ト通路（４５） （４７） 、第１通路（１７）
（１９）より分岐され九一対の第３通路（４９） （
５１） 、菖１通路（１７） （１？）の一方または
両方に接続されるパイロット通路（５３）、絞シ部（５
５） （５７）、を備えている。そして、このカウン
ターバランス弁（１５）は油圧モータ（５）のポンプ作
用時油圧七−タ（５）Ｋ液圧ブレーキ作用を付与するも
のである。(15) is a counterbalance valve that can be switched to the three-position state of (D) (G) (G), and its main body (15)
A pair of supply/discharge passages (1) (5) K A pair of connected first passages (17) (19) and a pair of second passages (21)
(25), a check valve body (25) (27) that allows only zero flow of pressure oil from the first passage (17) (19) to the second passage (21) (25), and a spring (29) (51) Check valve (33) consisting of
(35), due to its movement 1s1 passage (17) (
19) and the second passages (21) and (23), a spool (57) that blocks communication, a storage hole (59) that stores the spool (57), and a spool (37) that is neutralized when no pressure oil is supplied. Spring (41) to hold it in position (
43), first pilot passage (45) (47), first passage (17) that introduces pressure oil into the spool end face
91 pairs of third passages (49) branched from (19) (
51), a pilot passage (53) connected to one or both of the irises 1 passage (17) (1?), and a diaphragm part (5
5) (57). The counterbalance valve (15) provides a hydraulic braking action to the hydraulic motor (5) when the hydraulic motor (5) is pumping.
（５９）は、一対の給排路の一方側の圧力が負圧になっ
た時一対の給排路（１） （５）を連通させる二位置
切換弁であり、その本体（６１）は、カウンターバラン
ス弁の第３通路（４９）と接続する第１通路（１５！ｌ
） 、カウンターバランス弁の第３通路（５１）と接続
する通ｊ３ （（５５）および第１孔（６７）からなる
第２通路（６９） 、その移動によね第１通路（６３）
および第２通路（６９）を連通または連断するスプール
（７１）、スプールの一端部および他端部を摺動可能に
収納した第２孔（７５）および第３孔（７５）、第２孔
（７６）に収納され油圧モータの通常運転時第１通路（
６３）および第２通路（６９）を遮断するようスプール
（７１）’を押付けるスプリング（７７）、スプール（
７１）内に形成され第１通路（６３）および第３孔（７
５）を連通ずる第４孔（７９） 、カウンターバランス
弁のパイロット通路（５５）および第２孔（７３）を連
通するパイロット通路（８１）、を備えている。(59) is a two-position switching valve that connects the pair of supply and discharge passages (1) and (5) when the pressure on one side of the pair of supply and discharge passages becomes negative pressure, and its main body (61) is The first passage (15!l) connects with the third passage (49) of the counterbalance valve.
), the second passage (69) consisting of (55) and the first hole (67) connects with the third passage (51) of the counterbalance valve, and the first passage (63) due to its movement.
and a spool (71) that communicates or connects the second passageway (69), a second hole (75) and a third hole (75) that slidably accommodate one end and the other end of the spool, and a second hole (76) and is stored in the first passage (76) during normal operation of the hydraulic motor.
63) and a spring (77) that presses the spool (71)' to block the second passage (69), the spool (
formed in the first passageway (63) and the third hole (71).
5), a pilot passage (81) that communicates with the pilot passage (55) of the counterbalance valve, and the second hole (73).
（ｉｏｏ）は、クローラ式車輛のクローラシューに係合
するスプロケットホイールである。（２００）は、油圧
モータの回転を減速してスプロケットホイールへ伝達す
る減速機である。(ioo) is a sprocket wheel that engages with a crawler shoe of a crawler vehicle. (200) is a speed reducer that reduces the rotation of the hydraulic motor and transmits it to the sprocket wheel.
本発明のｌｌＩ２実施例を示す第３図において、同じ符
号は同じ部品を示しているが、第１図の場合と区別する
ため符号にダッシュをつけて示している。切換弁（５９
’）の構造は切換弁（５９）の構造と多少異なるが、い
ずれも本＠明の作用効果を奏するものである。第２図の
切換弁（５９）のＷＸ４孔（７９）を設けず、第６孔（
７５）およびタンク（９′） を連通する連通路（９０
）を具備すれば、切換弁（５９’）の構造となるのでお
る。In FIG. 3 showing the llI2 embodiment of the present invention, the same reference numerals indicate the same parts, but the numbers are shown with a dash to distinguish them from the case of FIG. Switching valve (59
Although the structure of ') is somewhat different from that of the switching valve (59), both of them achieve the effects of this invention. The WX4 hole (79) of the switching valve (59) in Fig. 2 is not provided, and the 6th hole (
75) and the tank (9').
), the structure becomes a switching valve (59').
次に本発明の作用についてａ＠＃する。第１図および第
２図において、方向切換弁（１１）をＡ位置に操作する
と油圧ポンプ（７）からの吐出油は給排路（１）より油
圧モータ（５）へ流入する。Next, let's talk about the effects of the present invention. In FIGS. 1 and 2, when the directional control valve (11) is operated to the A position, oil discharged from the hydraulic pump (7) flows into the hydraulic motor (5) from the supply/discharge path (1).
この時カウンタ−バランス弁（１６）はＤ位ＩＩＫ切換
えられる。油圧モータ（５）からの流出油は給排路（５
）よりタンク（９）へ排出妊れる。油圧ボンダ（７）か
らの吐出油鉱、また、パイロット通路（５３）および（
８１）を通って第２孔（７３）へ導入される。従って、
スプール（７１）は第１通路（６５）および第２通路（
６９）を遮断するよう押付けられている。すなわち、通
常運転時には、一対の給排路（１） （３層；切換弁
（５９）によって連通されてないのである。At this time, the counter balance valve (16) is switched to the D position IIK. The oil spilled from the hydraulic motor (5) is
) from the tank (9). The oil ore discharged from the hydraulic bonder (7) and also the pilot passage (53) and (
81) and is introduced into the second hole (73). Therefore,
The spool (71) has a first passage (65) and a second passage (
69) is pressed to block it. That is, during normal operation, the pair of supply/discharge passages (1) (three layers; not communicated by the switching valve (59)).
油圧モータ（５）を停止させる場合、方向切換弁を中立
のＣ位置へ操作させると、カウンターバランス弁（１５
）は中立のＦ位置へ復帰しつつ液圧ブレーキ力を油圧モ
ータ（５）へ徐々に付与するのである。その時、高速運
転されていた車輌の大きな慣性力が油圧モータ（５）に
加わり、油圧モータ（５）はポンプ作用を行うようにな
り、給排路（１）の圧力は負圧となるのである。従って
、パイロット通路（５５）および（８１）からスプール
（７１）の端部へ導入されていた圧油の圧力が、第１通
路（１９）に生じていた背圧（この背圧は第３通路（５
１）、第２通路（６９）Ｋ導入されている）より低下し
、スプール（７１）のバランスがくずれ、背圧を有する
第１通路（１９）すなわち、給排路（１）の圧力が負圧
になシキャビテーションが発生しようとした時、切換弁
（５９） Ｋよって給排路（１）および（３）を連通さ
せるようなしているので、油の不足分を速やかに補充す
ることができ、キャビテーションを防止することができ
る。なお、方向切換弁（１１）をＢ位置に操作し運転し
ていた場合、停止させるためＣ位置へ操作した時も前述
と同様キャビデーション肪止を行うことができる。また
、油圧モータ（５）を停止させる場合、方向切換弁（１
１）をＣ位置にしているので油圧ポンプ（７）の吐出油
はタンク圧に低下している。そして、そのタンク圧を吸
込むことができると考えられるが、実際には、カウンタ
ーバランス弁（１Ｓ）は、スプロケットホイール（１０
０）近傍の走行フレームへ取付けられる油圧モータ（５
）Ｋ直結され、方向切換弁（１１）は上部車体の１１１
１１１ｔｉした場所へ設置されるので、カウンターバラ
ンス弁（１３）および方向切換弁（１１）間の一対の給
排路が長くて速やかに吸込むことは困難である。When stopping the hydraulic motor (5), the counterbalance valve (15) is activated by operating the directional control valve to the neutral C position.
) gradually applies hydraulic brake force to the hydraulic motor (5) while returning to the neutral F position. At that time, the large inertial force of the vehicle that was being driven at high speed is applied to the hydraulic motor (5), and the hydraulic motor (5) begins to perform a pumping action, causing the pressure in the supply and discharge passage (1) to become negative pressure. . Therefore, the pressure of the pressure oil introduced from the pilot passages (55) and (81) to the end of the spool (71) is reduced by the back pressure generated in the first passage (19) (this back pressure is (5
1), the pressure in the first passage (19), that is, the supply/discharge passage (1), which has back pressure, becomes negative as the spool (71) becomes unbalanced. When cavitation is about to occur in the oil pressure, the switching valve (59) K allows the supply and discharge passages (1) and (3) to communicate with each other, so that the shortage of oil can be quickly replenished. , cavitation can be prevented. In addition, when the directional control valve (11) is operated to the B position and the operation is performed, the cavitation fat stop can be performed in the same manner as described above when the directional control valve (11) is operated to the C position to stop the operation. In addition, when stopping the hydraulic motor (5), the directional control valve (1
1) is in the C position, the oil discharged from the hydraulic pump (7) has dropped to the tank pressure. It is thought that the tank pressure can be sucked in, but in reality, the counterbalance valve (1S) is connected to the sprocket wheel (10
0) Hydraulic motor (5) attached to the nearby traveling frame
) K is directly connected, and the directional control valve (11) is connected to 111 on the upper vehicle body.
111ti, the pair of supply and discharge passages between the counterbalance valve (13) and the directional control valve (11) are long, making it difficult to draw in water quickly.
第６図において、第１図の説明の如く油圧モータ（５）
を停止させる場合、給排路（１）の圧力が負圧になると
、パイロット通路（８１’）の圧力が連通路（９０）の
ドレン圧より低下し、スプールのバランスがくずれ、背
圧を有する第２通路（６９’）内の油は第１通路（６５
’）に流入するのである。すなわち、第５図の場合も、
給排路（１）の圧力が負圧になりキャビテーションが発
生しようとした時切換弁（５９’）によって給排路（１
）および（３）を連通させるようなしているのであるＯ
以上説明したように本発明によれば、クローラ式車輛等
の走行の高速化に伴う停止時のキャビテーションを防止
することができ、騒音の発生、油圧モータの性能および
耐久性の低下を防止できる。また、カウンターバランス
弁のスプールの移動速度を従来より短かくする変史を行
わずにキヤビテーシヨンを防止するようなし得ているの
で操作フィーリングを悪くすることがない。In FIG. 6, as explained in FIG. 1, the hydraulic motor (5)
If the pressure in the supply/discharge path (1) becomes negative, the pressure in the pilot path (81') will drop below the drain pressure in the communication path (90), causing the spool to become unbalanced and creating back pressure. The oil in the second passage (69') is
'). In other words, also in the case of Figure 5,
When the pressure in the supply and discharge passage (1) becomes negative and cavitation is about to occur, the switching valve (59') closes the supply and discharge passage (1).
) and (3) are communicated with each other.As explained above, according to the present invention, it is possible to prevent cavitation when a crawler vehicle, etc. is stopped due to increased running speed, and to reduce noise. This can prevent deterioration in the performance and durability of the hydraulic motor. Furthermore, since cavitation can be prevented without changing the movement speed of the spool of the counterbalance valve to be shorter than before, the operation feeling does not deteriorate.
第１図社本発明の第１実施例を示す回路図、第２図は本
発明の第１実施例の切換弁およびカウンターバランス弁
の断面図、
第３図は本発明の第２実施例を示す回路図、である。
符号の説明
（１） （５） −・・−・一対の給排路、（１３
） ・・・−カウンターバランス弁、（１１）
・−・・方向切換弁、
（５９） （５９’）−・・切換弁、（１７） （
１９）・・・−・第１通路、（４９） （５１）−第
５通路、
（６５） （６５’）・・・第１通路、（６９）
（４９’）−第２通路、
（５５） −・パイロット通路、（８１） （
８１’）・・・パイロット通路。
第 ２ 図
手続補正書
昭和５７年 ３ 月−夕日
昭和５７年特許願第 １！＄１２１ 号２、発明
の名称
油圧毫−夕の駆動装置
３、補正をする者
事件との関係、特許出願人
名称 帝人製機株式会社
霞が関ビル内郵便局 私書第第４９１
栄光特許事務所 電話（５８１）−９６０１（代表）別
紙
「油圧モータ（５）を回転させ走行運転する場合、方向
切換弁（１１）をム位置へ操作すると、油圧Ｉンプ（７
）からの吐出油は、カウンターバランス弁（１Ｓ）の第
１パイロット通路（４５）へ導入され、スプリング（４
５）を圧縮しそのスプール（３７）を右方へ移動させる
（Ｄ位置に切換えられる）と共に、第１通路（１７）チ
ェック弁（３３）第２通路（２１）を通）油圧モータ（
５）へ流入する。すなわち、油圧モータ（５）は給排路
（１）及びＤ位置に切換えられ喪カウン）−／（ランス
弁（１５）内を通る供給油によって回転する。同時に、
吐出油はパイロット通路（５３）及び二位置切換弁（５
９）のパイロット通路（８１）を過多第２孔（７３）へ
導入されスプール（７１）を右方へ押付ける。従って、
そのスプール（７１）祉第２図の位値過少に保持され、
第Ｓ通路（４９）Ｋ連通している第１通路（１７）及び
第５通路（５１）Ｋ連通している第１通路（１９）は％
遮断されていることになる。
一方、油圧量−！（５）・かもの流出油はカウンターバ
ランス弁（１１０第２通路（２５）第１通路（１り及び
方向切換弁（１１）を通）タンク（りへ排出される。ζ
ＯＷ＊、カウンターバランス弁（１１）及び切換弁（５
り内部の一般的に＊＊積が小さい通路を通る排出油は抵
抗を受妙過常背圧が付与されているＯである。
次に油圧毫−タ（５）を停止させる場合、方向切換弁（
１１）を中立００位置へ操作すると、油圧ポンプ（７）
の吐出油はタンク（９）へ直接戻され、そＯ圧力はタン
ク圧に低下する。
吐出圧すなわち油圧モータ（５）への供給油の圧力が低
下するとカウンターバランス弁（１５）Ｏ第１パイロッ
ト通路（４５）内の圧力も低下するＯで、スプール（５
７）ａ圧縮されてい友スプリング（４３）０豐元力によ
って中立の１位置へ復帰すゐ。スツールＣ５７）０１位
置への移動によ〉、連通していえ第２通路（２３）及び
第１通路（１りは徐々Ｋｌｌ断され、油圧モータ（５）
へ徐々にブレーキを付与するのである。その時、高速運
転されてい九車輛の大き１慣性力が油圧モータ（５）に
加わり、油圧モータ（５）はポンプ作用を行い、給排路
（１）第２通路（２１）４１１通路（１７）内の圧力は
負圧に低下するのである。
従って、パイロット通路（５３）（８１）及び第２孔（
７３）内の圧力が、＃！１通路（１９）第３通路（５１
）第２通路（６９）に生じていた背圧よシ低下し、スプ
ール（７１）のバランスがくずれ（第１孔６７内の背圧
によ）スプリング７７を圧縮しスプール７１唸左方に移
動する）背圧を有する第１通路（１９）内の油が第１通
路（１７）に流入するのである。す表わち、給排路（１
）の圧力が負圧になシャヤビテーションが発生しようと
した時、切換弁（５りが切換わ〉給排路（１）及び給排
路（５）を連通させるようなしているので、油の不足分
を速やかに補充することかで１ｋｄＰヤビテーシ冒ンを
防止することができる。攻お、方向切換弁（１１）を１
位置へ操作し逆転運転している時、停止させる丸めＷＣ
Ｃｊ位置へ操作し友場合も、前述と同様キャビテーショ
ン防止は可能である。すなわち、Ｒｏ切換弁（５？ ）
Ｆｉ油圧モータ（５）の両方１１１１’ｌｉ ｆＥＫ対
処てきるものである。Figure 1 is a circuit diagram showing the first embodiment of the present invention, Figure 2 is a sectional view of the switching valve and counterbalance valve of the first embodiment of the present invention, and Figure 3 is a circuit diagram showing the second embodiment of the present invention. FIG. Explanation of symbols (1) (5) - Pair of supply and discharge passages, (13
) ...-Counterbalance valve, (11)
... Directional switching valve, (59) (59') --... Directional switching valve, (17) (
19)...--First passage, (49) (51)-Fifth passage, (65) (65')...First passage, (69)
(49') - Second passage, (55) - Pilot passage, (81) (
81')...Pilot passage. Figure 2 Procedural Amendment Document March 1982 - Sunset Patent Application No. 1 of 1982! $121 No. 2, Name of the invention Hydraulic cylinder-Yuu drive device 3, Relationship with the amended case, Name of patent applicant Teijin Seiki Co., Ltd. Kasumigaseki Building Post Office Private Letter No. 491 Eiko Patent Office Telephone (581)-9601 (Representative) Attachment ``When driving by rotating the hydraulic motor (5), when the directional control valve (11) is operated to the
) is introduced into the first pilot passage (45) of the counterbalance valve (1S), and the oil discharged from the spring (4
5) and moves its spool (37) to the right (switched to position D), the hydraulic motor (through the first passage (17), check valve (33), second passage (21))
5). That is, the hydraulic motor (5) is switched to the supply/discharge path (1) and the D position and is rotated by the oil supplied through the lance valve (15).
Discharge oil is supplied through the pilot passage (53) and the two-position switching valve (5
The pilot passage (81) of 9) is introduced into the excess second hole (73) and pushes the spool (71) to the right. Therefore,
The spool (71) is held at an undervalue in Figure 2,
The first passage (17) and the fifth passage (51) K are connected to each other by %
It will be blocked. On the other hand, the amount of oil pressure -! (5) - The spilled oil is discharged to the tank (through the counterbalance valve (110), second passage (25), first passage (1) and directional control valve (11)).ζ
OW*, counterbalance valve (11) and switching valve (5
The draining oil that passes through the internal passageway, which generally has a small volume, is subjected to excessive backpressure due to resistance. Next, when stopping the hydraulic cylinder (5), the directional control valve (
11) to the neutral 00 position, the hydraulic pump (7)
The discharged oil is directly returned to the tank (9), and its O pressure is reduced to the tank pressure. When the discharge pressure, that is, the pressure of oil supplied to the hydraulic motor (5) decreases, the pressure inside the counterbalance valve (15) O first pilot passage (45) also decreases.
7) A compressed spring (43) returns to the neutral position with zero force. By moving the stool C57) to the 01 position, the communication between the second passage (23) and the first passage (1) is gradually cut off, and the hydraulic motor (5)
The brakes are gradually applied to the vehicle. At that time, a large inertial force of the vehicle being operated at high speed is applied to the hydraulic motor (5), and the hydraulic motor (5) performs a pumping action, and the supply/discharge passage (1), the second passage (21), the 411 passage (17) The internal pressure drops to negative pressure. Therefore, the pilot passage (53) (81) and the second hole (
73) The pressure inside is #! 1st aisle (19) 3rd aisle (51
) The back pressure generated in the second passage (69) decreases, causing the spool (71) to become unbalanced (due to the back pressure in the first hole 67), compressing the spring 77 and causing the spool 71 to move to the left. The oil in the first passage (19) with back pressure flows into the first passage (17). In other words, the supply/discharge path (1
) When the pressure becomes negative and syavitation is about to occur, the switching valve (5) switches to connect the supply/discharge path (1) and the supply/discharge path (5). 1 kdP damage can be prevented by quickly replenishing the insufficient amount of oil.
Rounding WC that stops when operating in reverse position and operating in reverse.
Cavitation can be prevented in the same manner as described above even when the operation is performed to the Cj position. In other words, Ro switching valve (5?)
Fi hydraulic motor (5) is compatible with both 1111'li fEK.
Claims (1)
の給排路を有し、該一対の給排路の途中にカウンターバ
ランス弁および方向切換弁を設けた油圧モータの駆動装
置において、前記一対の給排路の一方個の圧力が負圧に
なった時、前記一対の給排路を連通させる切換弁を備え
たことを特徴とする油圧モータの駆動装置。In a hydraulic motor drive device, the hydraulic motor has a pair of supply/discharge passages that communicate with the hydraulic motor, a hydraulic pump, and a tank, and a counterbalance valve and a direction switching valve are provided in the middle of the pair of supply/discharge passages. A hydraulic motor drive device comprising a switching valve that connects the pair of supply/discharge passages when pressure in one of the discharge passages becomes negative pressure.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP57013121A JPS58131405A (en) | 1982-01-29 | 1982-01-29 | Driving unit for hydraulic motor |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP57013121A JPS58131405A (en) | 1982-01-29 | 1982-01-29 | Driving unit for hydraulic motor |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| JPS58131405A true JPS58131405A (en) | 1983-08-05 |
Family
ID=11824319
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP57013121A Pending JPS58131405A (en) | 1982-01-29 | 1982-01-29 | Driving unit for hydraulic motor |
Country Status (1)
| Country | Link |
|---|---|
| JP (1) | JPS58131405A (en) |
Cited By (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPS6038901U (en) * | 1983-08-26 | 1985-03-18 | 帝人製機株式会社 | fluid brake device |
| FR2674580A1 (en) * | 1991-03-27 | 1992-10-02 | Bobard Jeune Sa Ets | Device for controlling a hydraulic boost motor |
| EP1120573A2 (en) * | 1999-12-27 | 2001-08-01 | Kayaba Kogyo Kabushiki Kaisha | Hydraulic drive unit with counter balancing valve |
Citations (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPS5711305B2 (en) * | 1975-12-27 | 1982-03-03 |
-
1982
- 1982-01-29 JP JP57013121A patent/JPS58131405A/en active Pending
Patent Citations (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPS5711305B2 (en) * | 1975-12-27 | 1982-03-03 |
Cited By (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPS6038901U (en) * | 1983-08-26 | 1985-03-18 | 帝人製機株式会社 | fluid brake device |
| JPH0351521Y2 (en) * | 1983-08-26 | 1991-11-06 | ||
| FR2674580A1 (en) * | 1991-03-27 | 1992-10-02 | Bobard Jeune Sa Ets | Device for controlling a hydraulic boost motor |
| EP1120573A2 (en) * | 1999-12-27 | 2001-08-01 | Kayaba Kogyo Kabushiki Kaisha | Hydraulic drive unit with counter balancing valve |
| EP1120573A3 (en) * | 1999-12-27 | 2003-03-19 | Kayaba Kogyo Kabushiki Kaisha | Hydraulic drive unit with counter balancing valve |
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