JPH08312602A - Swing-back prevention device - Google Patents
Swing-back prevention deviceInfo
- Publication number
- JPH08312602A JPH08312602A JP11585095A JP11585095A JPH08312602A JP H08312602 A JPH08312602 A JP H08312602A JP 11585095 A JP11585095 A JP 11585095A JP 11585095 A JP11585095 A JP 11585095A JP H08312602 A JPH08312602 A JP H08312602A
- Authority
- JP
- Japan
- Prior art keywords
- valve
- circuit
- spring
- check valve
- hydraulic motor
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
- Pending
Links
Classifications
-
- E—FIXED CONSTRUCTIONS
- E02—HYDRAULIC ENGINEERING; FOUNDATIONS; SOIL SHIFTING
- E02F—DREDGING; SOIL-SHIFTING
- E02F9/00—Component parts of dredgers or soil-shifting machines, not restricted to one of the kinds covered by groups E02F3/00 - E02F7/00
- E02F9/20—Drives; Control devices
- E02F9/22—Hydraulic or pneumatic drives
- E02F9/2203—Arrangements for controlling the attitude of actuators, e.g. speed, floating function
- E02F9/2207—Arrangements for controlling the attitude of actuators, e.g. speed, floating function for reducing or compensating oscillations
-
- E—FIXED CONSTRUCTIONS
- E02—HYDRAULIC ENGINEERING; FOUNDATIONS; SOIL SHIFTING
- E02F—DREDGING; SOIL-SHIFTING
- E02F9/00—Component parts of dredgers or soil-shifting machines, not restricted to one of the kinds covered by groups E02F3/00 - E02F7/00
- E02F9/08—Superstructures; Supports for superstructures
- E02F9/10—Supports for movable superstructures mounted on travelling or walking gears or on other superstructures
- E02F9/12—Slewing or traversing gears
- E02F9/121—Turntables, i.e. structure rotatable about 360°
- E02F9/128—Braking systems
Landscapes
- Engineering & Computer Science (AREA)
- Mining & Mineral Resources (AREA)
- Civil Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Structural Engineering (AREA)
- Operation Control Of Excavators (AREA)
- Fluid-Pressure Circuits (AREA)
Abstract
Description
【０００１】[0001]
【産業上の利用分野】本発明は、油圧モータがその停止
時に正逆転しながら停止する状態を防止する揺れ戻り防
止装置に関する。BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a swing-back prevention device for preventing a state in which a hydraulic motor stops while rotating forward and backward.
【０００２】[0002]
【従来の技術】従来、油圧ショベル等の旋回体を駆動す
る油圧回路に於いては、図１のようなリリーフ弁ａとチ
ェック弁ｂを組み合わせたブレーキ弁ｃが一般的に使用
されている。該油圧回路に於いては、旋回体を駆動する
油圧モータｄを停止させるとき、その往復の管路ｅ，ｆ
に設けた切換弁ｇを中立位置に戻して管路ｅ，ｆを閉じ
るが、該油圧モータｄは旋回しているためにポンプ作用
をし、リリーフ弁ａが作動してブレーキ圧力が上昇し、
停止する。しかし、旋回停止後、ＡポートとＢポートで
残圧が異なるため、油圧モータｄに揺れ戻り現象が発生
する。例えば、モータｄが矢印方向に旋回している状態
で切換弁ｇを中立位置に戻し、ブレーキをかけると、Ｂ
ポート側の管路ｆに高圧が発生する。その時のＢポート
の圧力ＰBと押込側のＡポートの圧力ＰA は図２のよう
に変動し、モータｄの回転波形は曲線Ｃのように変動す
る。2. Description of the Related Art Conventionally, in a hydraulic circuit for driving a swing body such as a hydraulic excavator, a brake valve c combining a relief valve a and a check valve b as shown in FIG. 1 is generally used. In the hydraulic circuit, when the hydraulic motor d for driving the revolving unit is stopped, the reciprocating pipelines e and f
The switching valve g provided in the above is returned to the neutral position to close the pipelines e and f. However, since the hydraulic motor d is rotating, the hydraulic motor d acts as a pump, the relief valve a operates, and the brake pressure increases.
Stop. However, after the turning is stopped, the residual pressure is different between the A port and the B port, so that the hydraulic motor d will swing back. For example, when the switching valve g is returned to the neutral position while the motor d is turning in the direction of the arrow and the brake is applied, B
High pressure is generated in the conduit f on the port side. The pressure P A of the A port pressure P B and the pushing side of the B port at that time varied as shown in FIG. 2, the rotation waveform of the motor d varies as the curve C.
【０００３】つまり、切換弁ｇを中立位置に戻したと
き、Ｂポート側が圧力ＰB に昇圧する。その後Ｒ点に於
いてリリーフ弁ａがレシートする。レシートする圧力Ｐ
B はまだ高いので、Ｂポート側の管路ｆにはその圧力Ｐ
B が完全にこもってしまう。その後、Ｂポート側の管路
ｆの配管ボリュームによるアキュームレータ効果及び旋
回体系のバックラッシュ等によりＢポート側圧力ＰB は
油圧モータｄを逆転させるエネルギーとなり、該油圧モ
ータｄは矢印と反対方向に回転する。すると前記のブレ
ーキ時と同様に油圧モータｄがポンプ作用し、今度はＰ
A がＰB より高くなる。圧力ＰA が高くなると油圧モー
タｄが再び矢印方向に回転する。以上のように圧力
ＰA 、ＰB が交互に高くなるので、油圧モータｄは数回
の揺れ戻りを繰り返し起しながら停止する。That is, when the switching valve g is returned to the neutral position, the B port side increases the pressure to P B. After that, the relief valve a receives at the point R. Receiving pressure P
Since B is still high, the pressure P in the line f on the B port side
B is completely muffled. After that, the B port side pressure P B becomes energy for reversing the hydraulic motor d due to the accumulator effect due to the piping volume of the B port side pipe f and the backlash of the turning system, and the hydraulic motor d rotates in the direction opposite to the arrow. To do. Then, the hydraulic motor d acts as a pump in the same manner as when braking, and this time P
A becomes higher than P B. When the pressure P A increases, the hydraulic motor d rotates again in the direction of the arrow. As described above, since the pressures P A and P B are alternately increased, the hydraulic motor d is stopped while repeatedly causing swinging back several times.
【０００４】こうした揺れ戻りを防止するために、以前
より多くの手段が提案されており、その手段として、各
管路に揺れ戻り防止弁を設けたものと、各管路を短絡さ
せて揺れ戻り防止弁を設けたものとに大別することが出
来る。前者の手段よりも後者の手段の方が１つの弁に集
約できるので回路構成が簡略化されて製作、組立配管、
保守が容易になる利点がある。[0004] In order to prevent such swingback, many means have been proposed than before, such as providing a swingback prevention valve in each pipeline and swinging back by shorting each pipeline. It can be broadly divided into those provided with a check valve. Since the latter means can be integrated into one valve rather than the former means, the circuit configuration is simplified and the production, assembly piping,
There is an advantage that maintenance is easy.
【０００５】後者の手段の例としては、図３に示すよう
なオンオフ弁ｈを設けたもの（特開昭５７−１８０３号
公報）が公知である。しかし、このようなオンオフ弁を
設けたものは、リリーフ弁の設定圧力によりオンオフ弁
の作動圧力（スプリング力）を変えねばならず、オンオ
フ弁の作動圧力は、リリーフ弁の設定圧力に影響される
ため高圧となり、スプリングの荷重が高くなってそのた
めオンオフ弁の開閉弁のスピード調整が難しいという欠
点がある。[0005] As an example of the latter means, there is known an apparatus provided with an on / off valve h as shown in FIG. 3 (Japanese Patent Laid-Open No. 57-1803). However, in the case where such an on / off valve is provided, the operating pressure (spring force) of the on / off valve must be changed by the set pressure of the relief valve, and the operating pressure of the on / off valve is affected by the set pressure of the relief valve. Therefore, the pressure becomes high and the load of the spring becomes high, which makes it difficult to adjust the speed of the on-off valve.
【０００６】こうした欠点を解決するため、出願人は、
先に、図４に示すような、リリーフ弁ａとチェック弁ｂ
とで構成されたブレーキ弁ｃで油圧モータｄにブレーキ
を与えるようにしたものに於いて、該リリーフ弁ａのタ
ンク戻り回路ｉと該チェック弁ｂの流入回路ｊとの間
に、該タンク戻り回路ｉの流体圧力で開かれるばね負荷
形チェック弁ｋとこれに並行な絞り弁ｌとを設け、該ば
ね負荷形チェック弁の前後の圧力により、油圧モータｄ
の往復の管路ｅ、ｆ間を結んだ短絡回路ｍに設けた閉じ
位置ｎと絞り位置ｏを有すると共に該閉じ位置方向にば
ねｐにより付勢されたスプール形の短絡弁ｑを作動させ
るようにした装置を提案した（実願平５−１５０４
号）。To solve these drawbacks, the applicant has
First, as shown in FIG. 4, a relief valve a and a check valve b
A brake valve c constituted by means of applying a brake to a hydraulic motor d, wherein the tank return circuit i of the relief valve a and the inflow circuit j of the check valve b are A spring-loaded check valve k that is opened by the fluid pressure of the circuit i and a throttle valve l that is parallel to the spring-loaded check valve k are provided, and the hydraulic motor d is driven by the pressure before and after the spring-loaded check valve.
To operate a spool type short circuit valve q which has a closed position n and a throttle position o provided in a short circuit m connecting the reciprocating pipelines e and f, and which is biased by a spring p toward the closed position. I proposed the device which made it
issue).
【０００７】[0007]
【発明が解決しようとする課題】図４に示した装置で
は、絞り弁ｌの調整で短絡弁ｑの移動時間を任意に調整
できるという簡便さがあるが、油圧モータｄの起動時に
も短絡弁ｑが絞り位置ｏに移動して、油圧モータｄへの
供給流量の一部が短絡回路ｍを介して供給側の管路から
戻り側の管路へと流れ込み、油圧モータｄの効率が悪く
なる不都合を伴う。The device shown in FIG. 4 has the convenience that the moving time of the short-circuit valve q can be arbitrarily adjusted by adjusting the throttle valve l, but the short-circuit valve is also activated when the hydraulic motor d is started. q moves to the throttle position o, and a part of the flow rate supplied to the hydraulic motor d flows from the supply side pipe line to the return side pipe line via the short circuit m, and the efficiency of the hydraulic motor d deteriorates. Inconvenient.
【０００８】その原因は、通常はポンプから切換弁ｇへ
の供給回路に回路リリーフ弁ｒが回路保護のために設け
られており、これのリリーフ設定圧力がブレーキ弁ｃの
リリーフ弁ａのリリーフ設定圧力と略等しい程度に設定
されていることが多く、このような場合、油圧モータの
起動時に、両リリーフ弁ａ、ｒが干渉して作動し、短絡
弁ｑが絞り位置ｏに切り換わり、油圧モータｄに供給さ
れる流量の一部が戻りの管路にバイパスされ、油圧モー
タｄへの供給流量が減り、その容積効率が悪くなる。ま
た、チェック弁ｂの前後の差圧を短絡弁ｑに導くパイロ
ットラインｓ、ｔには油の流れが殆どなく、そのため、
気温が低いとパイロットラインｓ、ｔの油の粘度が常に
高いままになり、短絡弁ｑの開閉に要する時間が長引
き、揺れ戻り防止の作動が緩慢になって好ましくない。The cause is that a circuit relief valve r is usually provided in the supply circuit from the pump to the switching valve g for circuit protection, and the relief setting pressure of the circuit relief valve r is the relief setting of the relief valve a of the brake valve c. The pressure is often set to be approximately equal to the pressure. In such a case, when the hydraulic motor is started, both relief valves a and r interfere with each other to operate, and the short-circuit valve q switches to the throttle position o. A part of the flow rate supplied to the motor d is bypassed to the return pipe, the flow rate supplied to the hydraulic motor d is reduced, and the volumetric efficiency thereof is deteriorated. Further, there is almost no oil flow in the pilot lines s and t that guide the differential pressure before and after the check valve b to the short circuit valve q.
When the temperature is low, the viscosity of the oil in the pilot lines s and t always remains high, the time required to open / close the short-circuit valve q is prolonged, and the operation for preventing swing-back is slow, which is not preferable.
【０００９】本発明は、ブレーキ弁を構成するリリーフ
弁のタンク戻り回路にばね負荷形チェック弁と絞り弁を
並行に設け、これの前後の差圧で往復の管路を短絡させ
る閉じ位置と絞り位置を有する短絡弁の作動を制御する
揺れ戻り防止装置を設けたことによる油圧モータの容積
効率の低下を防止することを目的するものである。According to the present invention, a spring-loaded check valve and a throttle valve are provided in parallel in a tank return circuit of a relief valve that constitutes a brake valve, and a closed position and a throttle that short-circuit a reciprocating pipe line due to a differential pressure before and after the check valve. An object of the present invention is to prevent a reduction in volumetric efficiency of a hydraulic motor due to the provision of a swing-back prevention device for controlling the operation of a short circuit valve having a position.
【００１０】[0010]
【課題を解決するための手段】本発明では、切換弁と油
圧モータとを結ぶ往復の管路に、該管路の流体をタンク
へ排出するリリーフ弁と、該管路へタンク戻りの流体の
流入を許容するチェック弁とで構成されたブレーキ弁を
設けて該油圧モータにブレーキを与えるようにし、該リ
リーフ弁のタンク戻り回路と該チェック弁の流入回路と
の間に、該タンク戻り回路からの流体により開かれるば
ね負荷形チェック弁とこれに並行な絞り弁とを設け、該
往復の管路間を結んだ短絡回路に閉じ位置と絞り位置を
有すると共に該閉じ位置方向にばねにより付勢されたス
プール形の短絡弁を設け、該短絡弁のスプールのばね側
室をタンクに接続すると共にその反対側の室を該ばね負
荷形チェック弁の上流側のタンク戻り回路に接続した揺
れ戻り防止装置に於いて、該短絡弁に、該閉じ位置と絞
り位置の他に該ばねを撓めて該絞り位置を越えて移動し
た位置に第２閉じ位置を設けることにより、上記の目的
を達成するようにした。According to the present invention, a reciprocating pipe connecting a switching valve and a hydraulic motor is provided with a relief valve for discharging the fluid in the pipe to a tank, and a fluid returning to the tank in the pipe. A brake valve composed of a check valve that allows inflow is provided to apply a brake to the hydraulic motor, and a brake valve is provided between the tank return circuit of the relief valve and the inflow circuit of the check valve. A spring-loaded check valve that is opened by the fluid and a throttle valve that is parallel to the check valve are provided, and a short circuit that connects between the reciprocating pipes has a closed position and a throttle position and is biased by a spring toward the closed position. Of the spool type short circuit valve, the spring side chamber of the spool of the short circuit valve is connected to the tank, and the chamber on the opposite side is connected to the tank return circuit upstream of the spring loaded check valve. To In addition to the closed position and the throttle position, the short-circuit valve is provided with a second closed position at a position where the spring is bent to move beyond the throttle position, thereby achieving the above object. .
【００１１】[0011]
【作用】油圧モータの通常回転時には、該油圧モータの
押込側・出口側が共に低圧であるためにブレーキ弁のリ
リーフ弁は作動せず、短絡弁は閉じたままになる。切換
弁を中立位置に戻すと、油圧モータが慣性で回転するた
めにポンプ作用を営み、該油圧モータの出口側の圧力が
高まって該リリーフ弁が作動し、該リリーフ弁からタン
クにばね負荷形のチェック弁を介して流体が流れるが、
該短絡弁のばねは該ばね負荷形チェック弁のばねよりも
弱いので、短絡弁が絞り位置を過ぎて第２閉じ位置まで
移動し、出口側管路の圧力は該ばね負荷形チェック弁を
介して排出され、ブレーキが掛かる。油圧モータの停止
直前には、ブレーキ圧力は徐々に低くなるので短絡弁は
絞り位置に戻り、該短絡弁が絞り位置にある間に油圧モ
ータの出口側の昇圧を押込側に流体を循環させることに
より防止し、揺れ戻りが防止される。該ブレーキ弁のリ
リーフ弁は、油圧モータの起動時に供給側の管路に発生
する圧力で開弁することがあるが、このような場合には
比較的大量の流体が該リリーフ弁を流れるので、比較的
大きな差圧がばね負荷形チェック弁の前後に発生し、こ
の差圧によって該短絡弁はこれのばねに抗してストロー
クエンドの第２閉じ位置まで移動する。そのため、短絡
回路は開かず油圧モータの容積効率を低下させることが
ない。During normal rotation of the hydraulic motor, the relief valve of the brake valve does not operate and the short-circuit valve remains closed because both the pushing side and the outlet side of the hydraulic motor are at low pressure. When the directional control valve is returned to the neutral position, the hydraulic motor rotates by inertia, thereby acting as a pump, the pressure on the outlet side of the hydraulic motor increases, and the relief valve operates. Fluid flows through the check valve of
Since the spring of the short-circuit valve is weaker than the spring of the spring-loaded check valve, the short-circuit valve moves past the throttling position to the second closed position, and the pressure in the outlet side pipe line passes through the spring-loaded check valve. Are discharged and the brakes are applied. Immediately before stopping the hydraulic motor, the brake pressure gradually decreases, so the short-circuit valve returns to the throttle position, and while the short-circuit valve is in the throttle position, the pressure increase on the outlet side of the hydraulic motor is circulated to the pushing side. To prevent it from swinging back. The relief valve of the brake valve may open due to the pressure generated in the pipeline on the supply side when the hydraulic motor is started, but in such a case, a relatively large amount of fluid flows through the relief valve, A relatively large differential pressure develops across the spring-loaded check valve, which causes the shunt valve to move against its spring to a second closed position at the end of the stroke. Therefore, the short circuit is not opened and the volumetric efficiency of the hydraulic motor is not reduced.
【００１２】[0012]
【実施例】本発明の実施例を図面に基づき説明すると、
図５に於いて符号１は油圧ポンプ２に切換弁３を介して
接続した管路（又は油路）４、５を流れる流体により駆
動される油圧モータで、該油圧モータ１には油圧ショベ
ルの旋回体等が連結される。該管路４、５の夫々には、
各管路の高圧流体をタンク６に排出するリリーフ弁７、
８と、各管路へタンク６から流体を補充するためのチェ
ック弁９、１０とで構成されたブレーキ弁１１が設けら
れる。１２はリリーフ弁７、８からのタンク戻り回路
で、この回路１２の一部をチェック弁９、１０の流入回
路１３と共用するようにした。Embodiments of the present invention will be described with reference to the drawings.
In FIG. 5, reference numeral 1 denotes a hydraulic motor driven by a fluid flowing in pipes (or oil passages) 4 and 5 connected to a hydraulic pump 2 via a switching valve 3, and the hydraulic motor 1 includes a hydraulic shovel. A revolving body or the like is connected. In each of the conduits 4, 5,
A relief valve 7 for discharging the high-pressure fluid in each pipe to a tank 6;
A brake valve 11 is provided which includes a check valve 9 and a check valve 9 for replenishing each pipe with fluid from the tank 6. Reference numeral 12 is a tank return circuit from the relief valves 7 and 8, and a part of this circuit 12 is shared with the inflow circuit 13 of the check valves 9 and 10.
【００１３】該油圧モータ１の停止時に於ける揺れ戻り
を防止するために、該リリーフ弁７、８のタンク戻り回
路１２と該チェック弁９、１０のタンクからの流入回路
１３との間に、該タンク戻り回路１２からの流体により
開かれるばね負荷形チェック弁１４とこれに並行な絞り
弁１５とを設け、該管路４、５間を結んだ短絡回路１６
に閉じ位置１７と絞り位置１８を有する短絡弁１９が設
けられる。該短絡弁１９は、定常状態では閉じ位置に位
置するように弱いばね２０により押されたスプール形の
短絡弁であり、該短絡弁のスプールの一端が面するばね
側室をパイロットライン２２ａによりタンクに接続する
と共に、該スプールの他端が面する反対側の室を該ばね
負荷形チェック弁１４の上流側のタンク戻り回路１２に
パイロットライン２２ｂにより接続した。該ばね負荷形
チェック弁１４のばね２１の開弁圧力は、短絡弁１９の
ばね２０の開弁圧力よりも高く設定するものとし、該絞
り弁１５を可変絞りに構成して該短絡弁１９が絞り位置
１８から閉じ位置１７に移動する時間の調整を行えるよ
うにした。２４は切換弁３の前方に設けられる回路リリ
ーフ弁で、これの設定圧力はブレーキ弁１１のリリーフ
弁７、８の設定圧力と同等もしくはそれ以上に設定され
る。In order to prevent swinging back when the hydraulic motor 1 is stopped, between the tank return circuit 12 of the relief valves 7 and 8 and the inflow circuit 13 from the tank of the check valves 9 and 10, A spring-loaded check valve 14 opened by the fluid from the tank return circuit 12 and a throttle valve 15 in parallel therewith are provided, and a short circuit 16 connecting the pipe lines 4 and 5 is provided.
A shunt valve 19 having a closed position 17 and a throttle position 18 is provided at the. The short-circuit valve 19 is a spool-type short-circuit valve pushed by a weak spring 20 so as to be located at a closed position in a steady state. A spring side chamber facing one end of the spool of the short-circuit valve is connected to a tank by a pilot line 22a. In addition to the connection, the opposite chamber facing the other end of the spool was connected to the tank return circuit 12 upstream of the spring-loaded check valve 14 by a pilot line 22b. The opening pressure of the spring 21 of the spring-loaded check valve 14 is set to be higher than the opening pressure of the spring 20 of the short-circuit valve 19, and the throttle valve 15 is configured as a variable throttle so that the short-circuit valve 19 The time for moving from the aperture position 18 to the closing position 17 can be adjusted. Reference numeral 24 is a circuit relief valve provided in front of the switching valve 3, and the set pressure thereof is set to be equal to or higher than the set pressure of the relief valves 7 and 8 of the brake valve 11.
【００１４】以上の構成によれば、切換弁３が切換えら
れて油圧ポンプ２の吐出流体が管路４から油圧モータ１
を介して管路５に流れており、該油圧モータ１が旋回体
を駆動している場合、該油圧モータ１の押込側・出口側
が共に低圧であるので、リリーフ弁７、８は作動しな
い。該切換弁３を中立位置に戻し、該油圧モータ１の回
転を停止させた時には、油圧モータ１が慣性によりポン
プ作用を営み、モータ１の出口側の閉鎖された管路５の
圧力が高まり、リリーフ弁８が管路５の圧力を排除すべ
く開き、その圧力はばね負荷形チェック弁１４を介して
タンク６へと排出されると共に、パイロット回路２２ｂ
を介して短絡弁１９を絞り位置１８に切換えるべく作用
する。該管路５に発生するブレーキ圧力により油圧モー
タ１にブレーキが掛かるが、該油圧モータ１の停止直前
には、ブレーキ圧力は図６の曲線Ｄで示すように徐々に
低下し、リリーフ弁８はブレーキ圧力がＲ点にまで低下
したときレシートして閉弁状態になる。このレシートし
たとき出口側の管路５に圧力が残存しているために油圧
モータ１に揺り戻しが発生することになるが、上記の構
成としたことにより、リリーフ弁８がレシートしても短
絡弁１９は絞り弁１５があるためにばね２０に押されて
図６の曲線Ｆのように徐々に開弁状態から閉弁状態に変
化し、この間に油圧モータ１が停止しても該管路５に残
存するブレーキ圧力は該短絡弁１９を介して押込側の管
路４に循環するので、油圧モータ１の停止時に出口側の
昇圧により油圧モータ１が揺れ戻ることなく停止する。
短絡弁１９が絞り位置１８から閉じ位置１７へ移動する
時間は、ばね負荷形チェック弁１４に並行の絞り弁１５
の開度調整により自在に設定できる。According to the above construction, the switching valve 3 is switched so that the fluid discharged from the hydraulic pump 2 is transferred from the pipe 4 to the hydraulic motor 1.
When the hydraulic motor 1 is driving the revolving structure, the relief valves 7 and 8 do not operate because both the pushing side and the outlet side of the hydraulic motor 1 are at low pressure. When the switching valve 3 is returned to the neutral position and the rotation of the hydraulic motor 1 is stopped, the hydraulic motor 1 operates as a pump due to inertia, and the pressure in the closed pipeline 5 on the outlet side of the motor 1 increases. The relief valve 8 opens to eliminate the pressure in the line 5, and the pressure is discharged to the tank 6 via the spring-loaded check valve 14 and the pilot circuit 22b.
Via the switch to actuate the shunt valve 19 to the throttle position 18. The hydraulic motor 1 is braked by the brake pressure generated in the pipe 5, but immediately before the hydraulic motor 1 is stopped, the brake pressure gradually decreases as shown by the curve D in FIG. When the brake pressure drops to point R, a receipt is made and the valve is closed. At the time of this receipt, the hydraulic motor 1 will swing back because the pressure remains in the outlet-side conduit 5, but due to the above configuration, even if the relief valve 8 is receipt, a short circuit occurs. The valve 19 is pushed by the spring 20 due to the presence of the throttle valve 15 and gradually changes from the open state to the closed state as shown by the curve F in FIG. Since the brake pressure remaining in 5 circulates in the conduit 4 on the push-in side through the short-circuit valve 19, the hydraulic motor 1 is stopped without swinging back due to the pressure increase on the outlet side when the hydraulic motor 1 is stopped.
The time required for the short-circuit valve 19 to move from the throttle position 18 to the closing position 17 is the same as the spring-loaded check valve 14 in parallel with the throttle valve 15
It can be set freely by adjusting the opening of.
【００１５】こうした構成・作用は、出願人が先に提案
した装置と特に変わりがないが、本発明では、該短絡弁
１９に、該閉じ位置１７と絞り位置１８の他に該ばね２
０を撓めて該絞り位置１８を越えて移動した位置に第２
閉じ位置２５を設け、ブレーキ弁１１のリリーフ弁７、
８が開いてもばね負荷形チェック弁１４の前後の差圧が
予定の範囲でないときは短絡回路１６の閉鎖し、これに
よりブレーキ弁の作動時に於ける油圧モータ１の容積効
率の低下を防止するようにした。The construction and operation are the same as those of the device previously proposed by the applicant, but in the present invention, the short-circuit valve 19 is provided with the spring 2 in addition to the closed position 17 and the throttle position 18.
0 is bent and the second position is moved beyond the aperture position 18.
The closed position 25 is provided, the relief valve 7 of the brake valve 11,
When the differential pressure before and after the spring-loaded check valve 14 is not within the predetermined range even when 8 is opened, the short circuit 16 is closed, thereby preventing the volumetric efficiency of the hydraulic motor 1 from decreasing when the brake valve is activated. I did it.
【００１６】該短絡弁１９はスプール形弁であるから、
第２閉じ位置２５を設けることにより絞り位置１８は中
間の位置になり、差圧が大きさに応じて閉じ位置１７、
絞り位置１８或は第２閉じ位置２５に切り換わる。切換
弁３を中立位置から切り換えて油圧モータ１を起動した
ときには、油圧モータ１の負荷圧が大きいため、ブレー
キ弁１１のリリーフ弁７又は８が開弁して油圧モータ１
に供給される管路の流量の一部がタンク６へ放出される
ことが多いが、この場合、ばね負荷形チェック弁１４の
前後の差圧が比較的大きくなるので、短絡弁１９はばね
２０に抗して第２閉じ位置２５に切換わり、短絡回路１
６を遮断するため、該リリーフ弁７又は８からタンク６
へ放出される流量以外は油圧モータ１に供給されること
になり、これの容積効率が向上する。油圧モータ１が加
速或は定速回転になると、押込側の管路の圧力が起動時
よりも低くなるので、ブレーキ弁１１のリリーフ弁７又
は８が閉じ、パイロットライン２２ａ、２２ｂは共にタ
ンク圧になり、短絡弁１９はばね２０で閉じ位置１７に
戻され、押込側の管路に供給された流量は油圧モータ１
を循環して出口側管路からタンクへ戻る。油圧モータ１
の停止のために切換弁３を中立位置に戻したときは、油
圧モータ１が慣性で回転するためにポンプ作用を営み、
その出口側の圧力が高まって該リリーフ弁７又は８が作
動し、該リリーフ弁からタンクにばね負荷形チェック弁
１４を介して流体が流れるが、該短絡弁１９のばね２０
は該ばね負荷形チェック弁２１のばねよりも弱いので、
該ばね負荷形チェック弁２１が開く前に短絡弁１９が絞
り位置１８を過ぎて第２閉じ位置２５まで移動し、その
後、出口側管路の圧力は該ばね負荷形チェック弁を介し
て排出され、該出口側管路の圧力のためにブレーキが掛
かる。油圧モータ１の停止直前には、ブレーキ圧力は徐
々に低くなり、その圧力が設定圧力になったところで短
絡弁１９は絞り位置１８に戻り、この位置にある間に油
圧モータの出口側の昇圧を押込側に流体を循環させるこ
とにより防止し、揺れ戻りが防止される。Since the short-circuit valve 19 is a spool type valve,
By providing the second closed position 25, the throttle position 18 becomes an intermediate position, and the closed position 17, depending on the magnitude of the differential pressure,
It switches to the diaphragm position 18 or the second closing position 25. When the switching valve 3 is switched from the neutral position and the hydraulic motor 1 is started, since the load pressure of the hydraulic motor 1 is large, the relief valve 7 or 8 of the brake valve 11 is opened to open the hydraulic motor 1.
Often, a part of the flow rate of the pipeline supplied to the tank 6 is discharged to the tank 6, but in this case, the differential pressure before and after the spring-loaded check valve 14 becomes relatively large, so that the short circuit valve 19 causes the spring 20 To the second closed position 25 against the short circuit 1
6 to shut off the relief valve 7 or 8 from the tank 6
Other than the flow rate discharged to the hydraulic motor 1, the hydraulic motor 1 is supplied, and the volumetric efficiency of the hydraulic motor 1 is improved. When the hydraulic motor 1 accelerates or rotates at a constant speed, the pressure in the line on the pushing side becomes lower than that at the time of startup, so that the relief valve 7 or 8 of the brake valve 11 is closed and the pilot lines 22a and 22b are both at tank pressure. Then, the short-circuit valve 19 is returned to the closed position 17 by the spring 20, and the flow rate supplied to the pushing-side pipe is the hydraulic motor 1.
And returns to the tank from the outlet line. Hydraulic motor 1
When the switching valve 3 is returned to the neutral position for the stop of the hydraulic motor 1, the hydraulic motor 1 rotates by inertia, so that the pump function is performed.
The pressure on the outlet side increases and the relief valve 7 or 8 operates, and the fluid flows from the relief valve to the tank through the spring-loaded check valve 14, but the spring 20 of the short-circuit valve 19 is used.
Is weaker than the spring of the spring-loaded check valve 21,
Before the spring-loaded check valve 21 opens, the shunt valve 19 moves past the throttle position 18 to the second closed position 25, after which the outlet line pressure is drained via the spring-loaded check valve. , The brake is applied due to the pressure in the outlet line. Immediately before the hydraulic motor 1 is stopped, the brake pressure gradually decreases, and when the pressure reaches the set pressure, the short circuit valve 19 returns to the throttle position 18, and the pressure on the outlet side of the hydraulic motor is increased while it is in this position. It is prevented by circulating the fluid to the pushing side, and swing back is prevented.
【００１７】該パイロットライン２２ａに、図７に示す
ように、第２チェック弁２９とこれに並行な可変の第２
絞り弁３０とを介在させれば、短絡弁１９は第２チェッ
ク弁２９のために閉じ位置１７から第２閉じ位置２５の
方向へは迅速に作動するが、その逆方向へは第２絞り弁
３０を調節してその戻り作動時間を調節することがで
き、絞り位置１８にある時間を長引かせて揺れ戻り防止
の能力を向上させることができる。尚、図７の例では、
該短絡弁１９のスプールのばね側室と反対側の室を絞り
弁２６及び絞り位置１８の通路２７を介して接続回路２
８により連通させ、該短絡弁１９が絞り位置１８に位置
したとき、リリーフ弁７、８を通過した油温の上昇した
油が両室を流れるようにした。In the pilot line 22a, as shown in FIG. 7, a second check valve 29 and a variable second parallel to the second check valve 29 are provided.
With the interposition of the throttle valve 30, the short-circuit valve 19 operates quickly in the direction from the closed position 17 to the second closed position 25 because of the second check valve 29, but in the opposite direction, the second throttle valve 19 operates. The return operation time can be adjusted by adjusting 30, and the time in the throttle position 18 can be prolonged to improve the ability to prevent rocking return. In addition, in the example of FIG.
The connection circuit 2 connects the chamber on the side opposite to the spring side chamber of the spool of the short circuit valve 19 with the throttle valve 26 and the passage 27 at the throttle position 18.
When the short-circuit valve 19 is located at the throttle position 18, the oil having the increased oil temperature passing through the relief valves 7 and 8 is allowed to flow through both chambers.
【００１８】[0018]
【発明の効果】以上のように本発明によるときは、ブレ
ーキ弁のリリーフ弁のタンク戻り回路とチェック弁の流
入回路の間に、ばね負荷形チェック弁とこれに並行な絞
り弁とを設け、これの前後の圧力を短絡回路のばねで押
されたスプール形の短絡弁に導く形式の揺れ戻り防止装
置に於いて、該短絡弁に、該閉じ位置と絞り位置の他に
該ばねを撓めて該絞り位置を越えて移動した位置に第２
閉じ位置を設けたので、起動時に該短絡回路を介して短
絡する不都合が解消され、油圧モータの容積効率が向上
する効果が得られ、該短絡弁と該ばね負荷形チェック弁
の上流側を結ぶパイロットラインに第２チェック弁とこ
れに平行な第２絞り弁を設けたので、該短絡弁が絞り位
置で作動する時間を調節できて使用上便利になる等の効
果がある。As described above, according to the present invention, a spring-loaded check valve and a throttle valve parallel thereto are provided between the tank return circuit of the relief valve of the brake valve and the inflow circuit of the check valve, In a swing-back prevention device of the type in which the pressure before and after this is guided to a spool type short circuit valve that is pressed by a spring of a short circuit, in the short circuit valve, the spring is bent in addition to the closed position and the throttle position. The second position at a position that has moved beyond the diaphragm position.
Since the closed position is provided, the inconvenience of short-circuiting via the short-circuit circuit at the time of start-up is solved, the effect of improving the volumetric efficiency of the hydraulic motor is obtained, and the short-circuit valve and the upstream side of the spring-loaded check valve are connected. Since the pilot line is provided with the second check valve and the second throttle valve parallel thereto, it is possible to adjust the time during which the short-circuit valve operates at the throttle position, which is convenient in use.
【図１】従来例の線図FIG. 1 Diagram of conventional example
【図２】図１の場合の油圧モータの揺れ戻りの原因の説
明図FIG. 2 is an explanatory diagram of a cause of swinging back of the hydraulic motor in the case of FIG.
【図３】従来の揺れ戻り防止装置の１例の線図FIG. 3 is a diagram of an example of a conventional swing-back prevention device.
【図４】先に提案した揺れ戻り防止装置の線図FIG. 4 is a diagram of the previously proposed swing-back prevention device.
【図５】本発明の実施例の線図FIG. 5 is a diagram of an embodiment of the present invention.
【図６】図５の揺れ戻り防止の説明図FIG. 6 is an explanatory view of the swing-back prevention of FIG.
【図７】請求項２に記載の発明の実施例の線図FIG. 7 is a diagram of an embodiment of the invention described in claim 2;
１ 油圧モータ ２ 油圧ポンプ ３
切換弁 ４、５ 作動回路 ６ タンク ７、
８ リリーフ弁 ９、１０ チェック弁 １１ ブレーキ弁 １２
タンク戻り回路 １３ 流入回路 １４ ばね負荷形チェック弁
１５ 絞り弁 １６ 短絡回路 １７ 閉じ位置 １８
絞り位置 １９ 短絡弁 ２０ ばね ２５
第２閉じ位置 ２９ 第２チェック弁 ３０ 第２絞り弁1 Hydraulic motor 2 Hydraulic pump 3
Switching valve 4, 5 Operating circuit 6 Tank 7,
8 Relief valve 9, 10 Check valve 11 Brake valve 12
Tank return circuit 13 Inflow circuit 14 Spring-loaded check valve 15 Throttle valve 16 Short circuit 17 Closed position 18
Throttle position 19 Short-circuit valve 20 Spring 25
Second closed position 29 Second check valve 30 Second throttle valve
Claims (2)
に、該管路の流体をタンクへ排出するリリーフ弁と、該
管路へタンク戻りの流体の流入を許容するチェック弁と
で構成されたブレーキ弁を設けて該油圧モータにブレー
キを与えるようにし、該リリーフ弁のタンク戻り回路と
該チェック弁の流入回路との間に、該タンク戻り回路か
らの流体により開かれるばね負荷形チェック弁とこれに
並行な絞り弁とを設け、該往復の管路間を結んだ短絡回
路に閉じ位置と絞り位置を有すると共に該閉じ位置方向
にばねにより付勢されたスプール形の短絡弁を設け、該
短絡弁のスプールのばね側室をタンクに接続すると共に
その反対側の室を該ばね負荷形チェック弁の上流側のタ
ンク戻り回路に接続した揺れ戻り防止装置に於いて、該
短絡弁に、該閉じ位置と絞り位置の他に該ばねを撓めて
該絞り位置を越えて移動した位置に第２閉じ位置を設け
たことを特徴とする揺れ戻り防止装置。1. A reciprocating pipe connecting a switching valve and a hydraulic motor is provided with a relief valve for discharging the fluid in the pipe to a tank, and a check valve for allowing the fluid returning from the tank to the pipe. A spring-loaded type that is provided with a configured brake valve to apply a brake to the hydraulic motor and is opened by a fluid from the tank return circuit between the tank return circuit of the relief valve and the inflow circuit of the check valve. A check valve and a throttle valve parallel to the check valve are provided, and a spool type short circuit valve having a closed position and a throttle position in a short circuit connecting the reciprocating pipelines and being biased by a spring in the direction of the closed position is provided. In the swing-back prevention device, wherein the spring side chamber of the spool of the short-circuit valve is connected to the tank and the chamber on the opposite side is connected to the tank return circuit upstream of the spring-loaded check valve, , The closed position Swing anti-return device, characterized in that a second closed position to a position moved beyond the narrowed position flexing the spring in addition to the throttle position.
の室を上記ばね負荷形チェック弁の上流側のタンク戻り
回路へ接続するパイロットラインに、該反対側の室への
流体の流れを許容する第２チェック弁とこれに並行な絞
り弁を介在させたことを特徴とする請求項１に記載の揺
れ戻り防止弁。2. A pilot line connecting a chamber of the spool of the shunt valve on the side opposite to the spring side chamber to a tank return circuit on the upstream side of the spring-loaded check valve is provided with a fluid flow to the chamber on the opposite side. 2. The swing-back prevention valve according to claim 1, further comprising a second check valve that is allowed and a throttle valve that is parallel to the second check valve.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP11585095A JPH08312602A (en) | 1995-05-15 | 1995-05-15 | Swing-back prevention device |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP11585095A JPH08312602A (en) | 1995-05-15 | 1995-05-15 | Swing-back prevention device |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| JPH08312602A true JPH08312602A (en) | 1996-11-26 |
Family
ID=14672691
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP11585095A Pending JPH08312602A (en) | 1995-05-15 | 1995-05-15 | Swing-back prevention device |
Country Status (1)
| Country | Link |
|---|---|
| JP (1) | JPH08312602A (en) |
Cited By (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| EP1188867A2 (en) | 2000-09-14 | 2002-03-20 | NEW HOLLAND ITALIA S.p.A. | Hydraulic system and method for regulating pressure equalization to suppress oscillation in heavy equipment. |
| WO2005052268A1 (en) * | 2003-11-27 | 2005-06-09 | Bosch Rexroth Ag | Hydraulic control system |
| ITUD20120182A1 (en) * | 2012-10-29 | 2014-04-30 | Pmp Pro Mec S P A | "SHUTTLE VALVE FOR VEHICLE MOTOR CONTROL CIRCUIT" |
| CN110409549A (en) * | 2019-06-28 | 2019-11-05 | 三一重机有限公司 | A kind of anti-rock hydraulic system, revolution executive device and excavator |
| CN112555205A (en) * | 2020-12-14 | 2021-03-26 | 北京三一智造科技有限公司 | Rotary hydraulic system and engineering machinery |
-
1995
- 1995-05-15 JP JP11585095A patent/JPH08312602A/en active Pending
Cited By (11)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| EP1188867A2 (en) | 2000-09-14 | 2002-03-20 | NEW HOLLAND ITALIA S.p.A. | Hydraulic system and method for regulating pressure equalization to suppress oscillation in heavy equipment. |
| JP2002147403A (en) * | 2000-09-14 | 2002-05-22 | Case Corp | Hydraulic system and method controlling pressure equalization for suppressing vibration in heavy cargo transporter |
| EP1188867A3 (en) * | 2000-09-14 | 2002-05-29 | NEW HOLLAND ITALIA S.p.A. | Hydraulic system and method for regulating pressure equalization to suppress oscillation in heavy equipment. |
| WO2005052268A1 (en) * | 2003-11-27 | 2005-06-09 | Bosch Rexroth Ag | Hydraulic control system |
| US7454906B2 (en) | 2003-11-27 | 2008-11-25 | Bosch Rexroth Ag | Hydraulic control system |
| ITUD20120182A1 (en) * | 2012-10-29 | 2014-04-30 | Pmp Pro Mec S P A | "SHUTTLE VALVE FOR VEHICLE MOTOR CONTROL CIRCUIT" |
| WO2014067640A1 (en) * | 2012-10-29 | 2014-05-08 | Pmp Pro-Mec S.P.A. | Valve with a spool for the control circuit of the motor of a vehicle |
| CN104769289A (en) * | 2012-10-29 | 2015-07-08 | Pmppro-Mec股份公司 | Valve with a spool for the control circuit of the motor of a vehicle |
| CN110409549A (en) * | 2019-06-28 | 2019-11-05 | 三一重机有限公司 | A kind of anti-rock hydraulic system, revolution executive device and excavator |
| CN112555205A (en) * | 2020-12-14 | 2021-03-26 | 北京三一智造科技有限公司 | Rotary hydraulic system and engineering machinery |
| CN112555205B (en) * | 2020-12-14 | 2023-09-12 | 北京三一智造科技有限公司 | Rotary hydraulic system and engineering machinery |
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