JP2577676Y2 - Pressure oil supply device - Google Patents
Pressure oil supply deviceInfo
- Publication number
- JP2577676Y2 JP2577676Y2 JP1992049503U JP4950392U JP2577676Y2 JP 2577676 Y2 JP2577676 Y2 JP 2577676Y2 JP 1992049503 U JP1992049503 U JP 1992049503U JP 4950392 U JP4950392 U JP 4950392U JP 2577676 Y2 JP2577676 Y2 JP 2577676Y2
- Authority
- JP
- Japan
- Prior art keywords
- pressure
- port
- check valve
- valve
- hole
- 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.)
- Expired - Lifetime
Links
Description
【０００１】[0001]
【産業上の利用分野】本考案は、１つの油圧ポンプの吐
出圧油を複数のアクチュエータに供給する圧油供給装置
に関する。BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a pressure oil supply device for supplying pressure oil discharged from one hydraulic pump to a plurality of actuators.
【０００２】[0002]
【従来の技術】特開昭６０−１１７０６号公報に示す圧
油供給装置が知られている。すなわち、図１に示すよう
に油圧ポンプ１の吐出導管２に複数の圧力補償弁３，１
３を並列に接続し、各圧力補償弁３，１３の出口導管
４，１４に方向制御弁５，１５をそれぞれ設けこの各方
向制御弁５，１５の出力側をアクチュエータ６，１６に
それぞれ接続し、前記圧力補償弁３，１３をポンプ吐出
圧と方向制御弁出口圧で開き方向に押され、方向制御弁
入口圧と最も高い負荷圧で閉じ方向に押される構造とし
た圧油供給装置である。この圧油供給装置であれば、複
数の方向制御弁３，１３を同時操作した時に各アクチュ
エータにポンプ吐出圧油を所定の分配比で供給できる。2. Description of the Related Art A pressure oil supply device disclosed in Japanese Patent Application Laid-Open No. Sho 60-11706 is known. That is, as shown in FIG. 1, a plurality of pressure compensating valves 3 and 1 are connected to the discharge conduit 2 of the hydraulic pump 1.
3 are connected in parallel, and directional control valves 5 and 15 are provided at outlet pipes 4 and 14 of the pressure compensating valves 3 and 13, respectively, and the output sides of the directional control valves 5 and 15 are connected to actuators 6 and 16, respectively. The pressure oil supply device has a structure in which the pressure compensating valves 3 and 13 are pushed in the opening direction by the pump discharge pressure and the direction control valve outlet pressure, and are pushed in the closing direction by the direction control valve inlet pressure and the highest load pressure. . With this pressure oil supply device, the pump discharge pressure oil can be supplied to each actuator at a predetermined distribution ratio when a plurality of directional control valves 3 and 13 are simultaneously operated.
【０００３】かかる圧油供給装置であるとアクチュエー
タの負荷圧を比較して高い方の負荷圧を圧力補償弁に供
給するためにシャトル弁７が必ず必要であり、しかもこ
のシャトル弁７はアクチュエータの数より１つ少ない数
だけ必要であり、それだけコストが高くなる。また、前
述の図１に示す圧油供給装置であると２つのアクチュエ
ータ６，１２をともに作動させ、それらの負荷圧のう
ち、アクチュエータ６側の負荷圧が大きいとする。この
ときは、導管８内の圧力が最高負荷圧としてシャトル弁
７によって導管９に導かれる。次に、負荷圧が変動し
て、アクチュエータ１６側の負荷圧の方がアクチュエー
タ６側の負荷圧より大きくなったとする。その際、すな
わちシャトル弁７が切換わる際、シャトル弁７内の吹き
ぬけにより導管１８内の圧力がぬけ、他方の導管８内の
圧力が押しこめられる。そのため、シャトル弁７の切換
え時、過渡的にアクチュエータ６は自然降下しアクチュ
エータ６は加速される。そこで、本出願人は先に前述の
課題を解決できるようにした圧油供給装置を出願した。In such a pressurized oil supply device, a shuttle valve 7 is required to supply a higher load pressure to the pressure compensating valve by comparing the load pressure of the actuator. One less than the number is needed, which increases the cost. Further, in the case of the pressure oil supply device shown in FIG. 1 described above, it is assumed that the two actuators 6 and 12 are operated together, and the load pressure on the actuator 6 side is larger than the load pressure. At this time, the pressure in the conduit 8 is guided to the conduit 9 by the shuttle valve 7 as the maximum load pressure. Next, it is assumed that the load pressure fluctuates and the load pressure on the actuator 16 side becomes larger than the load pressure on the actuator 6 side. At that time, that is, when the shuttle valve 7 is switched, the pressure in the conduit 18 is released by the blowout in the shuttle valve 7 and the pressure in the other conduit 8 is suppressed. Therefore, when the shuttle valve 7 is switched, the actuator 6 transiently descends spontaneously and the actuator 6 is accelerated. Therefore, the present applicant has previously filed an application for a pressure oil supply device capable of solving the above-mentioned problem.
【０００４】かかる圧油供給装置は図２に示すように、
油圧ポンプ２０の吐出路２１に複数の方向制御弁２２を
設け、この各方向制御弁２２の入口側にチェック弁部２
３と減圧弁部２４より成る圧力補償弁２５をそれぞれ設
けたものであり、この方向制御弁２２と圧力補償弁２５
は図３に示すように構成してある。[0004] Such a pressure oil supply device is, as shown in FIG.
A plurality of directional control valves 22 are provided in a discharge path 21 of the hydraulic pump 20, and a check valve unit 2 is provided at an inlet side of each of the directional control valves 22.
3 and a pressure compensating valve 25 comprising a pressure reducing valve section 24. The directional control valve 22 and the pressure compensating valve 25
Are configured as shown in FIG.
【０００５】すなわち、図３に示すように、弁ブロック
３０は略直方体形状となり、この弁ブロック３０の上部
寄りにスプール孔３１が左右側面３２，３３に開口して
形成され、このスプール３１に開口した第１・第２アク
チュエータポート３４，３５が上面３６に開口して形成
してあり、弁ブロック３０の下部寄りには左側面３２に
開口したチェック弁用孔３７と右側面３３に開口した減
圧弁用孔３８が同心状に形成され、前記チェック弁用孔
３７に開口したポンプポート３９が前後面に開口して形
成され、前記減圧弁用孔３８に開口した第１、第２ポー
ト４２，４３が前後面に開口して形成してあり、複数の
弁ブロック３０の前後面を突き合せて連結すると各ポン
プ・第１・第２ポート３９，４２，４３が連通するよう
にしてある。That is, as shown in FIG. 3, the valve block 30 has a substantially rectangular parallelepiped shape, and a spool hole 31 is formed near the upper portion of the valve block 30 so as to open on the left and right side surfaces 32 and 33. First and second actuator ports 34 and 35 are formed in the upper surface 36 so as to be opened. Near the lower portion of the valve block 30, a check valve hole 37 opened in the left side 32 and a decompression opening opened in the right side 33. A valve hole 38 is formed concentrically, a pump port 39 opened in the check valve hole 37 is formed in the front and rear faces, and first and second ports 42 opened in the pressure reducing valve hole 38 are formed. A plurality of pump / first / second ports 39, 42, and 43 communicate with each other when the front and rear surfaces of the plurality of valve blocks 30 are connected by abutting each other.
【０００６】前記弁ブロック３０にはスプール孔３１に
開口した入力ポート４４、第１・第２負荷圧検出ポート
４５，４６、前記第１・第２アクチュエータポート３
４，３５、第１、第２タンクポート４７，４８が形成さ
れ、そのスプール孔３１に嵌挿した主スプール４９には
第１・第２小径部５０，５１と連通用溝５２が形成して
あり、主スプール４９には第１・第２負荷圧検出ポート
４５，４６を常時連通する第１油路５３及び第２負荷圧
検出ポート４６と第２タンクポート４８を連通・遮断す
る第２油路５４が形成され、スプール４９はスプリング
で各ポートを遮断し、第２油路５４で第２負荷圧検出ポ
ート４６と第２タンクポート４８を連通する中立位置に
保持され、スプール４９を右方に摺動すると第２小径部
５１で第２アクチュエータポート３５を第２タンクポー
ト４８に連通し、連通用溝５２で入力ポート４４が第２
負荷圧検出ポート４６に連通し、第１小径部５０で第１
アクチュエータポート３４が第１負荷圧検出ポート４５
に連通し、かつ第２負荷圧検出ポート４６と第２タンク
ポート４８が遮断する第１圧油供給位置となり、スプー
ル４９を左方に摺動すると第１小径部５０で第１アクチ
ュエータポート３４を第１タンクポート４７に連通し、
連通用溝５２で入力ポート４４が第１負荷圧検出ポート
４５に連通し、第２小径部５１で第２アクチュエータポ
ート３５が第２負荷圧検出ポート４６に連通し、かつ第
２負荷圧検出ポート４６と第２タンクポート４８が遮断
する第２圧油供給位置となって方向制御弁２２を構成し
ている。The valve block 30 has an input port 44 opened to the spool hole 31, first and second load pressure detection ports 45 and 46, and the first and second actuator ports 3.
4 and 35, first and second tank ports 47 and 48 are formed, and first and second small diameter portions 50 and 51 and a communication groove 52 are formed in a main spool 49 inserted into the spool hole 31. The main spool 49 has a first oil passage 53 which always connects the first and second load pressure detection ports 45 and 46 and a second oil which connects and shuts off the second load pressure detection port 46 and the second tank port 48. A passage 54 is formed, the spool 49 blocks each port with a spring, and is held at a neutral position where the second load pressure detection port 46 and the second tank port 48 communicate with each other by the second oil passage 54, and the spool 49 is moved rightward. , The second actuator port 35 communicates with the second tank port 48 through the second small diameter portion 51, and the input port 44 communicates with the second port 52 through the communication groove 52.
The first small diameter portion 50 communicates with the load pressure detection port 46 and
The actuator port 34 is the first load pressure detection port 45
When the spool 49 slides leftward, the first actuator port 34 is connected to the first actuator port 34 by sliding the spool 49 to the left. Communicates with the first tank port 47,
The input port 44 communicates with the first load pressure detection port 45 through the communication groove 52, the second actuator port 35 communicates with the second load pressure detection port 46 through the second small diameter portion 51, and the second load pressure detection port The direction control valve 22 is configured as a second pressure oil supply position where the 46 and the second tank port 48 are shut off.
【０００７】前記チェック弁用孔３７は油路５６で入力
ポート４４に開口し、そのチェック弁用孔３７には前記
ポンプポート３９と入力ポート４４を連通遮断する弁６
０が嵌挿され、その弁６０はプラグ６１に設けたストッ
パ杆６２で図示位置より左方に摺動しないように規制さ
れて遮断位置に保持されてチェック弁部２３を構成して
いる。前記減圧弁用孔３８は第３ポート５７と油路５８
で第２負荷圧検出ポート４６に連通し、この減圧弁用孔
３８にはスプール６４が嵌挿されて第１圧力室６５と第
２圧力室６６を形成し、第１圧力室６５は第３ポート５
７に連通し、第２圧力室６６は第２ポート４３に連通
し、前記スプール６４の盲穴６７に挿入したフリーピス
トン６８と盲穴６７底部との間にばね６９が設けられて
フリーピストン６８はプラグ７０に当接し、かつスプー
ル６４に一体的に設けた押杆７１が透孔７２より突出し
て前記弁６０をストッパ杆６２に当接しており、前記ス
プール６４には第１ポート４２を盲穴６７に連通する細
孔７３が形成されて減圧弁部２４を構成し、この減圧弁
部２４と前記チェック弁部２３とで圧力補償弁２５を構
成している。The check valve hole 37 opens in the oil passage 56 to the input port 44, and the check valve hole 37 opens and closes the pump port 39 and the input port 44.
The valve 60 is inserted into the valve 60, and the valve 60 is regulated by a stopper rod 62 provided on the plug 61 so as not to slide to the left from the position shown in the figure, and is held at the shut-off position to constitute the check valve portion 23. The pressure reducing valve hole 38 is provided between the third port 57 and the oil passage 58.
The second pressure detection port 46 communicates with the second pressure detection port 46, and a spool 64 is inserted into the pressure reducing valve hole 38 to form a first pressure chamber 65 and a second pressure chamber 66. Port 5
7, the second pressure chamber 66 communicates with the second port 43, and a spring 69 is provided between the free piston 68 inserted into the blind hole 67 of the spool 64 and the bottom of the blind hole 67, and the free piston 68 is provided. A push rod 71 integrally provided on a spool 64 projects from a through hole 72 to abut the valve 60 on a stopper rod 62, and the spool 64 has a first port 42 blind. A small hole 73 communicating with the hole 67 is formed to constitute the pressure reducing valve portion 24, and the pressure reducing valve portion 24 and the check valve portion 23 constitute a pressure compensating valve 25.
【０００８】そして、図２に示すように油圧ポンプ２０
の吐出路２１をポンプポート３９、第１ポート４２に連
通し、第２ポート４３に負荷圧検出路８２を接続し、第
１・第２アクチュエータポート３４，３５にアクチュエ
ータ８８が接続してある。図２において、８３は油圧ポ
ンプ８０の吐出流量を制御する斜板、８４はサーボシリ
ンダ、８５はポンプ調整用方向制御弁である。[0008] Then, as shown in FIG.
Is connected to the pump port 39 and the first port 42, the second port 43 is connected to the load pressure detecting path 82, and the first and second actuator ports 34 and 35 are connected to the actuator 88. In FIG. 2, reference numeral 83 denotes a swash plate for controlling the discharge flow rate of the hydraulic pump 80, reference numeral 84 denotes a servo cylinder, and reference numeral 85 denotes a pump adjusting direction control valve.
【０００９】次に作動を図２に基づいて説明する。 方向制御弁２２が中立位置Ａのとき。油圧ポンプ２０
によってタンク８６から吸上げられた油は、吐出路２１
を通ってチェック弁部２３の開く方向の圧力室ａに案内
される。この時、減圧弁部２４の圧力室６５，６６は、
ともにタンク８６に通じているので、この圧力室６５，
６６の圧力はともにゼロで、よって減圧弁部２４は、弱
いばね６９によって押され杆体７１がチェック弁部２３
に当接しているだけである。一方、ポンプ吐出圧は、ポ
ンプ調整用方向制御弁８５のばね８７によって負荷圧検
出路８２の圧力との差圧がある一定に保たれる。いま、
この差圧を２０ｋｇ／ｃｍ2 とすると負荷圧検出路８２
の圧力はゼロなので、ポンプ吐出圧は２０ｋｇ／ｃｍ2
まで上昇し、同時にチェック弁部２３の圧力室ａにポン
プ吐出圧が流入して方向制御弁２２の入口圧（チェック
弁部６３の出口圧）がポンプ吐出圧と等しくなるまでス
トロークし、等しくなれば、弱いばね６９によってレシ
ートする。減圧弁部２４は、ストロークエンド時のみ、
ポンプ吐出路８１と圧力室６６を連通させる一方、チェ
ック弁部２３は、ストロークエンドに達する前に、ポン
プ吐出路８１と出口側を連通させるので、方向制御弁２
２が中立位置Ａのときは、ポンプ吐出路２１と圧力室６
６が連通することはなく、圧力室６５の圧力はゼロのま
まである。Next, the operation will be described with reference to FIG. When the direction control valve 22 is in the neutral position A. Hydraulic pump 20
The oil sucked up from the tank 86 by the
Through the pressure chamber a in the opening direction of the check valve portion 23. At this time, the pressure chambers 65 and 66 of the pressure reducing valve section 24 are
Since both are connected to the tank 86, the pressure chamber 65,
The pressure at 66 is zero, so the pressure reducing valve portion 24 is pushed by the weak spring 69 and the rod 71 is moved to the check valve portion 23.
It just touches the On the other hand, the pump discharge pressure is maintained at a constant pressure difference from the pressure in the load pressure detection path 82 by the spring 87 of the pump adjustment direction control valve 85. Now
Assuming that the differential pressure is 20 kg / cm 2 , the load pressure detection path 82
Pump pressure is 20 kg / cm 2
And at the same time, strokes until the pump discharge pressure flows into the pressure chamber a of the check valve portion 23 and the inlet pressure of the direction control valve 22 (the outlet pressure of the check valve portion 63) becomes equal to the pump discharge pressure. In this case, the receipt is made by a weak spring 69. The pressure reducing valve section 24 is provided only at the end of the stroke.
While the pump discharge passage 81 communicates with the pressure chamber 66, the check valve portion 23 communicates the pump discharge passage 81 with the outlet before reaching the stroke end.
2 is in the neutral position A, the pump discharge passage 21 and the pressure chamber 6
6 does not communicate and the pressure in the pressure chamber 65 remains zero.
【００１０】方向制御弁２２のいずれか一方のみ第１
圧油供給位置Ｂにストロークさせるとき。いま、左側の
方向制御弁２２を第１圧油供給位置Ｂにストロークさ
せ、右側の方向制御弁２２は、中立位置Ａとする。方向
制御弁２２をストロークさせ入力ポート４４と第１アク
チュエータポート３４を接続させ、同時に、第２アクチ
ュエータ３５と第２タンクポート４８を接続させる。こ
の時第１アクチュエータポート３４とアクチュエータ８
８を接続する導管８９内の圧力（負荷圧）がポンプ吐出
圧（２０ｋｇ／ｃｍ2 ）より大きいときはチェック弁部
２３が圧力室ｂの圧力でレシートするため、アクチュエ
ータ８８の自然降下を防止することができる。アクチュ
エータ８８の導管８９の圧力、すなわち負荷圧が第１油
路５３、通路５８より減圧弁部２４の一方の圧力室６５
に導かれる。他方の圧力室６６の圧力はゼロであるた
め、減圧弁部２４は、チェック弁部２３から解離する方
向にストロークエンドまでストロークし、減圧弁部２４
の絞りを介して、ポンプ吐出路２１と負荷圧検出路８２
が連通する。前記導管８９内の圧力（負荷圧）がポンプ
吐出圧（＝２０ｋｇ／ｃｍ2 ）より大きいときは、チェ
ック弁部２３の圧力室ｂの圧力で閉じ、その圧力が、減
圧弁部２４の一方の圧力室６５に導かれるため、他方の
圧力室６６とポンプ吐出路２１が連通しても、減圧弁部
２４はストロークしたままである。一方、導管４１内の
圧力（負荷圧）がポンプ吐出圧（＝２０ｋｇ／ｃｍ2 ）
より小さいときは、その負荷圧が減圧弁部２４の一方の
圧力室６５に導かれ、減圧弁部２４が一方の圧力室６５
の圧力でストロークするが、他方の圧力室６６の圧力が
一方の圧力室６５の圧力（すなわち負荷圧）まで上昇す
ると、弱いばね６９によって閉じチェック弁部２３に当
接する。いずれの場合でも、減圧弁部２４は、一方の圧
力室６５内の圧力と他方の圧力室６６内の圧力が等しく
なるまで、ポンプ吐出路２１と圧力室６６を連通させ、
両圧力室６５，６６内の圧力が等しくなれば弱いばね６
９によって閉じチェック弁部２３に当接する。結果とし
て負荷圧検出路８２内の圧力は、負荷圧と等しくなり、
ポンプ吐出圧は、ポンプ調整用方向制御弁８５によっ
て、ある差圧（ここでは２０ｋｇ／ｃｍ2 ）分だけ、負
荷圧検出路８２内の圧力より高い圧力に制御される。こ
のポンプ吐出圧は、チェック弁部２３を介して、入力ポ
ート４４に導かれているので、すなわち、方向制御弁２
２の入口圧と出口圧（＝負荷圧）の間には、差圧（＝２
０ｋｇ／ｃｍ2 ）が保たれることになる。よって、方向
制御弁２２のストロークに伴なう入口側と出口側の間の
絞りの開口面積の変化によってのみ、アクチュエータ８
８へ供給される流量が制御される。方向制御弁２２をス
トロークさせる際、アクチュエータ８８の導管８９ある
いは９０と負荷圧導入用の第２油路５３が接続され、一
方、第２油路５３は、減圧弁部２４の一方の圧力室６５
と接続されているが、減圧弁部２４において負荷圧は、
パイロット圧力（減圧弁部のセット圧力）としてのみ使
われるので、その圧力がぬけることはなく、すなわち、
方向制御弁２２をストロークさせた際、負荷圧がぬける
ことによるアクチュエータ８８の自然降下はない。Only one of the directional control valves 22 is the first
When making a stroke to the pressure oil supply position B. Now, the left directional control valve 22 is stroked to the first pressure oil supply position B, and the right directional control valve 22 is set to the neutral position A. The directional control valve 22 is stroked to connect the input port 44 and the first actuator port 34, and at the same time, connect the second actuator 35 and the second tank port 48. At this time, the first actuator port 34 and the actuator 8
When the pressure (load pressure) in the conduit 89 connecting the pipe 8 is higher than the pump discharge pressure (20 kg / cm 2 ), the check valve section 23 receipts with the pressure in the pressure chamber b, thereby preventing the actuator 88 from dropping naturally. be able to. The pressure of the conduit 89 of the actuator 88, that is, the load pressure is changed from the first oil passage 53 and the passage 58 to one pressure chamber 65 of the pressure reducing valve section 24.
It is led to. Since the pressure in the other pressure chamber 66 is zero, the pressure reducing valve portion 24 strokes to the stroke end in a direction in which the pressure reducing valve portion 24 dissociates from the check valve portion 23, and the pressure reducing valve portion 24
Pump discharge path 21 and load pressure detection path 82
Communicate. When the pressure (load pressure) in the conduit 89 is higher than the pump discharge pressure (= 20 kg / cm 2 ), the pressure is closed by the pressure in the pressure chamber b of the check valve section 23, and the pressure is reduced to one of the pressure reducing valve sections 24. Since the pressure chamber 65 is guided to the pressure chamber 65, even if the other pressure chamber 66 and the pump discharge path 21 communicate with each other, the pressure reducing valve section 24 remains in a stroke. On the other hand, the pressure (load pressure) in the conduit 41 is the pump discharge pressure (= 20 kg / cm 2 ).
If it is smaller, the load pressure is led to one pressure chamber 65 of the pressure reducing valve section 24, and the pressure reducing valve section 24
When the pressure in the other pressure chamber 66 rises to the pressure in one pressure chamber 65 (that is, load pressure), the stroke is closed by the weak spring 69 and the valve abuts on the check valve portion 23. In any case, the pressure reducing valve section 24 allows the pump discharge path 21 and the pressure chamber 66 to communicate until the pressure in one pressure chamber 65 and the pressure in the other pressure chamber 66 become equal,
If the pressures in the pressure chambers 65 and 66 are equal, the spring 6 is weak.
9 closes the check valve portion 23. As a result, the pressure in the load pressure detection path 82 becomes equal to the load pressure,
The pump discharge pressure is controlled by the pump adjustment direction control valve 85 to a pressure higher than the pressure in the load pressure detection path 82 by a certain differential pressure (here, 20 kg / cm 2 ). This pump discharge pressure is guided to the input port 44 via the check valve section 23, that is, the direction control valve 2
2 between the inlet pressure and the outlet pressure (= load pressure).
0 kg / cm 2 ). Therefore, only by the change in the opening area of the throttle between the inlet side and the outlet side accompanying the stroke of the directional control valve 22, the actuator 8
The flow supplied to 8 is controlled. When the directional control valve 22 is to be stroked, the conduit 89 or 90 of the actuator 88 is connected to the second oil passage 53 for introducing load pressure, while the second oil passage 53 is connected to one pressure chamber 65 of the pressure reducing valve section 24.
The load pressure at the pressure reducing valve section 24 is
Since it is used only as the pilot pressure (set pressure of the pressure reducing valve), the pressure does not escape, that is,
When the directional control valve 22 is stroked, there is no spontaneous lowering of the actuator 88 due to the release of the load pressure.
【００１１】前記負荷圧検出路８２はもう一方の方向制
御弁２２に配設されている圧力補償弁２５の減圧弁部２
４の他方の圧力室６６にも接続されているが、減圧弁部
２４の一方の圧力室６５は、方向制御弁２２の中立位置
Ａによってタンク８６と接続しているため、負荷圧導入
用の第１油路５３内の圧力はゼロで、よって圧力室６６
内の圧力によって減圧弁部２４は、チェック弁部２３を
閉じる方向に付勢する。一方、チェック弁部２４を開く
方向の圧力室ａには、ポンプ吐出路８１よりポンプ吐出
圧が導かれるため、全体として、ポンプ吐出圧と負荷圧
検出路８２内の圧力の差圧分（＝２０ｋｇ／ｃｍ2 ）に
よってチェック弁部２３及び減圧弁部２４をチェック弁
部２３の開く方向にストロークさせるが、わずかにスト
ロークし入力ポート４４の圧力がその差圧（＝２０ｋｇ
／ｃｍ2 ）になれば、弱いばね６９によってレシート
し、結果として、ストロークエンドまで減圧弁部２４が
ストロークすることはなく、方向制御弁２２側の油圧制
御には、何ら影響することはない。The load pressure detecting path 82 is connected to the pressure reducing valve section 2 of the pressure compensating valve 25 disposed on the other directional control valve 22.
4 is connected to the other pressure chamber 66, but one pressure chamber 65 of the pressure reducing valve section 24 is connected to the tank 86 by the neutral position A of the directional control valve 22, so that it is used for introducing load pressure. The pressure in the first oil passage 53 is zero, and
The pressure reducing valve 24 urges the check valve 23 in the closing direction by the internal pressure. On the other hand, since the pump discharge pressure is guided from the pump discharge passage 81 to the pressure chamber a in the direction in which the check valve portion 24 is opened, the difference between the pump discharge pressure and the pressure in the load pressure detection passage 82 (= The check valve unit 23 and the pressure reducing valve unit 24 are stroked in the opening direction of the check valve unit 23 by the pressure of 20 kg / cm 2 ).
/ Cm 2 ), the receipt is performed by the weak spring 69, and as a result, the pressure reducing valve section 24 does not stroke until the stroke end, and the hydraulic control on the direction control valve 22 side is not affected at all.
【００１２】方向制御弁２２のいずれも第１圧油供給
位置Ｂにストロークさせるとき。 −各アクチュエータ８８に必要とされる流量の合計
が油圧ポンプ２０の最大吐出流量位置のとき。いま、方
向制御弁２２をともに第１圧油供給位置Ｂにストローク
させ、各入力ポート４４と各導管８９と各負荷圧導用の
第１油路５３をそれぞれ接続させたとする。一方の減圧
弁部２４は、圧力室６６内の圧力が一方の圧力室６５内
の圧力に等しくなるまで、また他方の減圧弁部２４は、
圧力室６６内の圧力が、一方の圧力室６５内の圧力に等
しくなるまで、それぞれストロークエンドまでストロー
クしたままである。いま、二つのアクチュエータ８８，
８８の負荷圧のうち、左側のアクチュエータ８８の負荷
圧がより大きいとする。仮に、左側アクチュエータ２６
の負荷圧を１００（ｋｇ／ｃｍ2 ）、右側のアクチュエ
ータ２７の負荷圧を１０（ｋｇ／ｃｍ2 ）とする。負荷
圧検出路８２は、絞り９１を介してタンク８６と接続さ
れているので、方向制御弁ストローク前は負荷圧検出路
８２内の圧力はゼロである。よって、各減圧弁部２４は
負荷圧検出用の第１油路５３内の圧力によってもストロ
ークし、ポンプ吐出圧が圧力検出導管３４内の圧力と連
通させる。負荷圧検出路８２内の圧力が低圧側である右
側のアクチュエータ８８の導管９０内の圧力（１０ｋｇ
／ｃｍ2 ）まで上昇すると、まず、右方の圧力補償弁２
５の減圧弁部２４が閉じる。左方の圧力補償弁２５の減
圧弁部２４はストロークしたままであり、負荷圧検出路
８２内の圧力はポンプ吐出圧（２０ｋｇ／ｃｍ2 ）と等
しくなるまで上昇する。このとき高圧側である左側のア
クチュエータ８８の方向制御弁５５の入力ポート４４の
圧力は１００（ｋｇ／ｃｍ2 ）であり、圧力補償弁２５
のチェック弁部２３は閉じていて、減圧弁部２４とは解
離している。一方圧力補償弁２５の減圧弁部２４は、二
つの圧力室６５と６６内の圧力の差（２０−１０＝１０
ｋｇ／ｃｍ2 ）でチェック弁部２３を閉じる方向に付勢
する。一方、チェック弁部２３の開く方向の圧力室ａ内
の圧力（ポンプ吐出圧）は２０（ｋｇ／ｃｍ2 ）である
ため、結果として方向制御弁２２の入力ポート４４の圧
力が１０（ｋｇ／ｃｍ2 ）になるまでチェック弁部２３
が開いた後、弱いばね６９によってレシートする。ポン
プ調整用方向制御弁８５によって、ある差圧（２０ｋｇ
／ｃｍ2 ）分だけ、負荷圧検出路８２内の圧力（２０ｋ
ｇ／ｃｍ2 ）より高い圧力にポンプ吐出圧が制御される
（４０ｋｇ／ｃｍ2 ）。このときも高圧側の圧力補償弁
２５のチェック弁部２３は閉じたままで減圧弁部２４は
ストロークしたままで負荷圧検出路８２内の圧力は４０
（ｋｇ／ｃｍ2 ）となり、一方、低圧側の圧力補償弁２
５の減圧弁部２４は、負荷圧検出路８２と負荷圧導入用
の第１油路５３内の圧力差（＝３０ｋｇ／ｃｍ2 ）でチ
ェック弁部２３を閉じる方向に付勢し、結果として方向
制御弁２２の入力ポート４４の圧力は１０ｋｇ／ｃｍ2
のままである。このようにして、負荷圧検出路８２内の
圧力とポンプ吐出圧が上昇し続け、やがてポンプ吐出圧
が高圧側のアクチュエータ８８の負荷圧（１００ｋｇ／
ｃｍ2）と等しくなると、高圧側の圧力補償弁２５の減
圧弁部２３の二つの圧力室６５と６６内の圧力はともに
１００ｋｇ／ｃｍ2 となり、弱いばね６９によって、閉
じチェック弁部２３に当接する。このとき低圧側の圧力
補償弁２５の減圧弁部２４は負荷圧検出路８２と負荷圧
導入用の第１油路５３内の圧力差（１００−１０＝９０
ｋｇ／ｃｍ2 ）でチェック弁部２３を閉じる方向に付勢
し、結果として低圧側の方向制御弁２２の入力ポート４
４の圧力は１０ｋｇ／ｃｍ2 のままである。再び、ポン
プ調整用方向制御弁８５によって、ポンプ吐出圧が１２
０（ｋｇ／ｃｍ2 ）に制御される。このとき高圧側の圧
力補償弁２５の減圧弁部２３は、弱いばね６９によって
チェック弁部２３に当接しているだけであり、チェック
弁部２３の二つの圧力室ａとｂの圧力差によって、ここ
で始めてチェック弁部２３が開き、ポンプ吐出圧（１２
０ｋｇ／ｃｍ2 ）が方向制御弁２２の入力ポート４４に
導かれる。一方、低圧側の圧力補償弁２５の減圧弁部２
４は負荷圧検出路８２と負荷圧導入用の第１油路５３内
の圧力差（＝９０ｋｇ／ｃｍ2 ）分でチェック弁部２３
を閉じる方向に付勢し続けるが、チェック弁部２３の開
く方向の圧力室ａ内の圧力が１２０（ｋｇ／ｃｍ2 ）に
なったので方向制御弁２２の入口ポート４４の圧力が３
０（ｋｇ／ｃｍ2 ）（１２０−９０）となる状態で、チ
ェック弁部２３及び減圧弁部２４が圧力バランスする。
すなわち、チェック弁部２３及び減圧弁部２４はわずか
にストロークし、チェック弁部２３において、１２０ｋ
ｇ／ｃｍ2 から３０ｋｇ／ｃｍ2 になるように絞ってい
る状態となる。ここで初めて、この油圧制御系はつり合
い、高圧側の方向制御弁２２の入力ポート４４の圧力が
１２０ｋｇ／ｃｍ2 、低圧側の方向制御弁２２の入力ポ
ート４４の圧力が３０ｋｇ／ｃｍ2 となり、すなわち、
二つの方向制御弁２２，２２の入口圧と出口圧（負荷
圧）の差は、ともに２０ｋｇ／ｃｍ2 に保たれることに
より、二つの方向制御弁２２，２２はともに、ストロー
ク分だけで、アクチュエータ８８，８８に供給する流量
を制御することができるようになる。When any of the direction control valves 22 is to be stroked to the first pressure oil supply position B. When the total flow rate required for each actuator 88 is at the maximum discharge flow rate position of the hydraulic pump 20. Now, it is assumed that the directional control valves 22 are both stroked to the first pressure oil supply position B, and the respective input ports 44, the respective conduits 89, and the respective first oil passages 53 for guiding the load pressure are connected. One pressure reducing valve portion 24 is operated until the pressure in the pressure chamber 66 becomes equal to the pressure in the one pressure chamber 65, and the other pressure reducing valve portion 24 is
The respective strokes are continued to the stroke end until the pressure in the pressure chamber 66 becomes equal to the pressure in the one pressure chamber 65. Now, two actuators 88,
It is assumed that the load pressure of the left actuator 88 among the load pressures of 88 is larger. Assuming the left actuator 26
Is 100 (kg / cm 2 ), and the load pressure of the right actuator 27 is 10 (kg / cm 2 ). Since the load pressure detection path 82 is connected to the tank 86 via the throttle 91, the pressure in the load pressure detection path 82 is zero before the directional control valve stroke. Therefore, each pressure reducing valve section 24 also strokes by the pressure in the first oil passage 53 for load pressure detection, and the pump discharge pressure communicates with the pressure in the pressure detection conduit 34. The pressure (10 kg) in the conduit 90 of the right actuator 88 where the pressure in the load pressure detection path 82 is the low pressure side
/ Cm 2 ), first, the right pressure compensating valve 2
5 is closed. The pressure reducing valve portion 24 of the pressure compensating valve 25 on the left side remains in the stroke, and the pressure in the load pressure detecting path 82 increases until it becomes equal to the pump discharge pressure (20 kg / cm 2 ). At this time, the pressure at the input port 44 of the direction control valve 55 of the left actuator 88 on the high pressure side is 100 (kg / cm 2 ), and the pressure compensating valve 25
Is closed and disengaged from the pressure reducing valve section 24. On the other hand, the pressure reducing valve section 24 of the pressure compensating valve 25 is provided with a pressure difference between the two pressure chambers 65 and 66 (20−10 = 10−10).
(kg / cm 2 ) to urge the check valve portion 23 in the closing direction. On the other hand, since the pressure in the pressure chamber a in the opening direction of the check valve portion 23 (pump discharge pressure) is 20 (kg / cm 2 ), as a result, the pressure of the input port 44 of the directional control valve 22 becomes 10 (kg / cm 2 ). cm 2 ) Check valve part 23
After opening, the receipt is made by the weak spring 69. A certain pressure difference (20 kg) is controlled by the pump adjustment direction control valve 85.
/ Cm 2 ), the pressure in the load pressure detection path 82 (20 k
g / cm 2 ), and the pump discharge pressure is controlled to a pressure higher than 40 kg / cm 2 ). Also at this time, the pressure in the load pressure detecting path 82 is 40 while the check valve section 23 of the high-pressure side pressure compensating valve 25 is closed and the pressure reducing valve section 24 is kept in stroke.
(Kg / cm 2 ), while the pressure compensating valve 2 on the low pressure side
The pressure reducing valve portion 24 of No. 5 urges the check valve portion 23 in the closing direction by a pressure difference (= 30 kg / cm 2 ) between the load pressure detecting path 82 and the first oil path 53 for introducing the load pressure, and as a result, The pressure at the input port 44 of the directional control valve 22 is 10 kg / cm 2
Remains. In this way, the pressure in the load pressure detection path 82 and the pump discharge pressure continue to increase, and eventually the pump discharge pressure becomes the load pressure (100 kg /
cm 2 ), the pressures in the two pressure chambers 65 and 66 of the pressure reducing valve portion 23 of the high-pressure side pressure compensating valve 25 both become 100 kg / cm 2 , and are applied to the closing check valve portion 23 by the weak spring 69. Touch At this time, the pressure reducing valve portion 24 of the pressure compensating valve 25 on the low pressure side has a pressure difference (100−10 = 90) between the load pressure detecting path 82 and the first oil path 53 for introducing the load pressure.
kg / cm 2 ) to urge the check valve portion 23 in the closing direction, and as a result, the input port 4 of the directional control valve 22 on the low pressure side.
The pressure of 4 remains at 10 kg / cm 2 . Again, the pump adjustment pressure control valve 85 reduces the pump discharge pressure to 12
It is controlled to 0 (kg / cm 2 ). At this time, the pressure reducing valve portion 23 of the pressure compensating valve 25 on the high pressure side is only in contact with the check valve portion 23 by the weak spring 69, and the pressure difference between the two pressure chambers a and b of the check valve portion 23 causes For the first time, the check valve section 23 opens and the pump discharge pressure (12
0 kg / cm 2 ) is led to the input port 44 of the directional control valve 22. On the other hand, the pressure reducing valve unit 2 of the pressure compensating valve 25 on the low pressure side
Reference numeral 4 denotes a pressure difference (= 90 kg / cm 2 ) between the load pressure detecting path 82 and the first oil path 53 for introducing the load pressure.
However, since the pressure in the pressure chamber a in the opening direction of the check valve portion 120 has become 120 (kg / cm 2 ), the pressure of the inlet port 44 of the directional control valve 22 becomes 3
In a state where the pressure becomes 0 (kg / cm 2 ) (120-90), the pressures of the check valve unit 23 and the pressure reducing valve unit 24 are balanced.
That is, the check valve portion 23 and the pressure reducing valve portion 24 slightly stroke, and the check valve portion 23
It is in a state of being squeezed so as to be from 30 g / cm 2 to 30 kg / cm 2 . For the first time, this hydraulic control system is balanced, the pressure at the input port 44 of the directional control valve 22 on the high pressure side is 120 kg / cm 2 , the pressure at the input port 44 of the directional control valve 22 on the low pressure side is 30 kg / cm 2 , That is,
Since the difference between the inlet pressure and the outlet pressure (load pressure) of the two directional control valves 22 and 22 is both maintained at 20 kg / cm 2 , both of the two directional control valves 22 and 22 have only a stroke. The flow rate supplied to the actuators 88, 88 can be controlled.
【００１３】−各アクチュエータ８８，８８に必要
とされる流量は合計が油圧ポンプ８０の最大吐出流量以
上のとき。いま、アクチュエータ８８，８８の負荷圧お
よび必要流量を左側のアクチュエータ８８が１００ｋｇ
／ｃｍ2 、５０１／ｍｉｎ、右側のアクチュエータ８８
が１０ｋｇ／ｃｍ2 、５０１／ｍｉｎとする。油圧ポン
プ８０の最大吐出流量が１００１／ｍｉｎ以上のとき
は、前述の通り、方向制御弁２２，２２の入口圧と出口
圧の差が一定に保たれる（＝２０ｋｇ／ｃｍ2 ）ため、
ストロークによって流量制御ができ、５０１／ｍｉｎず
つ流量分配することはできる。次に、油圧ポンプ８０の
滞在吐出量が７０１／ｍｉｎになったとする。二つの方
向制御弁２２，２２の入口圧は前述の通り１２０ｋｇ／
ｃｍ2 、３０ｋｇ／ｃｍ2 であるので、高圧側の方向制
御弁２２への流量が５０１／ｍｉｎから２０１／ｍｉｎ
に減る。低圧側の方向制御弁２２への流量は、５０１／
ｍｉｎのままである。二つの方向制御弁２２，２２のス
トローク（開口面積）を変えないとすると、高圧側の方
向制御弁２２の入口圧と出口圧の差圧が流量が減った
分、２０ｋｇ／ｃｍ2 から下がる。いま、差圧が１４ｋ
ｇ／ｃｍ2 、すなわち、入口圧が、１２０ｋｇ／ｃｍ2
から１１４（１００＋１４）ｋｇ／ｃｍ2 に下がったと
する。この時圧力補償弁２５の減圧弁部２４の二つの圧
力室６５，６６の圧力は、ともに１００ｋｇ／ｃｍ2 の
ままであるから、減圧弁部２４は弱いばね６９によって
チェック弁部２３に当接しているだけであり、チェック
弁部２３の閉じる方向の圧力室ｂ内の圧力が１２０ｋｇ
／ｃｍ2 から１１４ｋｇ／ｃｍ2 に減少すれば、チェッ
ク弁部２３が開いたまま（ストロークエンド）で、チェ
ック弁部２３の開く方向の圧力室ａ内の圧力、すなわ
ち、ポンプ吐出圧が１２０ｋｇ／ｃｍ2 から１１４ｋｇ
／ｃｍ2 に減少する。この時（ポンプ吐出流量不足時）
にはポンプ吐出圧はポンプ調整用方向制御弁８５の制御
によらなくなる。一方、低圧側の圧力補償弁２５の減圧
弁部２４の二つの圧力室６５と６６は、１００ｋｇ／ｃ
ｍ2 、１０ｋｇ／ｃｍ2 のままで、その差圧９０ｋｇ／
ｃｍ2 でチェック弁部６３の閉じる方向に付勢し続け
る。一方、チェック弁部２３の開く方向の圧力室ａ内の
圧力、すなわちポンプ吐出圧が１１４ｋｇ／ｃｍ2 に減
少したので、チェック弁部２３の閉じる方向の圧力室ｂ
内の圧力が３０ｋｇ／ｃｍ2から２４ｋｇ／ｃｍ2 に減
少した状態でチェック弁部２３及び減圧弁部２４が圧力
バランスする。よって、低圧側の方向制御弁２２の入口
圧と出口圧の差圧は２０ｋｇ／ｃｍ2 から１４ｋｇ／ｃ
ｍ2 （２４−１０）に減少する。方向制御弁２２のこの
差圧の減少により低圧側のアクチュエータ８８への供給
流量は５０１／ｍｉｎから減少し、その分高圧側のアク
チュエータ８８への供給流量が２０１／ｍｉｎから増え
る。すなわち、方向制御弁２２および２２の入口圧と出
口圧の差圧が等しく、かつ、二つのアクチュエータ８
８，８８への供給量がともに３５１／ｍｉｎずつに分配
される状態で、この油圧制御系がつり合う。When the sum of the flow rates required for the actuators 88 is greater than or equal to the maximum discharge flow rate of the hydraulic pump 80. Now, the load pressure and the required flow rate of the actuators 88, 88 are set to 100 kg by the left actuator 88.
/ Cm 2 , 501 / min, right actuator 88
Is 10 kg / cm 2 and 501 / min. When the maximum discharge flow rate of the hydraulic pump 80 is 1001 / min or more, as described above, the difference between the inlet pressure and the outlet pressure of the directional control valves 22, 22 is kept constant (= 20 kg / cm 2 ).
The flow rate can be controlled by the stroke, and the flow rate can be distributed every 501 / min. Next, it is assumed that the stay discharge amount of the hydraulic pump 80 becomes 701 / min. As described above, the inlet pressure of the two directional control valves 22, 22 is 120 kg /
cm 2 and 30 kg / cm 2 , the flow rate to the high-pressure side directional control valve 22 is from 501 / min to 201 / min.
Reduced to The flow rate to the low pressure side directional control valve 22 is 501 /
min. If the strokes (opening areas) of the two directional control valves 22 and 22 are not changed, the differential pressure between the inlet pressure and the outlet pressure of the high-pressure side directional control valve 22 drops from 20 kg / cm 2 by the reduced flow rate. Now the differential pressure is 14k
g / cm 2 , ie, the inlet pressure is 120 kg / cm 2
To 114 (100 + 14) kg / cm 2 . At this time, since the pressures in the two pressure chambers 65 and 66 of the pressure reducing valve portion 24 of the pressure compensating valve 25 remain at 100 kg / cm 2 , the pressure reducing valve portion 24 comes into contact with the check valve portion 23 by the weak spring 69. And the pressure in the pressure chamber b in the closing direction of the check valve portion 23 is 120 kg.
/ Cm 2 to 114 kg / cm 2 , the pressure in the pressure chamber a in the direction in which the check valve 23 opens, that is, the pump discharge pressure is 120 kg / cm 2 while the check valve 23 remains open (stroke end). 114kg from cm 2
/ Cm 2 . At this time (when the pump discharge flow rate is insufficient)
Therefore, the pump discharge pressure is no longer controlled by the pump adjusting direction control valve 85. On the other hand, the two pressure chambers 65 and 66 of the pressure reducing valve section 24 of the pressure compensating valve 25 on the low pressure side have a pressure of 100 kg / c.
m 2 , 10 kg / cm 2 and the differential pressure 90 kg / cm 2
The pressure continues to be urged in the closing direction of the check valve 63 at cm 2 . On the other hand, since the pressure in the pressure chamber a in the direction in which the check valve portion 23 opens, that is, the pump discharge pressure has been reduced to 114 kg / cm 2 , the pressure chamber b in the direction in which the check valve portion 23 closes.
The check valve section 23 and the pressure reducing valve section 24 are pressure-balanced in a state where the internal pressure is reduced from 30 kg / cm 2 to 24 kg / cm 2 . Therefore, the differential pressure between the inlet pressure and the outlet pressure of the low pressure side directional control valve 22 is 20 kg / cm 2 to 14 kg / c.
m 2 (24-10). Due to the decrease in the differential pressure of the directional control valve 22, the supply flow rate to the low-pressure side actuator 88 decreases from 501 / min, and the supply flow rate to the high-pressure side actuator 88 increases accordingly from 201 / min. That is, the differential pressure between the inlet pressure and the outlet pressure of the directional control valves 22 and 22 is equal, and the two actuators 8
The hydraulic control system is balanced in a state where the supply amounts to 8, 88 are both distributed at 351 / min.
【００１４】一つの油圧ポンプ８０によって負荷され
るアクチュエータが３つ以上のとき。アクチュエータが
３つ以上のときも、方向制御弁と油圧ポンプの間に、同
じチェック弁部２３及び減圧弁部２４を備えた圧力補償
弁２５を配設し、各減圧弁部の閉じる方向の圧力差を負
荷圧検出路８２によってすべて連通するだけで、アクチ
ュエータが３つ以上のときも前述の作動原理による作動
が実現される。When there are three or more actuators loaded by one hydraulic pump 80. Even when there are three or more actuators, a pressure compensating valve 25 having the same check valve portion 23 and pressure reducing valve portion 24 is disposed between the directional control valve and the hydraulic pump, and the pressure in the closing direction of each pressure reducing valve portion is arranged. The operation based on the above-described operation principle can be realized even when the number of actuators is three or more, by merely communicating all the differences by the load pressure detection path 82.
【００１５】[0015]
【考案が解決しようとする課題】かかる圧油供給装置で
あるとアクチュエータ８８からの戻り油がタンクポート
に流出し、アクチュエータ８８には油圧ポンプ２０の吐
出圧油のみが供給されるから大流量を必要とするアクチ
ュエータの場合にはポンプ吐出量を増加せねばならず動
力損失、コスト上不利となる。In such a pressurized oil supply device, the return oil from the actuator 88 flows out to the tank port, and only the discharge pressure oil of the hydraulic pump 20 is supplied to the actuator 88. In the case of a required actuator, the pump discharge amount must be increased, which is disadvantageous in power loss and cost.
【００１６】そこで、本考案は前述の課題を解決できる
ようにした圧油供給装置を提供することを目的とする。Therefore, an object of the present invention is to provide a pressure oil supply device capable of solving the above-mentioned problems.
【００１７】[0017]
【課題を解決するための手段】弁ブロック３０にスプー
ル孔３１とチェック弁用孔３７と減圧弁用孔３８を形成
し、前記弁ブロック３０にはスプール孔３１に開口した
入力ポート４４、第１・第２負荷圧検出ポート４５，４
６、第１・第２アクチュエータポート３４，３５、第１
・第２タンクポート４７，４８をそれぞれ形成し、この
スプール孔３１に各ポートを連通・遮断する主スプール
４９を嵌挿して方向制御弁２２とし、この主スプール４
９に第１・第２負荷圧検出ポート４５，４６を第１・第
２タンクポート４７，４８に連通・遮断する第１・第２
油路５３，５４を形成し、前記弁ブロック３０にはチェ
ック弁用孔３７に開口したポンプポート３９及びチェッ
ク弁用孔３７を入力ポート４４に連通する油路５６を形
成し、そのチェック弁用孔３７にポンプポート３９と油
路５６を連通・遮断し、かつ遮断位置でストップされる
スプール６０を挿入してチェック弁部２３とし、前記弁
ブロック３０には減圧弁用孔３８に開口する第１・第２
ポート４２，４３を形成し、この減圧弁用孔３８にスプ
ール６４を嵌挿して第１圧力室６５と第２圧力室６６を
形成し、その第１圧力室６５を第２負荷圧検出ポート４
６に連通し、第２圧力室６６を第２ポート４３に連通
し、前記スプール６４をばね６９で一方向に付勢して前
記チェック弁部２３のスプール６０を遮断位置に押しつ
け保持して減圧弁部２４とし、この減圧弁部２４と前記
チェック弁部２３で圧力補償弁２５とし、前記ポンプ・
第１ポート３９，４２に油圧ポンプ２０の吐出路２１を
接続し、前記第２ポート４３に負荷圧検出路８２を接続
し、前記第２油路５４を、第２負荷圧検出ポート４６に
連通・遮断する第１の軸孔と、第２アクチュエータポー
ト３５と第２タンクポート４８を連通・遮断する第２の
軸孔と、前記第１の軸孔と第２の軸孔を連通するチェッ
ク弁１０５で形成し、このチェック弁１０５は第２の軸
孔から第１の軸孔への圧油流れを阻止し、かつ第１の軸
孔の圧力で許容する形状であることを特徴とする圧油供
給装置。A spool hole 31, a check valve hole 37, and a pressure reducing hole 38 are formed in the valve block 30, and an input port 44 opened in the spool hole 31 is provided in the valve block 30. .Second load pressure detection ports 45 and 4
6, the first and second actuator ports 34, 35, the first
The second spool ports 47 and 48 are respectively formed, and a main spool 49 for communicating and blocking each port is inserted into the spool hole 31 to form the direction control valve 22.
9, the first and second load pressure detecting ports 45 and 46 are connected to and disconnected from the first and second tank ports 47 and 48, respectively.
Oil passages 53 and 54 are formed, and an oil passage 56 is formed in the valve block 30 to connect the pump port 39 opened to the check valve hole 37 and the check valve hole 37 to the input port 44. The pump port 39 communicates with the oil passage 56 in the hole 37 and is shut off, and a spool 60 stopped at the shutoff position is inserted into the check valve portion 23, and the valve block 30 is opened to the pressure reducing valve hole 38. 1 ・ second
Ports 42 and 43 are formed, and a spool 64 is inserted into the pressure reducing valve hole 38 to form a first pressure chamber 65 and a second pressure chamber 66. The first pressure chamber 65 is connected to the second load pressure detection port 4.
6, the second pressure chamber 66 is communicated with the second port 43, and the spool 64 is urged in one direction by a spring 69 to press and hold the spool 60 of the check valve portion 23 in the shut-off position to reduce the pressure. The pressure reducing valve part 24 and the check valve part 23 constitute a pressure compensating valve 25, and the pump
The discharge port 21 of the hydraulic pump 20 is connected to the first ports 39 and 42, the load pressure detection path 82 is connected to the second port 43, and the second oil path 54 communicates with the second load pressure detection port 46. A first shaft hole to be shut off, a second shaft hole to communicate and shut off the second actuator port 35 and the second tank port 48, and a check valve to communicate the first shaft hole and the second shaft hole. The check valve 105 is formed in a shape which prevents the flow of pressurized oil from the second shaft hole to the first shaft hole and has a shape which is allowed by the pressure of the first shaft hole. Oil supply device.
【００１８】[0018]
【作 用】アクチュエータ８８からの戻り油の一部が
第２アクチュエータポート３５、第２の軸孔、チェック
弁１０５、第１の軸孔を経て第２負荷圧検出ポート４
６、第１負荷圧検出ポート４５に流入するから、アクチ
ュエータ８８からの戻り油の一部をアクチュエータ８８
に直接供給でき、油圧ポンプ２０の吐出流量を増大せず
にアクチュエータ８８に大流量を供給できる。また、チ
ェック弁部２３と減圧弁部２４で圧力補償弁２５とし、
その減圧弁部２４の第２ポート４３に負荷圧検出路８２
を接続したので、アクチュエータの負荷圧を比較して高
い方の負荷圧を圧力補償弁に供給するシャトル弁が不要
である。[Operation] A part of the return oil from the actuator 88 passes through the second actuator port 35, the second shaft hole, the check valve 105, the first shaft hole, and the second load pressure detection port 4.
6. Since the oil flows into the first load pressure detection port 45, part of the return oil from the actuator 88
Can be directly supplied to the actuator 88 without increasing the discharge flow rate of the hydraulic pump 20. Further, the check valve section 23 and the pressure reducing valve section 24 constitute a pressure compensating valve 25,
A load pressure detecting path 82 is connected to the second port 43 of the pressure reducing valve section 24.
Is connected, it is not necessary to provide a shuttle valve for comparing the load pressure of the actuator and supplying a higher load pressure to the pressure compensating valve.
【００１９】[0019]
【実 施 例】図４と図５に示すように、主スプール４
９に形成した第２負荷圧検出ポート４６と第２タンクポ
ート４８を連通・遮断する第２油路５４は、小径軸孔１
００と大径軸孔１０１と小径軸孔１００を主スプール外
周面に開口する径方向穴１０２と大径軸孔１０１を主ス
プール外周面に開口する径方向穴１０３より成り、その
大径軸孔１０１は半径方向穴１０４で第２アクチュエー
タポート３５に開口していると共に、大径軸孔１０１か
ら小径軸孔１００に圧油流れを阻止するチェック弁１０
５が設けてある。なお、主スプール４９には中間小径部
１０６が形成されて入力ポート４４を第１又は第２負荷
圧検出ポート４５，４６の一方に連通するようにしてあ
ると共に、その第１・第２負荷圧検出ポート４５，４６
を連通する連通孔１０７が形成してある。以上の構成を
模式的に表わすと図６に示すようになる。[Embodiment] As shown in FIG. 4 and FIG.
9, a second oil passage 54 that communicates and shuts off the second load pressure detection port 46 and the second tank port 48 is provided in the small-diameter shaft hole 1.
00, a large-diameter shaft hole 101 and a small-diameter shaft hole 100 are formed on the outer peripheral surface of the main spool, and a large-diameter hole 103 is formed on the main spool outer peripheral surface. The check valve 101 is a radial hole 104 which is open to the second actuator port 35, and which prevents the flow of pressurized oil from the large diameter shaft hole 101 to the small diameter shaft hole 100.
5 are provided. The main spool 49 has an intermediate small-diameter portion 106 formed so that the input port 44 communicates with one of the first and second load pressure detection ports 45 and 46, and the first and second load pressures. Detection ports 45, 46
A communication hole 107 is formed to communicate with. FIG. 6 schematically shows the above configuration.
【００２０】次に作動を説明する。主スプール４９を右
方に摺動して第１圧油供給位置Ｂとすると、油圧ポンプ
２０の吐出圧油が入力ポート４４、中間小径部１０６、
第２負荷圧検出ポート４６、連通孔１０７、第１負荷圧
検出ポート４５、第１小径部５０、第１アクチュエータ
ポート３４よりアクチュエータ８８に供給され、アクチ
ュエータ８８の戻り油は第２アクチュエータポート３
５、半径方向穴１０４、大径軸孔１０１、径方向穴１０
３より第２タンクポート４８に流出する。この時、第２
負荷圧検出ポート４６と径方向穴１０３が流通して第２
負荷圧検出ポート４６の圧油が小径軸孔１００に流入し
てチェック弁１０５を押し開き、アクチュエータ８８の
戻り油が増加すると第２アクチュエータポート３５から
戻り油の一部が半径方向穴１０４、大径軸孔１０１、チ
ェック弁１０５、小径軸孔１００、半径方向穴１０２よ
り第２負荷圧検出ポート４６に流れてアクチュエータ８
８に再生される。Next, the operation will be described. When the main spool 49 is slid rightward to the first pressure oil supply position B, the discharge pressure oil of the hydraulic pump 20 is supplied to the input port 44, the intermediate small diameter portion 106,
The second load pressure detection port 46, the communication hole 107, the first load pressure detection port 45, the first small diameter portion 50, and the first actuator port 34 are supplied to the actuator 88, and the return oil of the actuator 88 is supplied to the second actuator port 3.
5, radial hole 104, large diameter shaft hole 101, radial hole 10
3 flows out to the second tank port 48. At this time, the second
The load pressure detection port 46 and the radial hole 103
When the pressure oil of the load pressure detection port 46 flows into the small-diameter shaft hole 100 to open the check valve 105 and the return oil of the actuator 88 increases, a part of the return oil from the second actuator port 35 becomes large in the radial hole 104. The fluid flows from the radial shaft hole 101, the check valve 105, the small-diameter shaft hole 100, and the radial hole 102 to the second load pressure detection port 46, and the actuator 8
8 is played.
【００２１】[0021]
【考案の効果】アクチュエータ８８からの戻り油の一部
が第２アクチュエータポート３５、第２の軸孔、チェッ
ク弁１０５、第１の軸孔を経て第２負荷圧検出ポート４
６、第１負荷圧検出ポート４５に流入するから、アクチ
ュエータ８８からの戻り油の一部をアクチュエータ８８
に直接供給でき、油圧ポンプ２０の吐出流量を増大せず
にアクチュエータ８８に大流量を供給できる。また、チ
ェック弁部２３と減圧弁部２４で圧力補償弁２５とし、
その減圧弁部２４の第２ポート４３に負荷圧検出路８２
を接続したので、アクチュエータの負荷圧を比較して高
い方の負荷圧を圧力補償弁に供給するシャトル弁が不要
である。A part of the return oil from the actuator 88 passes through the second actuator port 35, the second shaft hole, the check valve 105, the first shaft hole, and the second load pressure detecting port 4.
6. Since the oil flows into the first load pressure detection port 45, part of the return oil from the actuator 88
Can be directly supplied to the actuator 88 without increasing the discharge flow rate of the hydraulic pump 20. Further, the check valve section 23 and the pressure reducing valve section 24 constitute a pressure compensating valve 25,
A load pressure detecting path 82 is connected to the second port 43 of the pressure reducing valve section 24.
Is connected, it is not necessary to provide a shuttle valve for comparing the load pressure of the actuator and supplying a higher load pressure to the pressure compensating valve.
【図１】従来の圧油供給装置の回路図である。FIG. 1 is a circuit diagram of a conventional pressure oil supply device.
【図２】先に出願した圧油供給装置の回路図である。FIG. 2 is a circuit diagram of a pressure oil supply device filed earlier.
【図３】弁ブロックに主スプール、スプールを組み込ん
だ状態の断面図である。FIG. 3 is a sectional view showing a state in which a main spool and a spool are incorporated in a valve block.
【図４】本考案の実施例を示す弁ブロックに主スプー
ル、スプールを組み込んだ状態の断面図である。FIG. 4 is a sectional view of the valve block according to the embodiment of the present invention, in which the main spool and the spool are assembled.
【図５】油路部分の拡大図である。FIG. 5 is an enlarged view of an oil passage portion.
【図６】油圧回路図である。FIG. 6 is a hydraulic circuit diagram.
２０…油圧ポンプ、２１…吐出路、２２…方向制御弁、
２３…チェック弁部、２４…減圧弁部、２５…圧力補償
弁、３０…弁ブロック、３１…スプール孔、３４…第１
アクチュエータポート、３５…第２アクチュエータポー
ト、３７…チェック弁用孔、３８…減圧弁用孔、３９…
ポンプポート、４２…第１ポート、４３…第２ポート、
４４…入力ポート、４５…第１負荷圧検出ポート、４６
…第２負荷圧検出ポート、４７…第１タンクポート、４
８…第２タンクポート、４９…主スプール、５３…第１
油路、５４…第２油路、５６…油孔、５８…油孔、６０
…スプール、６４…スプール、６５…第１圧力室、６６
…第２圧力室、６９…ばね、８２…負荷圧検出路、８８
…アクチュエータ、１０５…チェック弁。Reference numeral 20: hydraulic pump, 21: discharge path, 22: directional control valve,
23 check valve part, 24 pressure reducing valve part, 25 pressure compensation valve, 30 valve block, 31 spool hole, 34 first
Actuator port, 35 ... second actuator port, 37 ... check valve hole, 38 ... pressure reducing valve hole, 39 ...
Pump port, 42 ... first port, 43 ... second port,
44 input port, 45 first load pressure detection port, 46
... second load pressure detection port, 47 ... first tank port, 4
8 ... second tank port, 49 ... main spool, 53 ... first
Oil passage, 54 ... second oil passage, 56 ... oil hole, 58 ... oil hole, 60
... Spool, 64 ... Spool, 65 ... First pressure chamber, 66
... second pressure chamber, 69 ... spring, 82 ... load pressure detection path, 88
... actuator, 105 ... check valve.
フロントページの続き (56)参考文献 特開 昭56−167902（ＪＰ，Ａ) 特開 平２−247801（ＪＰ，Ａ) 特開 平２−134401（ＪＰ，Ａ) 特開 昭58−196371（ＪＰ，Ａ) 実開 平５−32802（ＪＰ，Ｕ) (58)調査した分野(Int.Cl.6，ＤＢ名) F15B 11/00 F15B 11/05 F15B 11/16 F15B 13/06Continuation of front page (56) References JP-A-56-167902 (JP, A) JP-A-2-247801 (JP, A) JP-A-2-134401 (JP, A) JP-A-58-196371 (JP) , A) Hira 5-32802 (JP, U) (58) Fields investigated (Int. Cl. 6 , DB name) F15B 11/00 F15B 11/05 F15B 11/16 F15B 13/06
Claims (1)
ック弁用孔３７と減圧弁用孔３８を形成し、前記弁ブロ
ック３０にはスプール孔３１に開口した入力ポート４
４、第１・第２負荷圧検出ポート４５，４６、第１・第
２アクチュエータポート３４，３５、第１・第２タンク
ポート４７，４８をそれぞれ形成し、このスプール孔３
１に各ポートを連通・遮断する主スプール４９を嵌挿し
て方向制御弁２２とし、この主スプール４９に第１・第
２負荷圧検出ポート４５，４６を第１・第２タンクポー
ト４７，４８に連通・遮断する第１・第２油路５３，５
４を形成し、 前記弁ブロック３０にはチェック弁用孔３７に開口した
ポンプポート３９及びチェック弁用孔３７を入力ポート
４４に連通する油路５６を形成し、そのチェック弁用孔
３７にポンプポート３９と油路５６を連通・遮断し、か
つ遮断位置でストップされるスプール６０を挿入してチ
ェック弁部２３とし、 前記弁ブロック３０には減圧弁用孔３８に開口する第１
・第２ポート４２，４３を形成し、この減圧弁用孔３８
にスプール６４を嵌挿して第１圧力室６５と第２圧力室
６６を形成し、その第１圧力室６５を第２負荷圧検出ポ
ート４６に連通し、第２圧力室６６を第２ポート４３に
連通し、前記スプール６４をばね６９で一方向に付勢し
て前記チェック弁部２３のスプール６０を遮断位置に押
しつけ保持して減圧弁部２４とし、この減圧弁部２４と
前記チェック弁部２３で圧力補償弁２５とし、前記ポン
プ・第１ポート３９，４２に油圧ポンプ２０の吐出路２
１を接続し、前記第２ポート４３に負荷圧検出路８２を
接続し、前記第２油路５４を、第２負荷圧検出ポート４６に連通
・遮断する第１の軸孔と、第２アクチュエータポート３
５と第２タンクポート４８を連通・遮断する第２の軸孔
と、前記第１の軸孔と第２の軸孔を連通するチェック弁
１０５で形成し、このチェック弁１０５は第２の軸孔か
ら第１の軸孔への圧油流れを阻止し、かつ第１の軸孔の
圧力で許容する形状であることを特徴とする圧油供給装
置。 1. A valve block 30 has a spool hole 31, a check valve hole 37, and a pressure reducing valve hole 38, and the valve block 30 has an input port 4 opened to the spool hole 31.
4, first and second load pressure detection ports 45 and 46, first and second actuator ports 34 and 35, and first and second tank ports 47 and 48, respectively.
A first spool 49 for connecting and disconnecting each port is inserted into the first spool 49 to form the directional control valve 22, and first and second load pressure detection ports 45 and 46 are connected to the first and second tank ports 47 and 48. First and second oil passages 53 and 5 that communicate with and shut off
The valve block 30 is formed with a pump port 39 opened to the check valve hole 37 and an oil passage 56 communicating the check valve hole 37 to the input port 44. A pump is formed in the check valve hole 37. The spool 39 which communicates / blocks the port 39 with the oil passage 56 and is stopped at the blocking position is inserted into the check valve portion 23.
The second ports 42 and 43 are formed, and the pressure reducing valve holes 38 are formed.
A first pressure chamber 65 and a second pressure chamber 66 are formed by inserting a spool 64 into the first pressure chamber 65, the first pressure chamber 65 is communicated with the second load pressure detection port 46, and the second pressure chamber 66 is connected to the second port 43. , The spool 64 is urged in one direction by a spring 69 to press and hold the spool 60 of the check valve portion 23 at the shut-off position to form the pressure reducing valve portion 24. The pressure reducing valve portion 24 and the check valve portion Reference numeral 23 designates a pressure compensating valve 25, and the pump / first ports 39 and 42 are connected to the discharge path 2 of the hydraulic pump 20.
1 is connected, the load pressure detection path 82 is connected to the second port 43, and the second oil path 54 is connected to the second load pressure detection port 46.
A first shaft hole to be shut off and a second actuator port 3
Second shaft hole for communicating / cutting off the second tank port 48 with the fifth tank port 48
And a check valve communicating the first shaft hole and the second shaft hole.
The check valve 105 is formed with a second shaft hole.
From the first shaft hole to the first shaft hole, and
Pressure oil supply device characterized in that it has a shape that allows pressure
Place.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP1992049503U JP2577676Y2 (en) | 1992-06-23 | 1992-06-23 | Pressure oil supply device |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP1992049503U JP2577676Y2 (en) | 1992-06-23 | 1992-06-23 | Pressure oil supply device |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| JPH064404U JPH064404U (en) | 1994-01-21 |
| JP2577676Y2 true JP2577676Y2 (en) | 1998-07-30 |
Family
ID=12832942
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP1992049503U Expired - Lifetime JP2577676Y2 (en) | 1992-06-23 | 1992-06-23 | Pressure oil supply device |
Country Status (1)
| Country | Link |
|---|---|
| JP (1) | JP2577676Y2 (en) |
Families Citing this family (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN114294280B (en) * | 2021-12-26 | 2024-04-09 | 浙江海宏液压科技股份有限公司 | Working valve plate and multi-way valve |
Family Cites Families (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPS56167902A (en) * | 1980-05-26 | 1981-12-23 | Daikin Ind Ltd | Reducing type pressure compensation valve with check valve |
| JPS58196371A (en) * | 1982-05-11 | 1983-11-15 | Diesel Kiki Co Ltd | Direction change-over valve |
| JPH02134401A (en) * | 1988-11-10 | 1990-05-23 | Diesel Kiki Co Ltd | Hydraulic control unit |
| JPH0799561B2 (en) * | 1989-03-20 | 1995-10-25 | 松下電器産業株式会社 | Magnetic recording / reproducing device |
-
1992
- 1992-06-23 JP JP1992049503U patent/JP2577676Y2/en not_active Expired - Lifetime
Also Published As
| Publication number | Publication date |
|---|---|
| JPH064404U (en) | 1994-01-21 |
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