JPH061801U - Pressure oil supply device - Google Patents
Pressure oil supply deviceInfo
- Publication number
- JPH061801U JPH061801U JP4677792U JP4677792U JPH061801U JP H061801 U JPH061801 U JP H061801U JP 4677792 U JP4677792 U JP 4677792U JP 4677792 U JP4677792 U JP 4677792U JP H061801 U JPH061801 U JP H061801U
- Authority
- JP
- Japan
- Prior art keywords
- pressure
- port
- spool
- check valve
- valve portion
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
- Granted
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Abstract
(57)【要約】 （修正有）
【目的】 慣性体をハンチングなしにスムーズに動作制
御できるようにする。
【構成】 弁ブロック３０のスプール孔３１に主スプー
ル４９を嵌挿して方向制御弁２２とし，チェック弁用孔
３７にスプール６０を嵌挿してチェック弁部２３とし，
減圧弁用孔３８にスプール６４を嵌挿して第１圧力室６
５と第２圧力室６６とを構成する。第１圧力室６５を方
向制御弁２２の負荷圧検出ポートに連通し，第２圧力室
６６を第２ポート４３に連通し，そのスプール６４をば
ね６９でスプール６０側に押して減圧弁部２４とする。
ポンプポート３９と第１ポート４２にポンプ吐出路を接
続し，第２ポート４３，負荷圧検出回路を接続してチェ
ック弁部２３と減圧弁部とで圧力補償弁２５とする。主
スプールに第１・第２絞り１００，１０１を形成してア
クチュエータポートの圧油をブリードオフして圧力上昇
を緩かにする。
(57) [Summary] (Modified) [Purpose] To enable smooth motion control of inertial bodies without hunting. A main spool 49 is inserted into a spool hole 31 of a valve block 30 to form a directional control valve 22, and a spool 60 is inserted into a check valve hole 37 to form a check valve portion 23.
The spool 64 is fitted into the pressure reducing valve hole 38, and the first pressure chamber 6
5 and the second pressure chamber 66. The first pressure chamber 65 communicates with the load pressure detection port of the directional control valve 22, the second pressure chamber 66 communicates with the second port 43, and the spool 64 is pushed toward the spool 60 side by the spring 69 so that the pressure reducing valve section 24 is formed. To do.
The pump discharge path is connected to the pump port 39 and the first port 42, the second port 43 and the load pressure detection circuit are connected, and the check valve portion 23 and the pressure reducing valve portion form the pressure compensating valve 25. The first and second throttles 100 and 101 are formed on the main spool to bleed off the pressure oil in the actuator port to moderate the pressure increase.
Description
【０００１】[0001]
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。 The present invention relates to a hydraulic oil supply device that supplies the hydraulic oil discharged from one hydraulic pump to a plurality of actuators.
【０００２】[0002]
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 ，１３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。 A pressure oil supply device disclosed in Japanese Patent Laid-Open No. 60-11706 is known. That is, as shown in FIG. 1, a plurality of pressure compensating valves 3 and 13 are connected in parallel to a discharge conduit 2 of a hydraulic pump 1, and directional control valves 5 and 15 are connected to outlet conduits 4 and 14 of each pressure compensating valve 3 and 13. The output sides of the directional control valves 5 and 15 are connected to the actuators 6 and 16, respectively, and the pressure compensating valves 3 and 13 are pushed in the opening direction by the pump discharge pressure and the directional control valve outlet pressure to control the direction. It is a pressure oil supply device that is structured to be pushed in the closing direction by the 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 pressure oil supply device, the shuttle valve 7 is indispensable for comparing the load pressure of the actuator and supplying the higher load pressure to the pressure compensating valve, and moreover, the shuttle valve 7 is the actuator. Only one less than is needed, and the cost is higher. Further, in the above-described pressure oil supply device shown in FIG. 1, it is assumed that the two actuators 6 and 12 are both actuated, and the load pressure on the actuator 6 side is large among those load pressures. 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 pushed. Therefore, when the shuttle valve 7 is switched, the actuator 6 is transiently lowered naturally and the actuator 6 is accelerated. Therefore, the present applicant previously applied for a pressure oil supply device capable of solving the above-mentioned problems.
【０００４】[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２３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。 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 。 As shown in FIG. 2, such a pressure oil supply device is provided with a plurality of directional control valves 22 in a discharge passage 21 of a hydraulic pump 20, and a check valve portion 23 and a pressure reducing valve portion 24 are provided on the inlet side of each directional control valve 22. The pressure compensating valves 25 are respectively provided, and the directional control valve 22 and the pressure compensating valve 25 are configured as shown in FIG. That is, as shown in FIG. 3, the valve block 30 has a substantially rectangular parallelepiped shape, and a spool hole 31 is formed in the left and right side surfaces 32 and 33 near the upper portion of the valve block 30. The second actuator ports 34, 35 are formed so as to open on the upper surface 36, and the check valve hole 37 opened on the left side surface 32 and the pressure reducing valve hole opened on the right side surface 33 are formed near the lower part of the valve block 30. 38 is formed concentrically, a pump port 39 opened in the check valve hole 37 is formed in the front and rear surfaces, and first and second ports 42, 43 opened in the pressure reducing valve hole 38 are formed. The first and second ports 39, 42, 43 of the pumps communicate with each other when the front and rear surfaces of a plurality of valve blocks 30 are butted and connected to each other.
【０００５】 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３４，３ ５、第１、第２タンクポート４７，４８、第１・第２負荷圧検出ポート４５，４ ６を連通する連通路５３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 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、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アクチュエーポート３４を第１タンクポート４ ７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４ ６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 in a spool hole 31, first and second load pressure detection ports 45 and 46, first and second actuator ports 34 and 35, first and second ports. A communication passage 53 is formed to connect the tank ports 47, 48 and the first and second load pressure detection ports 45, 46, and the main spool 49 fitted in the spool hole 31 has the first and second small diameter portions 50. , 51 and a communication groove 52 are formed, and an oil passage 54 is formed in the main spool 49 to connect and disconnect the second load pressure detection port 46 and the second tank port 48. The spool 49 is a spring. The port is shut off, and the oil passage 54 holds the second load pressure detection port 46 and the second tank port 48 in the neutral position. When the spool 49 slides to the right, the second small diameter portion 51 causes the second actuator port to move. - Port 35 communicates with the second tank port 48, the communication groove 52 allows the input port 44 to communicate with the second load pressure detection port 46, and the first small diameter portion 50 allows the first actuator port 34 to communicate with the first load pressure detection port. When the spool 49 slides to the left, the first small-diameter portion 50 causes the first actuator port to communicate with the second load pressure detection port 46 and the second tank port 48. 34 communicates with the first tank port 47, the input groove 44 communicates with the first load pressure detection port 45 in the communication groove 52, and the second actuator port 35 communicates with the second load pressure detection port in the second small diameter portion 51. The directional control valve 22 is located at a second pressure oil supply position that communicates with the second load pressure detection port 46 and the second tank port 48.
【０００６】 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６０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５７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６ ８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７ ２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７４と前記チェック弁部６３とで圧力補償弁２５を構成し ている。The check valve hole 37 is opened to the input port 44 by the oil passage 56, and the check valve hole 37 is fitted with a valve 60 that cuts off the communication between the pump port 39 and the input port 44. Numeral 60 is a stopper rod 62 provided on the plug 61, which is regulated so as not to slide to the left from the illustrated position and is held at the cutoff position to form the check valve portion 23. The pressure reducing valve hole 38 communicates with the second load pressure detecting port 46 through the third port 57 and the oil passage 58, and the spool 64 is fitted into the pressure reducing valve hole 38 to connect the first pressure chamber 65 and the second pressure chamber 65. A pressure chamber 66 is formed, the first pressure chamber 65 communicates with the third port 57, the second pressure chamber 66 communicates with the second port 43, and the free piston 68 inserted in the blind hole 67 of the spool 64 and the blind piston 68 are connected to each other. A spring 69 is provided between the free piston 68 and the bottom of the hole 67 so that the free piston 68 abuts on the plug 70, and a push rod 71 integrally provided on the spool 64 projects from the through hole 72 so that the valve 60 is stopped by the stopper rod. 62, and the spool 64 is formed with a fine hole 73 for communicating the first port 42 with the blind hole 67 to form the pressure reducing valve portion 24. The pressure reducing valve portion 74 and the check valve portion 63 are connected to each other. Pressure compensating valve 25.
【０００７】 そして、油圧ポンプ２０の吐出路２１がポンプポート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が接続し、第１、第２アクチュエー タポート３４，３５に第１、第２管路８９，９０を介してアクチュエータ８８が 接続している。 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。The discharge passage 21 of the hydraulic pump 20 communicates with the pump port 39 and the first port 42, the load pressure detection passage 82 is connected to the second port 43, and the first and second actuator ports 34 and 35 are connected. The actuator 88 is connected via the first and second conduits 89 and 90. In FIG. 2, 83 is a swash plate that controls the discharge flow rate of the hydraulic pump 80, 84 is a servo cylinder, and 85 is a directional control valve for pump adjustment.
【０００８】 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８０によってタンク８６から吸上げられた油は、吐出路８１を通っ てチェック弁部６３の開く方向の圧力室ａに案内される。この時、減圧弁部７４ 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７４は、弱いばね６９によって押さ れ杆体７１がチェック弁部６３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２０ｋ ｇ／ｃｍ2 まで上昇し、同時にチェック弁部６３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２２が中立位置Ａのときは、 ポンプ吐出路８１と圧力室６６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 directional control valve 22 is in the neutral position A. The oil sucked up from the tank 86 by the hydraulic pump 80 is guided through the discharge passage 81 to the pressure chamber a in the opening direction of the check valve portion 63. At this time, since the pressure chambers 65 and 66 of the pressure reducing valve portion 74 both communicate with the tank 86, the pressures of the pressure chambers 65 and 66 are both zero, so the pressure reducing valve portion 74 is pressed by the weak spring 69. The rod 71 is only in contact with the check valve portion 63. On the other hand, the pump discharge pressure is kept constant by the spring 87 of the pump adjusting directional control valve 85, which is a differential pressure from the pressure of the load pressure detecting path 82. Now, assuming that this differential pressure is 20 kg / cm 2 , the pressure in the load pressure detection path 82 is zero, so the pump discharge pressure rises to 20 kg / cm 2, and at the same time, the pump discharge pressure enters the pressure chamber a of the check valve 63. After flowing in, the stroke is made until the inlet pressure of the directional control valve 22 (the outlet pressure of the check valve portion 63) becomes equal to the pump discharge pressure, and when they become equal, the weak spring 69 makes a receipt. The pressure reducing valve portion 24 communicates the pump discharge passage 81 with the pressure chamber 66 only at the end of the stroke, while the check valve portion 23 communicates the pump discharge passage 81 with the outlet side before reaching the stroke end. When the control valve 22 is in the neutral position A, the pump discharge passage 81 and the pressure chamber 66 do not communicate with each other, and the pressure in the pressure chamber 65 remains zero.
【０００９】 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８８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６３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７４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７４は、チェック弁部６３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７４の絞りを介して、ポンプ吐出路８ １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６３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８１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８１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６９によって閉じチェック 弁部６３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２２の入口圧と出口圧（＝負荷圧）の間 には、差圧（＝２０ｋｇ／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８８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。When only one of the directional control valves 22 is stroked to the first 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, if the pressure (load pressure) in the conduit 89 connecting the first actuator port 34 and the actuator 88 is higher than the pump discharge pressure (20 kg / cm 2 ), the check valve portion 63 receives the pressure in the pressure chamber b. Therefore, it is possible to prevent the actuator 88 from naturally descending. The pressure in the conduit 89 of the actuator 88, that is, the load pressure, is introduced from the first oil passage 53 and the passage 58 into the pressure chamber 65 of the pressure reducing valve portion 74. Since the pressure in the other pressure chamber 66 is zero, the pressure reducing valve portion 74 strokes in the direction of disengagement from the check valve portion 63 to the stroke end, and through the throttle of the pressure reducing valve portion 74, the pump discharge passage 8 1 And the load pressure detection path 82 communicate with each other. When the pressure (load pressure) in the conduit 89 is larger 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 portion 63, and the pressure is reduced to one side of the pressure reducing valve portion 24. Since the pressure reducing valve portion 24 is guided to the pressure chamber 65, the pressure reducing valve portion 24 remains in a stroke even when the other pressure chamber 66 and the pump discharge passage 81 communicate with each other. On the other hand, when the pressure (load pressure) in the conduit 41 is lower than the pump discharge pressure (= 20 kg / cm 2 ), the load pressure is guided to one pressure chamber 65 of the pressure reducing valve portion 24, and the pressure reducing valve portion 24 is Although the stroke is made by the pressure of one pressure chamber 65, when the pressure of the other pressure chamber 66 rises to the pressure of one pressure chamber 65 (that is, the load pressure), the weak spring 69 closes and abuts against the check valve portion 23. In any case, the pressure reducing valve section 24 makes the pump discharge passage 81 and the pressure chamber 66 communicate with each other until the pressure in one pressure chamber 65 and the pressure in the other pressure chamber 66 become equal to each other. When the pressures in 66 become equal, the weak spring 69 abuts the closing check valve portion 63. As a result, the pressure in the load pressure detection path 82 becomes equal to the load pressure, and the pump discharge pressure is adjusted by the pump adjustment directional control valve 85 by a certain differential pressure (here, 20 kg / cm 2 ). The pressure is controlled to be higher than the pressure in 82. This pump discharge pressure is guided to the input port 44 via the check valve portion 23, that is, between the inlet pressure and the outlet pressure (= load pressure) of the directional control valve 22. 20 kg / cm 2 ) will be maintained. Therefore, the flow rate supplied to the actuator 88 is controlled only by the change in the opening area of the throttle between the inlet side and the outlet side due to the stroke of the directional control valve 22. When the directional control valve 22 is stroked, the conduit 89 or 90 of the actuator 88 and the second oil passage 53 for introducing the load pressure are connected, while the second oil passage 53 is connected to the pressure of one of the pressure reducing valve portions 24. Although it is connected to the chamber 65, the load pressure in the pressure reducing valve section 24 is used only as pilot pressure (set pressure of the pressure reducing valve section), so the pressure is not lost, that is, the directional control valve 22 is When the stroke is made, there is no spontaneous lowering of the actuator 88 due to the release of the load pressure.
【００１０】 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２４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６ ６内の圧力によって減圧弁部２４は、チェック弁部６３を閉じる方向に付勢する 。一方、チェック弁部２３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２ ４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６ ９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 detection path 82 is also connected to the other pressure chamber 66 of the pressure reducing valve portion 24 of the pressure compensating valve 25 disposed in the other directional control valve 22, but the pressure reducing valve portion 24 Since one of the pressure chambers 65 is connected to the tank 86 by the neutral position A of the directional control valve 22, the pressure in the first oil passage 53 for introducing the load pressure is zero, and therefore the pressure chamber 66 is The pressure reducer 24 urges the check valve 63 in the closing direction. On the other hand, since the pump discharge pressure is introduced from the pump discharge passage 81 to the pressure chamber a in the direction in which the check valve portion 23 is opened, as a whole, the difference between the pump discharge pressure and the pressure in the load pressure detection passage 82 ( = 20 kg / cm 2 ), the check valve portion 23 and the pressure reducing valve portion 24 are stroked in the opening direction of the check valve portion 23, but a slight stroke occurs and the pressure of the input port 44 is the differential pressure (= 20 kg / cm 2 ). In this case, the weak spring 69 causes a receipt, and as a result, the pressure reducing valve portion 24 does not stroke to the stroke end, and the hydraulic control on the side of the directional control valve 22 is not affected at all.
【００１１】 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をもとに第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２ ６の負荷圧を１００（ｋｇ／ｃｍ2 ）、右側のアクチュエータ２７の負荷圧を１ ０（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９ ０内の圧力（１０ｋｇ／ｃｍ2 ）まで上昇すると、まず、右方の圧力補償弁２５ 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２２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＝１０ｋｇ／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６３が開いた後、弱いばね６ ９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（２０ｋｇ／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（ ＝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 じてチェック弁部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（１００−１ ０＝９０ｋｇ／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４４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１２０（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（ １２０ｋｇ／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（＝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３０（ｋ ｇ／ｃｍ2 ）（１２０−９０）となる状態で、チェック弁部２３及び減圧弁部２ ４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、１２０ｋｇ／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４ ４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 directional control valves 22 is 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 valve 22 is moved to the first pressure oil supply position B to connect the respective input ports 44, the respective conduits 89, and the respective first oil passages 53 for introducing the load pressure. One of the pressure reducing valve portions 24 has the pressure in the pressure chamber 66 equal to the pressure in the one pressure chamber 65, and the other pressure reducing valve portion 24 has the pressure in the pressure chamber 66 equal to that of the one pressure chamber 65. It continues to stroke to the end of each stroke until it becomes equal to the pressure in 65. Now, assume that the load pressure of the left actuator 88 is larger than the load pressure of the two actuators 88, 88. It is assumed that the load pressure of 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 stroke of the directional control valve. Therefore, each pressure reducing valve section 24 also strokes due to the pressure in the first oil passage 53 for detecting the load pressure, and the pump discharge pressure communicates with the pressure in the pressure detection conduit 34. When the pressure in the load pressure detection path 82 rises to the pressure (10 kg / cm 2 ) in the conduit 90 of the actuator 88 on the right side, which is the low pressure side, first, the pressure reducing valve portion 24 of the pressure compensating valve 25 on the right side closes. . The pressure reducing valve portion 24 of the pressure compensating valve 25 on the left side is still in a stroke, and the pressure in the load pressure detecting path 82 rises until it becomes equal to the pump discharge pressure (20 kg / cm 2 ). At this time, the pressure of the input port 44 of the directional control valve 22 of the left-side actuator 88 on the high pressure side is 100 (kg / cm 2 ), the check valve portion 23 of the pressure compensating valve 25 is closed, and the pressure reducing valve portion 24 Is dissociated from. On the other hand, the pressure reducing valve portion 24 of the pressure compensating valve 25 urges the check valve portion 23 in the closing direction by the difference in pressure between the two pressure chambers 65 and 66 (20-10 = 10 kg / cm 2 ). On the other hand, 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 ), and as a result, the pressure force of the input port 44 of the directional control valve 22 is 10 (kg / Cm 2 ), the check valve portion 63 is opened, and then a receipt is made by the weak spring 69. The pump adjusting directional control valve 85 controls the pump discharge pressure to a pressure higher than the pressure (20 kg / cm 2 ) in the load pressure detection path 82 by a certain pressure difference (20 kg / cm 2 ) (40 kg / cm 2 ). 2 ). Also at this time, the pressure in the load pressure detection path 82 becomes 40 (kg / cm 2 ) while the check valve portion 23 of the high-pressure side pressure compensating valve 25 remains closed and the pressure reducing valve portion 24 remains stroked. The pressure reducing valve portion 24 of the pressure compensating valve 25 on the low pressure side is closed in the direction in which the check valve portion 23 is closed due to the pressure difference (= 30 kg / cm 2 ) in the load pressure detecting passage 82 and the first oil passage 53 for introducing the load pressure. It is energized so that the pressure at the input port 44 of the directional control valve 22 remains at 10 kg / cm 2 . In this way, the pressure in the load pressure detection path 82 and the pump discharge pressure continue to rise, and when the pump discharge pressure eventually becomes equal to the load pressure (100 kg / cm 2 ) of the high pressure side actuator 88, the high pressure side The pressures in the two pressure chambers 65 and 66 of the pressure reducing valve portion 23 of the pressure compensating valve 25 are both 100 kg / cm 2 and are closed by the weak spring 69 to contact the check valve portion 23. At this time, the pressure reducing valve portion 24 of the pressure compensating valve 25 on the low pressure side has a check valve portion due to a pressure difference (100-10 = 90 kg / cm 2 ) in the load pressure detecting passage 82 and the first oil passage 53 for introducing the load pressure. 23 is urged in the closing direction, and as a result, the pressure of the input port 44 of the directional control valve 22 on the low pressure side remains 10 kg / cm 2 . Again, the pump adjusting directional control valve 85 controls the pump discharge pressure to 120 (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 due to the pressure difference between the two pressure chambers a and b of the check valve portion 23. For the first time, the check valve portion 23 is opened, and the pump discharge pressure (120 kg / cm 2 ) is guided to the input port 44 of the directional control valve 22. On the other hand, the pressure reducing valve portion 24 of the pressure compensating valve 25 on the low pressure side closes the check valve portion 23 by the pressure difference (= 90 kg / cm 2 ) in the load pressure detecting passage 82 and the first oil passage 53 for introducing the load pressure. However, since the pressure in the pressure chamber a in the opening direction of the check valve portion 23 became 120 (kg / cm 2 ), the pressure at the inlet port 44 of the directional control valve 22 was 30 (kg / cm 2 ). cm 2 ) (120-90), the check valve portion 23 and the pressure reducing valve portion 24 are pressure balanced. That is, the check valve portion 23 and the pressure reducing valve portion 24 make a slight stroke, and the check valve portion 23 is in a state of being squeezed to be 120 kg / cm 2 to 30 kg / cm 2 . For the first time, this hydraulic control system is balanced so that the pressure of the input port 44 of the high-pressure side directional control valve 22 is 120 kg / cm 2 and the pressure of the input port 44 of the low-pressure side directional control valve 22 is 30 kg / cm 2. 2 , that is, the difference between the inlet pressure and the outlet pressure (load pressure) of the two directional control valves 22 and 22 is maintained at 20 kg / cm 2 , so that the two directional control valves 22 and 22 are In both cases, the flow rate supplied to the actuators 88, 88 can be controlled only by the stroke amount.
【００１２】 −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８ ０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１ ００１／ｍｉｎ以上のときは、前述の通り、方向制御弁５５，５５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の最大吐出量が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／ｃ ｍ2 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、２０ｋ ｇ／ｃｍ2 から下がる。いま、差圧が１４ｋｇ／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／ｃｍ2 、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２ ０ｋｇ／ｃｍ2 から１４ｋｇ／ｃｍ2 （２４−１０）に減少する。方向制御弁２ ２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８８，８８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。-The total flow rate required for each actuator 88, 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 actuator 88, 88 left actuator 88 is 100kg / cm 2, 501 / min , the right actuator 88 and 10kg / cm 2, 501 / min . When the maximum discharge flow rate of the hydraulic pump 80 is 1001 / min or more, the difference between the inlet pressure and the outlet pressure of the directional control valves 55, 55 is kept constant (= 20 kg / cm 2 ) as described above. , The flow rate can be controlled by the stroke, and the flow rate can be distributed by 501 / min. Next, assume that the maximum discharge amount of the hydraulic pump 80 becomes 701 / min. Since the inlet pressure of the two directional control valves 22 and 22 are described above 120kg / cm 2, 30kg / c m 2, flow to the high pressure side of the directional control valve 22 is reduced to 201 / min from 501 / min. The flow rate to the low-pressure side directional control valve 22 remains at 501 / min. Assuming that 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 directional control valve 22 on the high pressure side is reduced by 20 kg / cm 2 due to the decrease in the flow rate. Go down. Now, assume that the differential pressure is 14 kg / cm 2 , that is, the inlet pressure is reduced from 120 kg / cm 2 to 114 (100 + 14) kg / cm 2 . At this time, the pressures of 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 , and therefore the pressure reducing valve portion 24 is checked by the weak spring 69. If the pressure inside the pressure chamber b in the closing direction of the check valve portion 23 decreases from 120 kg / cm 2 to 114 kg / cm 2 , the check valve portion 23 remains open (stroke end). ), the direction of the pressure in the pressure chamber a to open the check valve unit 23, i.e., the pump discharge pressure is reduced to 120 kg / cm 2 or et 114 kg / cm 2. At this time (when the pump discharge flow rate is insufficient), the pump discharge pressure is not controlled by the pump adjustment directional control valve 85. On the other hand, the two pressure chambers 65 and 66 of the pressure reducing valve portion 24 of the pressure compensating valve 25 on the low pressure side remain 100 kg / cm 2 and 10 kg / cm 2 , and the differential pressure of 90 kg / cm 2 causes the check valve portion 63 to be Continue to push 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, that is, the pump discharge pressure is reduced to 114 kg / cm 2 , the pressure in the pressure chamber b in the closing direction of the check valve portion 23 is 30 kg / cm 2. The check valve portion 23 and the pressure reducing valve portion 24 balance the pressure in the state where the pressure is reduced from 2 to 24 kg / cm 2 . Therefore, the differential pressure between the inlet pressure and the outlet pressure of the directional control valve 22 on the low pressure side is reduced from 20 kg / cm 2 to 14 kg / cm 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 from 201 / min. That is, in the state where the differential pressure between the inlet pressure and the outlet pressure of the directional control valves 22 and 22 is equal, and the supply amounts to the two actuators 88, 88 are both divided into 351 / min, the hydraulic control system is controlled. Balance.
【００１３】 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 the number of actuators loaded by one hydraulic pump 80 is three or more. Even when there are three or more actuators, a pressure compensating valve 25 having the same check valve section 23 and pressure reducing valve section 24 is disposed between the directional control valve and the hydraulic pump, and the pressure compensating valve 25 in the closing direction of each pressure reducing valve section is arranged. Even if the number of actuators is three or more, the operation according to the above-described operation principle can be realized by simply communicating all the pressure differences through the load pressure detection path 82.
【００１４】 以上述べた様な圧油供給装置においては負荷圧の変動に対応してポンプ吐出圧 が直ちに変動するので、アクチュエータ８８でパワーショベルの上部車体などの 慣性体を駆動する場合に、慣性体を急加速する時には負荷圧が高圧となりポンプ 吐出圧が高圧となるが、次に慣性体が動き出すとその慣性力により負荷圧が低圧 で動くためポンプ吐出圧が降圧する現象がおき、いわゆるハンチングを生じるか らスムーズな慣性体の制御が行なえない。In the pressure oil supply device as described above, the pump discharge pressure fluctuates immediately in response to fluctuations in the load pressure. Therefore, when the actuator 88 drives an inertial body such as the upper vehicle body of a power shovel, When the body accelerates rapidly, the load pressure becomes high and the pump discharge pressure becomes high.However, when the inertial body moves next, the load pressure moves at a low pressure due to the inertial force, so the pump discharge pressure decreases, which is called hunting. As a result, the inertial body cannot be controlled smoothly.
【００１５】 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.
【００１６】[0016]
主スプール４９に第１・第２アクチュエータポート３４，３５を第１・第２タ ンクポート４７，４８に連通する第１・第２絞り１００，１０１を形成して成る 圧油供給装置。 A pressure oil supply device in which main spool 49 is formed with first and second throttles 100 and 101 that connect the first and second actuator ports 34 and 35 to the first and second tank ports 47 and 48.
【００１７】[0017]
第１・第２アクチュエータ３４，３５の圧油を第１・第２タンクポート４７， ４８にブリードオフして圧力上昇を緩かにする。 The pressure oil of the first and second actuators 34 and 35 is bleed off to the first and second tank ports 47 and 48 to moderate the pressure increase.
【００１８】[0018]
図４に示すように、方向制御弁２２の主スプール４９における第１・第２小径 部５０，５１と連続した第１・第２絞り１００，１０１を形成して第１アクチュ エータポート３４から第１タンクポート４７又は第２アクチュエータポート３５ から第２タンクポート４８に高圧油の一部が流出（ブリードオフ）するようにす る。 これによって、第１又は第２アクチュエータポート３４，３５の圧力上昇が緩 かになってハンチングのないスムーズな慣性体の制御ができる。 As shown in FIG. 4, first and second throttles 100 and 101, which are continuous with the first and second small diameter portions 50 and 51 of the main spool 49 of the directional control valve 22, are formed to form the first actuator port 34 and the first throttle port 100. A part of the high pressure oil flows out (bleeds off) from the first tank port 47 or the second actuator port 35 to the second tank port 48. As a result, the pressure rise in the first or second actuator port 34, 35 is moderated, and a smooth inertial body control without hunting can be performed.
【００１９】 図５、図６に示すように、第２負荷圧検出ポート４６を第２タンクポート４８ に連通する油路５４の径方向の孔５４ａの径を大きくして前述と同様にブリード オフの機能を追加するようにしても良い。As shown in FIGS. 5 and 6, the diameter of the hole 54 a in the radial direction of the oil passage 54 that communicates the second load pressure detection port 46 with the second tank port 48 is increased to bleed off as described above. The function of may be added.
【００２０】[0020]
第１又は第２アクチュエータポート３４，３５の圧油の一部をブリードオフし て圧力上昇を緩かにできるから慣性体をハンチングなしにスムーズに動作制御で きる。 Since a part of the pressure oil in the first or second actuator port 34, 35 can be bleed off to moderate the pressure rise, the inertial body can be smoothly operated and controlled without hunting.
【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 previously applied.
【図３】その弁ブロックに主スプール、スプールを組み
こんだ断面図である。FIG. 3 is a cross-sectional view in which a main spool and a spool are assembled in the 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 cross-sectional view showing a state in which a main spool and a spool are incorporated in a valve block showing an embodiment of the present invention.
【図５】第２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. 5 is a sectional view of a valve block showing a second embodiment in which a main spool and a spool are incorporated.
【図６】図５の−断面図である。FIG. 6 is a − sectional view of FIG. 5;
２２…方向制御弁、２３…チェック弁、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、４８…第２タンクポート、４９…主ス
プール、５４…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、８０…油圧ポンプ、８１…ポ
ンプ吐出路、８２…負荷圧検出路、１００…第１絞り、
１０１…第２絞り。22 ... Direction control valve, 23 ... Check valve, 24 ... Pressure reducing valve section, 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 ... 2nd port, 44 ... Input port, 45 ... 1st load pressure detection port, 46 ... 2nd load pressure detection port, 47 ... 1st tank port, 48 ... 2nd tank port, 49 ... Main spool, 54 ... Oil passage, 56 ... Oil hole, 58 ... Oil hole, 60 ...
Spool, 64 ... Spool, 65 ... First pressure chamber, 66 ...
Second pressure chamber, 69 ... Spring, 80 ... Hydraulic pump, 81 ... Pump discharge passage, 82 ... Load pressure detection passage, 100 ... First throttle,
101 ... Second diaphragm.
Claims (2)
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、 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７５とし、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、 前記主スプール４９に第１アクチュエータポート３４と
第１タンクポート４７を連通する第１絞り１００及び第
２アクチュエータポート３５と第２タンクポート４８を
連通する第２絞り１０１を形成して成る圧油供給装置。1. A spool hole 31, a check valve hole 37 and a pressure reducing valve hole 38 are formed in a valve block 30, and an input port 4 opened in the spool hole 31 is formed in the valve block 30.
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.
The main spool 49 for connecting / disconnecting each port is fitted into 1 to form the direction control valve 22, and the valve block 30 has the pump port 39 and the check valve hole 37 opened in the check valve hole 37 in the input port 44. An oil passage 56 is formed to communicate with the check valve hole 37, and the pump port 39 and the oil passage 56 are connected to and cut off from the check valve hole 37, and a spool 60 that is stopped at the cut position is inserted to form the check valve portion 23. The block 30 has a first opening that opens to the pressure reducing valve hole 38.
The second port 42, 43 is formed, and the pressure reducing valve hole 38 is formed.
The first pressure chamber 65 and the second pressure chamber 66 are formed by inserting the 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. And the spool 64 of the check valve portion 23 is pressed and held in the shut-off position to form a pressure reducing valve portion 24. The pressure reducing valve portion 24 and the check valve portion 24 are connected to each other. 23 as a pressure compensation valve 75, the pump first ports 39 and 42 are connected to the discharge passage 21 of the hydraulic pump 20, the second port 43 is connected to a load pressure detection passage 82, and the main spool 49 is connected to the first actuator. A pressure oil supply device formed by forming a first throttle 100 that communicates the port 34 and the first tank port 47 and a second throttle 101 that communicates the second actuator port 35 and the second tank port 48.
検出ポート４５，４６をタンクポートに連通する油路５
４を形成して成る請求項１記載の圧油供給装置。2. An oil passage 5 connecting the first and second load pressure detection ports 45 and 46 to the tank port on the main spool 49.
4. The pressure oil supply device according to claim 1, which is formed by forming 4.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP1992046777U JP2577675Y2 (en) | 1992-06-12 | 1992-06-12 | Pressure oil supply device |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP1992046777U JP2577675Y2 (en) | 1992-06-12 | 1992-06-12 | Pressure oil supply device |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| JPH061801U true JPH061801U (en) | 1994-01-14 |
| JP2577675Y2 JP2577675Y2 (en) | 1998-07-30 |
Family
ID=12756766
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP1992046777U Expired - Lifetime JP2577675Y2 (en) | 1992-06-12 | 1992-06-12 | Pressure oil supply device |
Country Status (1)
| Country | Link |
|---|---|
| JP (1) | JP2577675Y2 (en) |
Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPS5145077U (en) * | 1974-09-30 | 1976-04-02 |
Citations (3)
| 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 |
| JPH02134401A (en) * | 1988-11-10 | 1990-05-23 | Diesel Kiki Co Ltd | Hydraulic control unit |
| JPH02247801A (en) * | 1989-03-20 | 1990-10-03 | Matsushita Electric Ind Co Ltd | Magnetic recording and reproducing device |
-
1992
- 1992-06-12 JP JP1992046777U patent/JP2577675Y2/en not_active Expired - Lifetime
Patent Citations (3)
| 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 |
| JPH02134401A (en) * | 1988-11-10 | 1990-05-23 | Diesel Kiki Co Ltd | Hydraulic control unit |
| JPH02247801A (en) * | 1989-03-20 | 1990-10-03 | Matsushita Electric Ind Co Ltd | Magnetic recording and reproducing device |
Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPS5145077U (en) * | 1974-09-30 | 1976-04-02 |
Also Published As
| Publication number | Publication date |
|---|---|
| JP2577675Y2 (en) | 1998-07-30 |
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