JP3119317B2 - Pressure oil supply device - Google Patents
Pressure oil supply deviceInfo
- Publication number
- JP3119317B2 JP3119317B2 JP04161925A JP16192592A JP3119317B2 JP 3119317 B2 JP3119317 B2 JP 3119317B2 JP 04161925 A JP04161925 A JP 04161925A JP 16192592 A JP16192592 A JP 16192592A JP 3119317 B2 JP3119317 B2 JP 3119317B2
- Authority
- JP
- Japan
- Prior art keywords
- pressure
- port
- valve
- check valve
- spool
- 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
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Description
【０００１】[0001]
【産業上の利用分野】本発明は、１つ又は複数の油圧ポ
ンプの吐出油を複数のアクチュエータ、特に左右走行用
油圧モ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 discharge oil from one or more hydraulic pumps to a plurality of actuators, in particular, a left-right traveling hydraulic motor.
【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に開口した第１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２、第３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第１・
第２・第３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 first port 39 opened in the check valve hole 37 is formed in the front and rear surfaces, and a second and third port 42 opened in the pressure reducing valve hole 38. , 43 are formed to be open at the front and rear surfaces.
The second and third ports 39, 42, 43 communicate with each other.
【０００６】前記弁ブロック３０にはスプール孔３１に
開口したポンプポート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でポンプポート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４
５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でポンプポート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 a pump 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 at the second small diameter portion 51, the pump port 44 communicates with the second load pressure detection port 46 at the communication groove 52, and the first small diameter portion 50. And the first actuator Over door 34 is the first load pressure detection port 4
5 and the second load pressure detection port 46 and the second tank port 48 are shut off to the first pressure oil supply position. When the spool 49 is slid to the left, the first actuator port 34 is formed by the first small diameter portion 50. To the first tank port 47, the communication port 52 connects the pump port 44 to the first load pressure detection port 45, and the second small-diameter portion 51 connects the second actuator port 35 to the second load pressure detection port 46. Communication,
And the second load pressure detection port 46 and the second tank port 48
Is a second pressure oil supply position at which the directional control valve 22 is shut off.
【０００７】前記チェック弁用孔３７は油路５６でポン
プポート４４に開口し、そのチェック弁用孔３７には前
記第１ポート３９とポンプポート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４ポート５７と油路５
８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４ポート
５７に連通し、第２圧力室６６は第３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２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 to the pump port 44 through an oil passage 56, and a valve 60 for shutting off the communication between the first port 39 and the pump port 44 is inserted into the check valve hole 37. 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 illustrated position, 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 fourth port 57 and the oil passage 5.
At 8, it communicates with the second load 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. The second pressure chamber 66 communicates with the fourth port 57, the second pressure chamber 66 communicates with the third 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. The piston 68 contacts the plug 70, and the push rod 71 integrally provided on the spool 64 projects from the through hole 72 to contact the valve 60 with the stopper rod 62. The pressure reducing valve portion 24 is formed by forming a fine hole 73 communicating with the blind hole 67, and the pressure compensating valve 25 is formed by the pressure reducing valve portion 24 and the check valve portion 23.
【０００８】そして、図２に示すように油圧ポンプ２０
の吐出路２１を第１ポート３９、第２ポート４２に連通
し、第３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２０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 first port 39 and the second port 42, and the load pressure detection path 82 is connected to the third port 43.
-The actuator 88 is connected to the second actuator ports 34 and 35. In FIG. 2, 83 is a hydraulic pump.
A swash plate for controlling the discharge flow rate of the pump 20, a servo cylinder 84, and a pump adjusting direction control valve 85.
【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２１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２１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２１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 direction control valve 22 is in the neutral position A. The oil sucked from the tank 86 by the hydraulic pump 20 is guided to the pressure chamber a in the opening direction of the check valve portion 23 through the discharge path 21. At this time, since the pressure chambers 65 and 66 of the pressure reducing valve section 24 both communicate with the tank 86, the pressure chambers 65 and 66
Are zero, so that the pressure reducing valve portion 24 is only pushed by the weak spring 69 and the rod 71 is in contact with the check valve portion 23. 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 pressure in the load pressure detecting path 82 is zero, so the pump discharge pressure rises to 20 kg / cm 2, and at the same time, the pump discharge pressure flows into the pressure chamber a of the check valve portion 23. Then, the stroke is performed 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. Pressure reducing valve 24, when the stroke end only, Pong
While the discharge passage 21 communicates with the pressure chamber 66, the check valve section 23 stops the pump discharge before reaching the stroke end.
Since the outlet 21 communicates with the outlet side, when the direction control valve 22 is at the neutral position A, the pump discharge passage 21 does not communicate with the pressure chamber 66, 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をストロークさせポンプポート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
チュエータポート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８９内の圧力（負荷圧）がポンプ吐出圧（＝２０ｋ
ｇ／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２
４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６
６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／ｃ
ｍ2 ）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、ポンプポート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。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 direction control valve 22 is moved to connect the pump port 44 and the first actuator port 34, and at the same time, the second
The tutor port 35 and the second tank port 48 are connected. At this time, when 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 23 receives the pressure in the pressure chamber b. , The natural descent of the actuator 88 can be prevented.
The pressure of the conduit 89 of the actuator 88, that is, the load pressure, is guided from the first oil passage 53 and the passage 58 to one pressure chamber 65 of the pressure reducing valve section 24. 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 is dissociated from the check valve portion 23, and communicates with the pump discharge passage 21 through the throttle of the pressure reducing valve portion 24. The pressure detection path 82 communicates. 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 89 is the pump discharge pressure (= 20k)
g / cm 2 ), the load pressure is guided to one pressure chamber 65 of the pressure reducing valve section 24, and the pressure reducing valve section 24 strokes with the pressure of the one pressure chamber 65, but the other pressure chamber 66. When the pressure rises to the pressure in one pressure chamber 65 (that is, the load pressure), it is closed by a weak spring 69 and abuts against the check valve portion 23. In any case, the pressure reducing valve section 2
4 until the pressure in one pressure chamber 65 and the pressure in the other pressure chamber 66 are equal.
When the pressures in the two pressure chambers 65 and 66 become equal, the spring 6 is closed by a weak spring 69 and abuts on the check valve portion 23. 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 direction control valve 85 to a certain differential pressure (here, 20 kg / c).
The pressure is controlled to be higher than the pressure in the load pressure detecting path 82 by m 2 ). The pump discharge pressure is controlled by the check valve unit 23.
, The differential pressure (= 20 kg / cm 2 ) is maintained between the inlet pressure and the outlet pressure (= load pressure) of the directional control valve 22. become. Therefore, the flow rate supplied to the actuator 88 is controlled only by a change in the opening area of the throttle between the inlet side and the outlet side according to the stroke of the direction control valve 22. When the directional control valve 22 is to be stroked, the conduit 89 or 90 of the actuator 88 and the second
The oil passage 53 is connected, while the second oil passage 53 is connected to one pressure chamber 65 of the pressure reducing valve portion 24. In the pressure reducing valve portion 24, the load pressure is equal to the pilot pressure (set of the pressure reducing valve portion). Pressure), so that the pressure is not released. That is, when the directional control valve 22 is stroked, the load 88 is released.
There is no natural descent.
【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２３の開く
方向の圧力室ａには、ポンプ吐出路２１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
ロークしポンプポート４４の圧力がその差圧（＝２０ｋ
ｇ／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 21 to the pressure chamber a in the opening direction of the check valve portion 23, the differential pressure (== the pressure difference between the pump discharge pressure and the pressure in the load pressure detection passage 82) as a whole. 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 the stroke is slightly increased and the pressure of the pump port 44 becomes the differential pressure (= 20 k).
g / 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 does not affect the hydraulic control of the direction control valve 22 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、各ポンプポート
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８８の負荷圧を１００
（ｋｇ／ｃｍ2 ）、右側のアクチュエータ８８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のポンプポート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６
５と６６内の圧力の差（２０−１０＝１０ｋｇ／ｃ
ｍ2 ）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のポンプポート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／ｃ
ｍ2 ）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（４
０ｋｇ／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（ｋ
ｇ／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のポンプポート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／ｃ
ｍ2）と等しくなると、高圧側の圧力補償弁２５の減圧
弁部２４の二つの圧力室６５と６６内の圧力はともに１
００ｋｇ／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＝９０ｋ
ｇ／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のポンプポート
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１
２０（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（１
２０ｋｇ／ｃｍ2 ）が方向制御弁２２のポンプポート４
４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５
３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／ｃ
ｍ2 ）になったので方向制御弁２２の入口ポート４４の
圧力が３０（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、
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のポンプポート４
４の圧力が１２０ｋｇ／ｃｍ2 、低圧側の方向制御弁２
２のポンプポート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 both the directional control valves 22 are stroked to the first pressure oil supply position B, and the respective pump ports 44, the respective conduits 89, and the respective first hydraulic passages 53 for guiding the load pressure are connected. One of the pressure reducing valves 24 operates 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 24 operates to reduce the pressure in the pressure chamber 66 to one of the pressure chambers 65. , Respectively, until they equal the internal pressure.
Now, it is assumed that the load pressure of the left actuator 88 among the load pressures of the two actuators 88, 88 is larger. Assuming that the load pressure of the left actuator 88 is 100
(Kg / cm 2 ), and the load pressure of the right actuator 88 is 10 (kg / cm 2 ). The load pressure detection path 82
Since it 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. When the pressure in the load pressure detection path 82 rises to the pressure (10 kg / cm 2 ) in the conduit 90 of the right actuator 88 on the low pressure side, first, the pressure reducing valve section 24 of the right pressure compensating valve 25.
Closes. 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 left actuator 88 on the high pressure side
Pressure of the pump port 44 of the directional control valve 22 is 100
(Kg / cm 2 ), and the check valve portion 23 of the pressure compensating valve 25 is closed and dissociated from the pressure reducing valve portion 24.
On the other hand, the pressure reducing valve portion 24 of the pressure compensating valve 25 is provided with two pressure chambers 6.
Pressure difference between 5 and 66 (20-10 = 10kg / c
At m 2 ), the check valve 23 is urged in the closing direction. On the other hand, since the pressure (pump discharge pressure) in the pressure chamber a in the opening direction of the check valve portion 23 is 20 (kg / cm 2 ),
As a result, the check valve 23 is opened until the pressure of the pump port 44 of the direction control valve 22 becomes 10 (kg / cm 2 ), and then the receipt is performed by the weak spring 69. By the pump control directional control valve 85, a certain differential pressure (20 kg / c
m 2 ), the pressure in the load pressure detection path 82 (20 kg /
cm 2 ), the pump discharge pressure is controlled to a pressure higher than
0 kg / cm 2 ). Also at this time, the high pressure side pressure compensating valve 25
The pressure in the load pressure detection path 82 is 40 (k) while the check valve section 23 is closed and the pressure reducing valve section 24 is stroked.
g / cm 2 ). On the other hand, the pressure reducing valve portion 24 of the pressure compensating valve 25 on the low pressure side has 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. Urges the check valve portion 23 in the closing direction, and as a result, the pressure of the pump port 44 of the directional control valve 22 remains at 10 kg / cm 2 . In this manner, 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 / c) of the high-pressure side actuator 88.
m 2 ), the pressure of the high-pressure side pressure compensating valve 25 is reduced.
The pressure in the two pressure chambers 65 and 66 of the valve portion 24 is 1
It becomes 00 kg / cm 2 and comes into contact with the close check valve portion 23 by the weak spring 69. 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 k) between the load pressure detecting path 82 and the first oil path 53 for introducing the load pressure.
g / cm 2 ) to urge the check valve portion 23 in the closing direction. As a result, the pressure at the pump port 44 of the directional control valve 22 on the low pressure side remains at 10 kg / cm 2 . Again, the pump discharge pressure becomes 1 by the pump adjustment direction control valve 85.
It is controlled at 20 (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 (1
20 kg / cm 2 ) is the pump port 4 of the directional control valve 22.
It is led to 4. On the other hand, the pressure reducing valve section 24 of the pressure compensating valve 25 on the low pressure side is connected to the load pressure detecting path 82 and the first oil path 5 for introducing the load pressure.
3, the check valve portion 23 is continuously urged in the closing direction by the pressure difference (= 90 kg / cm 2 ).
The pressure in the pressure chamber a in the opening direction is 120 (kg / c).
m 2 ), the check valve section 23 and the pressure reducing valve section 24 are pressure-balanced with the pressure at the inlet port 44 of the directional control valve 22 being 30 (kg / cm 2 ) (120-90). That is, the check valve section 23 and the pressure reducing valve section 24
Strokes slightly, and at the check valve portion 23,
It is in a state of being squeezed so as to be 120 kg / cm 2 to 30 kg / cm 2 . For the first time, the hydraulic control system is balanced and the pump port 4 of the directional control valve 22 on the high pressure side is
4 is 120 kg / cm 2 , low pressure side directional control valve 2
2 is 30 kg / cm 2 , that is, the difference between the inlet pressure and the outlet pressure (load pressure) of the two directional control valves 22 is maintained at 20 kg / cm 2 . The two directional control valves 22 can control the flow rate supplied to the actuators 88 only by the stroke.
【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２０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２０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２０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／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２３を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 total flow rate required for each of the actuators 88, 88 is equal to or greater than the maximum discharge flow rate of the hydraulic pump 20 . 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. Hydraulic pon
When the maximum discharge flow rate of the pump 20 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, the hydraulic pump 20
It is assumed that the maximum discharge amount has reached 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
In cm 2 , the check valve portion 23 is continuously urged in the closing direction . 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２０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 20 . 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]
【発明が解決しようとする課題】かかる圧油供給装置で
あると、方向切換弁２２の主スプール４９のストローク
による第１・第２負荷圧検出ポート４５，４６と第１・
第２アクチュエータポート３４，３５の開口面積に比例
した流量がアクチュエータ８８の負荷圧に関係なく第１
・第２アクチュエータポート３４，３５に供給される。
このために、油圧駆動車両の左右走行用油圧モータに圧
油を供給する場合に、左右の方向制御弁２２，２２の開
口面積が加工誤差により異なると左右走行用油圧モータ
に供給される流量が異なって直進走行せずに旋回走行し
てしまう。With such a pressure oil supply device, the first and second load pressure detection ports 45 and 46 and the first and second load pressure detection ports 45 and 46 based on the stroke of the main spool 49 of the direction switching valve 22 are provided.
The flow rate proportional to the opening area of the second actuator ports 34 and 35 is the first flow rate regardless of the load pressure of the actuator 88.
-It is supplied to the second actuator ports 34, 35.
For this reason, when supplying the pressure oil to the left and right traveling hydraulic motors of the hydraulically driven vehicle, if the opening areas of the left and right directional control valves 22 are different due to processing errors, the flow rate supplied to the left and right traveling hydraulic motors is reduced. The driver turns around instead of straight ahead.
【００１６】そこで、本発明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。Accordingly, 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】減圧弁部２４のスプール
６４を第１圧力室６５内の圧力でバネ６９に抗して摺動
した時に第１圧力室６５と第２ポート４２を連通する形
状とし、一対の弁ブロック３０，３０の第１ポート３９
に油圧ポンプ２０の吐出路２１を接続し、第２ポート４
２相互を連通し、第３ポート４３を負荷圧検出路８２に
それぞれ接続した圧油供給装置。When the spool 64 of the pressure reducing valve section 24 slides against the spring 69 with the pressure in the first pressure chamber 65, the first pressure chamber 65 and the second port 42 are communicated. And the first port 39 of the pair of valve blocks 30, 30.
Is connected to the discharge path 21 of the hydraulic pump 20 and the second port 4
2. A pressure oil supply device that communicates with each other and connects the third port 43 to the load pressure detection path 82, respectively.
【００１８】[0018]
【作 用】一対の弁ブロック３０，３０の方向制御弁
２２，２２の各主スプール４９を同時に同一方向に摺動
して各第１又は第２アクチュエータポート３４，３５に
油圧ポンプ２０の吐出圧油を供給した時に各減圧弁部２
４のスプール６４が第１圧力室６５内の圧力でバネ６９
に抗する方向に押されて第１圧力室６５と第２ポート４
２が連通するから、左右の弁ブロック３０，３０の第２
ポート４２の圧力が同一となり、左右の弁ブロック３
０，３０の方向制御弁２２，２２の開口面積が加工誤差
等により異なっても左右のアクチュエータ８８に同一流
量の圧油を供給できる。The main pump 49 of the directional control valve 22, 22 of the pair of valve blocks 30, 30 is simultaneously slid in the same direction so that the discharge pressure of the hydraulic pump 20 is applied to each of the first or second actuator ports 34, 35. When oil is supplied, each pressure reducing valve section 2
The spool 64 of the fourth device is moved by the pressure in the first pressure chamber 65 to the spring 69.
The first pressure chamber 65 and the second port 4
2 communicate with each other, the second of the left and right valve blocks 30
The pressure of the port 42 becomes the same, and the left and right valve blocks 3
Even if the opening areas of the directional control valves 22 and 22 of 0 and 30 are different due to processing errors and the like, the same flow is applied to the left and right actuators 88.
Can supply a quantity of pressurized oil .
【００１９】[0019]
【実 施 例】本発明の実施例を図４以降を参照して説
明する。なお、従来と同一部材は符号を同一とする。主
スプール４９にはポンプポート４４と第１・第２負荷圧
検出ポート４５，４６を連通・遮断する中間小径部１２
０が形成してある。減圧弁部２４の第３ポート４３と第
２圧力室６６をスプール６４で遮断し、第３ポート４３
と第２ポート４２を連通・遮断するスリット状の開口１
００をスプール６４の外周面に形成し、第３ポート４３
に負荷圧検出路８２を接続する。スプール６４の盲穴６
７を段付形状とし、シート６８を盲穴６８ａと環状凹部
６８ｂを有する形状とし、そのシート６８を盲穴６７の
外向段部６７ａに当接して固定し、そのシート６８とプ
ラグ７０との間にバネ６９を設け、前記シート６８の盲
穴６８ａ開口周縁にチェック弁１０１をバネ１０２で押
しつけて盲穴６８ａとチェック弁１０１との間に圧力室
１０３を構成し、その圧力室１０３を第１絞り１０４で
第２圧力室６６に連通し、かつ第２絞り１０５で環状凹
部６８ｂに連通し、その環状凹部６８ｂをスプール６４
の絞り１０６で第３ポート４３に開口し、チェック弁１
０１のバネ室１０７を絞り１０８で第２ポート４２に開
口する。前記第１圧力室６５をスプール６４の切欠部１
０９と細孔１１０でフリーピストン６８とチェック弁１
０１との間に連通してある。Embodiment An embodiment of the present invention will be described with reference to FIG. The same members as those in the related art have the same reference numerals. The main spool 49 has an intermediate small-diameter portion 12 that communicates and shuts off the pump port 44 and the first and second load pressure detection ports 45 and 46.
0 is formed. The third port 43 of the pressure reducing valve section 24 and the second pressure chamber 66 are shut off by the spool 64 and the third port 43
Slit-shaped opening 1 for communicating and blocking between the first port 42 and the second port 42
00 is formed on the outer peripheral surface of the spool 64 and the third port 43
Is connected to the load pressure detecting path 82. Blind hole 6 of spool 64
7 has a stepped shape, the sheet 68 has a shape having a blind hole 68a and an annular concave portion 68b, and the sheet 68 abuts on the outward stepped portion 67a of the blind hole 67 and is fixed. A check valve 101 is pressed against the periphery of the opening of the blind hole 68a of the seat 68 by a spring 102 to form a pressure chamber 103 between the blind hole 68a and the check valve 101. The throttle 104 communicates with the second pressure chamber 66, and the second throttle 105 communicates with the annular recess 68b.
Of the check valve 1
The spring chamber 107 of No. 01 is opened to the second port 42 by the throttle 108. The first pressure chamber 65 is inserted into the notch 1 of the spool 64.
09 and free piston 68 and check valve 1 with small hole 110
01.
【００２０】図５に示すように左右の弁ブロック３０，
３０の減圧弁部２４，２４における第２ポート４２相互
を通路１１１で連通してあり、この左右の弁ブロック３
０の第１・第２アクチュエータポート３４，３５に連通
したアクチュエータ８８は左右の走行用油圧モータとな
っていると共に、油圧ポンプ２０の吐出路２１は左右の
弁ブロック３０の第１ポート３９にそれぞれ接続してい
る。As shown in FIG. 5, the left and right valve blocks 30,
The second ports 42 of the pressure-reducing valve portions 24, 24 are connected to each other by a passage 111.
The actuator 88 communicating with the first and second actuator ports 34 and 35 is a left and right traveling hydraulic motor, and the discharge path 21 of the hydraulic pump 20 is connected to the first port 39 of the left and right valve blocks 30 respectively. Connected.
【００２１】次に作動を説明する。直進走行時。図４に
示すように左右の弁ブロック３０の方向制御弁２２の主
スプール４９を左方に移動させると、油圧ポンプ２０の
吐出圧油は第１ポート３９，ポンプポート４４、中間小
径部１２０、左側切欠部１２１、第１負荷圧検出ポート
４５、連通路１２２、第２負荷圧検出ポート４６、左側
切欠き１２３、第２小径部５１、第２アクチュエータポ
ート３５よりアクチュエータ８８の一方のポート８８ａ
に流入し、その他方のポート８８ｂからの戻り油は第１
アクチュエータポート３４、第１小径部５０、左側切欠
き１２４より第１タンクポート４７に流出する。アクチ
ュエータ８８の負荷圧は第２アクチュエータポート３
５、第２負荷圧検出ポート４６、通路５８より第１圧力
室６５に作用してスプール６４を右方に押圧してストロ
ークさせる。この時、第２ポート４２の圧力はスプール
６４の絞り１０８でチェック弁１０１のバネ室１０７に
導入されてチェック弁１０１の左側面に作用する。他
方、チェック弁１０１とシート６８の盲穴６８ａとの間
の圧力室１０３にはスプール６４の絞り１０６、環状凹
部６８ｂ、シート６８の第２絞り１０５より第３ポート
４３の圧力が流入してチェック弁１０１の右側面に作用
する。そして、前記第２ポート４２の圧力と第３ポート
４３の圧力はほぼ同一であるからチェック弁１０１はバ
ネ１０２でシート６８に押しつけ保持される。Next, the operation will be described. When traveling straight. As shown in FIG. 4, when the main spool 49 of the directional control valve 22 of the left and right valve blocks 30 is moved to the left, the discharge pressure oil of the hydraulic pump 20 is discharged from the first port 39, the pump port 44 , the intermediate small diameter section 120, One port 88a of the actuator 88 from the left notch 121, the first load pressure detection port 45, the communication passage 122, the second load pressure detection port 46, the left notch 123, the second small diameter portion 51, and the second actuator port 35.
Return oil from the other port 88b
The fluid flows out from the actuator port 34, the first small diameter portion 50 , and the left notch 124 to the first tank port 47. The load pressure of the actuator 88 is the second actuator port 3
5. Act on the first pressure chamber 65 from the second load pressure detection port 46 and the passage 58 to push the spool 64 rightward to cause a stroke. At this time, the pressure of the second port 42 is introduced into the spring chamber 107 of the check valve 101 by the throttle 108 of the spool 64 and acts on the left side surface of the check valve 101. On the other hand, the pressure in the third port 43 flows into the pressure chamber 103 between the check valve 101 and the blind hole 68a of the seat 68 from the throttle 106 of the spool 64, the annular recess 68b, and the second throttle 105 of the seat 68. Acts on the right side of valve 101. Since the pressure of the second port 42 and the pressure of the third port 43 are substantially the same, the check valve 101 is pressed against the seat 68 by the spring 102 and held.
【００２２】これによりスプール６４の切欠溝１０９が
第２ポート４２に開口して図５のように通路１１１で連
通するから左右の弁ブロック３０，３０に接続した左右
のアクチュエータ８８，８８の負荷圧は第２ポート４２
と通路１１１で同一圧力となり、しかもこの第２ポート
４２は開口１００で第３ポート４３に連通するから、前
記負荷圧が負荷圧検出回路８２に供給されるので、左右
のアクチュエータ８８の一方のポート８８ａに供給され
る圧力、つまり負荷圧が同一となって直進走行できる。As a result, the notch groove 109 of the spool 64 opens to the second port 42 and communicates with the passage 111 as shown in FIG. 5, so that the load pressure of the left and right actuators 88, 88 connected to the left and right valve blocks 30, 30 is increased. Is the second port 42
Since the second port 42 communicates with the third port 43 through the opening 100, the load pressure is supplied to the load pressure detecting circuit 82. When the pressure supplied to 88a, that is, the load pressure becomes the same, the vehicle can travel straight.
【００２３】左右旋回走行時。前述の状態から右側の弁
ブロック３０の方向制御弁２２の主スプール４９を中立
位置に向けて右方に摺動すると、第２負荷圧検出ポート
４６と第２アクチュエータポート３５との開口面積が小
さくなるため右側のアクチュエータ８８の一方のポート
８８ａに流れる流量が減少する。この結果、右側のアク
チュエータ８８の負荷圧が低下して右側の弁ブロック３
０の減圧弁部２４の第１圧力室６５の圧力が低下し、そ
のスプール６４は第２圧力室６６に負荷圧検出路８２で
供給されている左側の弁ブロック３０の第２圧力室６６
内の負荷圧（つまり制御圧）により左方に押されて第２
ポート４２と第１圧力室６５が切欠溝１０９によって連
通されなくなるから、左右側の負荷圧が同圧にならずに
右側のアクチュエータ８８の負荷圧が低く、左側のアク
チュエータ８８の負荷圧が高くなって右旋回走行する。
この時、右側の弁ブロック３０の減圧弁部２４のチェッ
ク弁１０１のバネ室１０２には通路１１１、第２ポート
４２、絞り１０８より左側のアクチュエータ８８の負荷
圧が導入されてチェック弁１０１の左側面に作用する。
他方、チェック弁１０１の右側面には負荷圧検出路８
２、第３ポート４３、スプール６４の絞り１０６、第２
絞り１０５より制御圧が作用するが、この制御圧は左側
のアクチュエータ８８の負荷圧とほぼ等しいからチェッ
ク弁１０１はフリーピストン６８に押しつけた状態とな
る。At the time of right and left turning traveling. When the main spool 49 of the direction control valve 22 of the right valve block 30 is slid rightward toward the neutral position from the above-described state, the opening area between the second load pressure detection port 46 and the second actuator port 35 decreases. Therefore, the flow rate flowing to one port 88a of the right actuator 88 decreases. As a result, the load pressure of the right actuator 88 decreases and the right valve block 3
0, the pressure in the first pressure chamber 65 of the pressure reducing valve section 24 decreases, and the spool 64 of the second pressure chamber 66 is supplied to the second pressure chamber 66 by the load pressure detection path 82 in the second pressure chamber 66 of the left valve block 30.
Pressed to the left by the load pressure (that is, the control pressure) inside
Since the port 42 and the first pressure chamber 65 are not communicated with each other by the cutout groove 109, the load pressure on the right actuator 88 is low and the load pressure on the left actuator 88 is high without the left and right load pressures being equal. Turn right.
At this time, the load pressure of the passage 88, the second port 42, and the load of the actuator 88 on the left side of the throttle 108 is introduced into the spring chamber 102 of the check valve 101 of the pressure reducing valve section 24 of the right valve block 30, so that the left side of the check valve 101 Act on the surface.
On the other hand, on the right side of the check valve 101, a load pressure detecting path 8 is provided.
2, third port 43, throttle 106 of spool 64, second
The control pressure acts from the throttle 105, but this control pressure is almost equal to the load pressure of the left actuator 88, so that the check valve 101 is pressed against the free piston 68.
【００２４】図６は複数の弁ブロック３０をその左右側
面３２，３３相互を接合して組み合せ連結した状態の横
断面図であり、説明の都合上弁ブロック３０を第１・第
２・第３・第４・第５・第６弁ブロック３０ａ、３０
ｂ、３０ｃ、３０ｄ、３０ｅ、３０ｆとする。第２、第
３弁ブロック３０ｂ、３０ｃが図５に示す左右走行用油
圧モータの弁ブロックとなり、第１弁ブロック３０ａに
一側ブロック１３０が接合して連結され、この一側弁ブ
ロック１３０に第１ポート３９に連通した主油孔１３１
が形成され、この主油孔１３１はチェック弁１３２を介
して油孔１３３に連通し、この油孔１３３が第１弁ブロ
ック３０ａの第２ポート４２にポート１３４で連通し、
各弁ブロック３０の第３ポート４３はポート１３５でそ
れぞれ連通し、第２・第３弁ブロック３０ｂ、３０ｃの
第２ポート４２相互がポート１３６で連通し、第４、第
５、第６弁ブロック３０ｄ、３０ｅ、３０ｆの第２ポー
ト４２がポート１３７でそれぞれ連通し、各弁ブロック
３０の第１ポート３９は相互に連通している。第６弁ブ
ロック３０ｆには他側ブロック１３９が接合して連結さ
れ、この他側ブロック１３９には第１通路１４０と第２
通路１４１が形成してあり、その第１通路１４０は第６
弁ブロック３０ｆの第１ポート３９と第２ポート４２に
連通したポート１４２を連通し、第２連通路１４１は第
６弁ブロック３０ｆの第３ポート４３に連通したポート
１４３と負荷圧検出路８２を連通している。FIG. 6 is a cross-sectional view of a state in which a plurality of valve blocks 30 are combined and connected by joining their left and right side surfaces 32 and 33 to each other. For convenience of explanation, the valve blocks 30 are first, second, and third.・ Fourth, fifth and sixth valve blocks 30a, 30
b, 30c, 30d, 30e, and 30f. The second and third valve blocks 30b and 30c are valve blocks of the hydraulic motor for right and left traveling shown in FIG. 5, and a first block 130 is joined and connected to the first valve block 30a. Main oil hole 131 communicating with 1 port 39
The main oil hole 131 communicates with the oil hole 133 via the check valve 132, and the oil hole 133 communicates with the second port 42 of the first valve block 30a at the port 134,
The third port 43 of each valve block 30 communicates with a port 135, the second port 42 of the second and third valve blocks 30b and 30c communicates with a port 136, and the fourth, fifth, and sixth valve blocks. The second ports 42 of 30d, 30e, and 30f communicate with each other at a port 137, and the first ports 39 of each valve block 30 communicate with each other. The other block 139 is joined and connected to the sixth valve block 30f, and the other block 139 is connected to the first passage 140 and the second passage 139.
A passage 141 is formed, and the first passage 140 is the sixth passage.
The port 142 communicating with the first port 39 and the second port 42 of the valve block 30f communicates, and the second communication passage 141 connects the load pressure detection path 82 with the port 143 communicating with the third port 43 of the sixth valve block 30f. Communicating.
【００２５】図４において、チェック弁部２３のスプー
ル６０に第１ポート３９とポンプポート４４を連通・遮
断する小径部１５０を形成してスプール６０を右方に押
す圧力室１５１と第１ポート３９を区画し、スプール６
０に形成したダンパ用絞り１５２と連通孔１５３で第１
ポート３９に連通する。これにより、スプール６０が右
方、左方に摺動する時に第１ポート３９と圧力室１５１
との間にダンパ用絞り１５２を通して圧油が流れるか
ら、スプール６０が急激に左方、右方に摺動することを
防止できる。In FIG. 4, a small-diameter portion 150 is formed in the spool 60 of the check valve portion 23 for connecting and disconnecting the first port 39 and the pump port 44, and the pressure chamber 151 for pushing the spool 60 rightward and the first port 39 are formed. Partition and spool 6
0 through the damper throttle 152 and the communication hole 153.
It communicates with port 39. Thus, when the spool 60 slides rightward and leftward, the first port 39 and the pressure chamber 151 slide.
Therefore, the pressure oil flows through the damper throttle 152 between the two positions, so that the spool 60 can be prevented from suddenly sliding left and right.
【００２６】[0026]
【発明の効果】左右の弁ブロック３０，３０の方向制御
弁２２，２２の各主スプール４９を同一方向に同一スト
ローク摺動した時に左右の弁ブロック３０，３０の減圧
弁部２４の第１圧力室６５と第２ポート４２が連通し、
しかも左右の弁ブロック３０，３０の第２ポート４２相
互が連通しているから、その左右の弁ブロック３０，３
０の第２ポート４２の圧力が等しくなり、左右の弁ブロ
ック３０，３０の方向制御弁２２，２２の開口面積が加
工誤差等で異なっても左右の弁ブロック３０，３０の第
１・第２アクチュエータポート３４，３５に油圧ポンプ
２０の吐出圧油を同一流量供給できる。したがって、左
右の弁ブロック３０，３０の第１・第２アクチュエータ
ポート３４，３５を左右走行用油圧モータに接続するこ
とで、左右走行用モータに同一流量を供給して直進走行
できる。When the main spools 49 of the directional control valves 22, 22 of the left and right valve blocks 30, 30 are slid in the same direction by the same stroke, the first pressure of the pressure reducing valve portions 24 of the left and right valve blocks 30, 30 is increased. The chamber 65 communicates with the second port 42,
Moreover, since the second ports 42 of the left and right valve blocks 30, 30 are in communication with each other, the left and right valve blocks 30, 3,
0, the pressures of the second ports 42 become equal, and even if the opening areas of the directional control valves 22, 22 of the left and right valve blocks 30, 30 are different due to processing errors and the like, the first and second valve blocks 30, 30 are left and right. Discharge pressure oil of the hydraulic pump 20 can be supplied to the actuator ports 34 and 35 at the same flow rate. Therefore, by connecting the first and second actuator ports 34 and 35 of the left and right valve blocks 30 and 30 to the left and right traveling hydraulic motors, it is possible to supply the same flow rate to the left and right traveling motors and travel straight.
【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】圧力補償弁と方向制御弁の具体例を示す断面図
である。FIG. 3 is a sectional view showing a specific example of a pressure compensating valve and a direction control valve.
【図４】本発明の実施例を示す弁ブロックの断面図であ
る。FIG. 4 is a sectional view of a valve block showing an embodiment of the present invention.
【図５】左右の弁ブロックの接続状態を示す説明図であ
る。FIG. 5 is an explanatory diagram showing a connection state of left and right valve blocks.
【図６】複数の弁ブロックを接合して組み合せた状態の
横断面図である。FIG. 6 is a cross-sectional view of a state where a plurality of valve blocks are joined and combined.
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…
第１ポート、４２…第２ポート、４３…第３ポート、４
４…ポンプポート、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、１０９…切欠溝。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 ...
1st port, 42 ... 2nd port, 43 ... 3rd port, 4
4 pump 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, 109 ... notched groove.
───────────────────────────────────────────────────── フロントページの続き (56)参考文献 特開 昭53−41681（ＪＰ，Ａ) 特開 平５−332308（ＪＰ，Ａ) 特開 平５−332309（ＪＰ，Ａ) 特開 平４−351384（ＪＰ，Ａ) 実開 平５−30503（ＪＰ，Ｕ) (58)調査した分野(Int.Cl.7，ＤＢ名) F15B 11/00 - 11/22 ────────────────────────────────────────────────── ─── Continuation of the front page (56) References JP-A-53-41681 (JP, A) JP-A-5-332308 (JP, A) JP-A-5-332309 (JP, A) JP-A-4- 351384 (JP, A) Japanese Utility Model 5-30503 (JP, U) (58) Field surveyed (Int. Cl. 7 , DB name) F15B 11/00-11/22
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に開口したポンプポート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
第１ポート３９及びチェック弁用孔３７をポンプポート
４４に連通する油路５６を形成し、そのチェック弁用孔
３７に第１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２
・第３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３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、 前記減圧弁部２４のスプール６４を、第１圧力室６５内
の圧力でバネ６９に抗する方向に押された時に第１圧力
室６５を第２ポート４２に連通する形状とし、 一対の弁ブロック３０の第１ポート３９に油圧ポンプ２
０の吐出路２１を接続し、一対の弁ブロック３０の第２
ポート４２相互を連通し、一対の弁ブロック３０の第３
ポート４３を負荷圧検出器８２に連通したことを特徴と
する油圧供給装置。1. A spool port 31, a check valve hole 37, and a pressure reducing valve hole 38 are formed in a valve block 30, and a pump 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.
A main spool 49 for connecting and disconnecting each port is inserted into the directional control valve 22 by inserting the first port 39 and the check valve hole 37 opened in the check valve hole 37 into the valve block 30. An oil passage 56 communicating with the first port 39 is formed in the check valve hole 37. The first port 39 communicates and shuts off the oil passage 56, and a spool 60 stopped at the shut-off position is inserted into the check valve portion 23 to form the check valve portion 23. The valve block 30 has a second opening that opens to the pressure reducing hole 38.
The third 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 communicates with the second load pressure detection port 46, and the second pressure chamber 66 is connected to the third 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 A pressure compensating valve 25 is provided at 23, and the first pressure chamber 65 communicates with the second port 42 when the spool 64 of the pressure reducing valve section 24 is pressed in a direction against the spring 69 by the pressure in the first pressure chamber 65. The hydraulic pump 2 is connected to the first port 39 of the pair of valve blocks 30.
0 discharge path 21, and the second
The ports 42 communicate with each other, and the third
A hydraulic supply device characterized in that the port (43) communicates with a load pressure detector (82).
Priority Applications (7)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP04161925A JP3119317B2 (en) | 1992-05-29 | 1992-05-29 | Pressure oil supply device |
| DE4391634T DE4391634T1 (en) | 1992-04-08 | 1993-04-08 | Pressurized fluid supply system |
| DE4391634A DE4391634B4 (en) | 1992-04-08 | 1993-04-08 | Pressure oil supplying device |
| US08/302,912 US5533334A (en) | 1992-04-08 | 1993-04-08 | Pressurized fluid supply system |
| DE4345488A DE4345488B4 (en) | 1992-04-08 | 1993-04-08 | Pressure oil supplying device |
| PCT/JP1993/000452 WO1993021446A1 (en) | 1992-04-08 | 1993-04-08 | Pressure oil supplying device |
| US08/552,693 US5622206A (en) | 1992-04-08 | 1995-11-03 | Multiple valve unit for pressurized fluid supply system |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP04161925A JP3119317B2 (en) | 1992-05-29 | 1992-05-29 | Pressure oil supply device |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| JPH05332310A JPH05332310A (en) | 1993-12-14 |
| JP3119317B2 true JP3119317B2 (en) | 2000-12-18 |
Family
ID=15744646
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP04161925A Expired - Lifetime JP3119317B2 (en) | 1992-04-08 | 1992-05-29 | Pressure oil supply device |
Country Status (1)
| Country | Link |
|---|---|
| JP (1) | JP3119317B2 (en) |
Families Citing this family (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPH082269A (en) * | 1994-06-21 | 1996-01-09 | Komatsu Ltd | Travel control circuit for hydraulic drive type traveling device |
| US6082106A (en) * | 1997-10-17 | 2000-07-04 | Nachi-Fujikoshi Corp. | Hydraulic device |
| JP4155811B2 (en) * | 2002-12-13 | 2008-09-24 | 株式会社小松製作所 | Differential pressure adjustment valve |
-
1992
- 1992-05-29 JP JP04161925A patent/JP3119317B2/en not_active Expired - Lifetime
Also Published As
| Publication number | Publication date |
|---|---|
| JPH05332310A (en) | 1993-12-14 |
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