JPH05296207A - Confluence-diffluence device in hydraulic circuit - Google Patents
Confluence-diffluence device in hydraulic circuitInfo
- Publication number
- JPH05296207A JPH05296207A JP4092502A JP9250292A JPH05296207A JP H05296207 A JPH05296207 A JP H05296207A JP 4092502 A JP4092502 A JP 4092502A JP 9250292 A JP9250292 A JP 9250292A JP H05296207 A JPH05296207 A JP H05296207A
- Authority
- JP
- Japan
- Prior art keywords
- valve
- pressure
- pump
- merging
- 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.)
- Granted
Links
Landscapes
- Operation Control Of Excavators (AREA)
- Fluid-Pressure Circuits (AREA)
Abstract
Description
【０００１】[0001]
【産業上の利用分野】本発明は、複数のポンプの吐出圧
油を複数の操作弁によって複数のアクチュエータに供給
する油圧回路における合分流装置に関する。BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a merging / dividing device in a hydraulic circuit for supplying pressure oil discharged from a plurality of pumps to a plurality of actuators by a plurality of operating valves.
【０００２】[0002]
【従来の技術】図１に示すように、第１ポンプ１と第２
ポンプ２の吐出路１ａ，２ａを接続し、その吐出路１
ａ，１ｂに複数のクローズドセンタ型式の操作弁３を配
設し、その操作弁３とアクチュエータの接続回路４に圧
力補償弁５を設け、各アクチュエータの負荷圧における
最高圧をシャトル弁６で検出し、その負荷圧を各圧力補
償弁５のバネ室５ａに供給して、その負荷圧に対応する
セット圧とする油圧回路が知られている。2. Description of the Related Art As shown in FIG. 1, a first pump 1 and a second pump 1
The discharge paths 1a and 2a of the pump 2 are connected to each other, and the discharge path 1
A plurality of closed center type operation valves 3 are provided in a and 1b, a pressure compensation valve 5 is provided in a connection circuit 4 between the operation valve 3 and the actuator, and the maximum pressure of the load pressure of each actuator is detected by the shuttle valve 6. However, there is known a hydraulic circuit in which the load pressure is supplied to the spring chamber 5a of each pressure compensating valve 5 to obtain a set pressure corresponding to the load pressure.
【０００３】かかる油圧回路であれば、複数の操作弁３
を同時操作した時に複数のアクチュエータの負荷圧にお
ける最高圧によって圧力補償弁５がセットされ、複数の
アクチェータの負荷圧が異なっても操作弁３の開口面積
比によって複数のアクチュエータに流量分配できる。With such a hydraulic circuit, a plurality of operating valves 3
The pressure compensating valve 5 is set by the maximum pressure among the load pressures of the plurality of actuators when the actuators are simultaneously operated, and even if the load pressures of the plurality of actuators are different, the flow rates can be distributed to the plurality of actuators by the opening area ratio of the operation valve 3.
【０００４】かかる油圧回路であると、複数のアクチュ
エータを同時作動する場合に圧力補償弁は高い方の負荷
圧でセットされポンプ吐出圧力はそのセット圧より若干
高い高圧となるので、アクチュエータの負荷圧の差が大
きい場合には負荷圧の小さいアクチュエータ側の圧力補
償弁における圧力損失が大となり、第１・第２ポンプ
１，２を駆動する原動機の損失馬力が大となると共に、
作動油の温度が高くなって作動油の劣化を早めることに
なる。例えば、パワーショベルのブームシリンダと旋回
モータに圧油を供給してブーム下降、上部車体旋回する
場合に、ブームは自重降下するから負荷圧は低圧である
が、旋回モータは上部車体を起動・加速するため負荷圧
が高圧となり、その時のポンプ吐出圧はセット圧より若
干高い高圧となるので、ブームシリンダ側の圧力補償弁
では高圧−低圧の分が圧力損失となり、前述のように負
荷圧の差が大であるから圧力損失が大となってしまう。
このことは、アームシリンダでアームを上昇させバケッ
トシリンダでバケットをダンプして土砂を排出する場合
に、アームシリンダの負荷圧が高く、バケットシリンダ
の負荷圧が低くなるから同様である。In such a hydraulic circuit, when a plurality of actuators are simultaneously operated, the pressure compensating valve is set at a higher load pressure and the pump discharge pressure becomes a pressure slightly higher than the set pressure. When the difference between the two is large, the pressure loss in the pressure compensating valve on the actuator side where the load pressure is small becomes large, and the loss horsepower of the prime mover driving the first and second pumps 1 and 2 becomes large, and
The temperature of the hydraulic oil rises, which accelerates the deterioration of the hydraulic oil. For example, when supplying pressure oil to the boom cylinder and swing motor of a power shovel to lower the boom and swing the upper body, the load pressure is low because the boom descends by its own weight, but the swing motor starts and accelerates the upper body. Therefore, the load pressure becomes high, and the pump discharge pressure at that time is slightly higher than the set pressure.Therefore, at the boom cylinder side pressure compensating valve, the high pressure-low pressure component causes a pressure loss. Is large, the pressure loss will be large.
This is the same as when the arm cylinder raises the arm and the bucket cylinder dumps the bucket to discharge the earth and sand, the load pressure of the arm cylinder is high and the load pressure of the bucket cylinder is low.
【０００５】このことを解消する油圧回路として図２に
示すものが知られている。すなわち、図２に示すように
第１ポンプ１の吐出路１ａと第２ポンプ２の吐出路２ａ
を合分流弁１６で接続し、第１ポンプ１の吐出路１ａに
接続した操作弁３の圧力補償弁５の負荷圧導入路１７と
第２ポンプ２の吐出路２ａに接続した操作弁３の圧力補
償弁５の負荷圧導入路１８を合分流弁１９で接続した油
圧回路であり、これによって、合分流弁１６，１９によ
って各吐出路１ａ，１ｂ及び各負荷圧導入路１７，１８
をそれぞれ独立させ、一方の吐出路１ａに接続したアク
チュエータ１０，１１，１２と他方の吐出路２ａに接続
したアクチュエータ１３，１４，１５を同時操作した時
に、それぞれのアクチュエータの負荷圧で圧力補償弁を
セットして、圧力損失を低減できるようにできる。A hydraulic circuit shown in FIG. 2 is known as a hydraulic circuit for solving this problem. That is, as shown in FIG. 2, the discharge passage 1 a of the first pump 1 and the discharge passage 2 a of the second pump 2 are shown.
Of the operation valve 3 connected to the discharge passage 1a of the first pump 1 and the load pressure introduction passage 17 of the pressure compensation valve 5 of the operation valve 3 connected to the discharge passage 2a of the second pump 2 This is a hydraulic circuit in which the load pressure introducing passage 18 of the pressure compensating valve 5 is connected by a merging / dividing valve 19, whereby the discharge passages 1a, 1b and the load pressure introducing passages 17, 18 are connected by the merging / dividing valves 16, 19.
When the actuators 10, 11, 12 connected to one discharge passage 1a and the actuators 13, 14, 15 connected to the other discharge passage 2a are operated simultaneously, the pressure compensating valve is adjusted by the load pressure of each actuator. Can be set to reduce pressure loss.
【０００６】[0006]
【発明が解決しようとする課題】かかる合分流機能を有
する油圧回路であると、２つの合分流弁１６，１９が必
要となるので、油圧回路を構成する機器が多くなって全
体が大型となるばかりか、２つの合分流弁１６，１９へ
の配管が増えて配管が複雑となる。In the hydraulic circuit having such a merging / branching function, two merging / branching valves 16 and 19 are required, so that the number of devices forming the hydraulic circuit increases and the whole becomes large. In addition, the number of pipes to the two merging / branching valves 16 and 19 is increased, and the pipes are complicated.
【０００７】そこで、本発明は前述の課題を解決できる
ようにした油圧回路における合分流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 merging / branching device in a hydraulic circuit that can solve the above-mentioned problems.
【０００８】[0008]
【課題を解決するための手段】操作弁本体７０に弁ブロ
ック７３を取付け、この弁ブロック７３に複数のポンプ
ポートを連通、遮断する第１スプール８７を設けて第１
合分流弁５５とし、前記弁ブロック７３に複数の負荷圧
導入ポートを連通、遮断する第２スプール８９を設けて
第２合分流弁５６とした油圧回路における合分流装置。A valve block 73 is attached to an operation valve main body 70, and a first spool 87 for connecting and disconnecting a plurality of pump ports is provided in the valve block 73.
A merging / dividing device in a hydraulic circuit that is a merging / dividing valve 55, and a second spool 89 that connects and disconnects a plurality of load pressure introducing ports to the valve block 73 is provided as a second merging / dividing valve 56.
【０００９】[0009]
【作 用】操作弁本体７０と弁ブロック７３より成る
からコンパクトにできるし、操作弁本体７０と第１・第
２合分流弁５５，５６との間の配管が不要で配管が簡単
となる。[Operation] Since the operation valve body 70 and the valve block 73 are used, the size can be made compact, and piping between the operation valve body 70 and the first and second combined flow dividing valves 55 and 56 is not required, which simplifies the piping.
【００１０】[0010]
【実 施 例】図３に基づいて合分流機能を有する油圧
回路を説明する。図３に示すように、油圧ポンプ３０の
吐出路３０ａには操作弁３１が設けられ、この操作弁３
１とアクチュエータ３２を接続する回路３３に圧力補償
弁３４が設けてあり、そのアクチュエータ３２の負荷圧
は操作弁３０内の絞りを通して負荷圧導入路３５に導入
される。前記油圧ポンプ３０の斜板３６は小径ピストン
３７で容量大方向に傾転され、大径ピストン３８で容量
小方向に傾転されると共に、その小径ピストン３７の小
径受圧室３７ａは前記吐出路３０ａに接続してポンプ吐
出圧が供給され、前記大径ピストン３８の大径受圧室３
８ａはＬＳ弁３９で吐出路３０ａとタンク４０に連通制
御される。前記ＬＳ弁３９は負荷圧とばね４１でドレー
ン位置Ａに押され、ポンプ吐出圧で供給位置Ｂに押され
るようになって、ポンプ吐出圧を負荷圧よりも若干高い
圧力、例えば２０ｋｇ／ｃｍ2 となるように斜板３６を
傾転動作する。前記油圧ポンプ３０の吐出路３０ａには
アンロード弁４２が設けられ、このアンロード弁４２は
ばねと第１受圧部４３に供給される負荷圧でオンロード
位置４２ａに押され、第２受圧部４４に供給されるポン
プ吐出圧でアンロード位置４２ｂに押され、ポンプ吐出
圧と負荷圧の差圧が設定圧力、例えば３０ｋｇ／ｃｍ2
以上となるとアンロード位置４２ｂとなるもので、複数
の油圧ポンプの個別のポンプ吐出圧と負荷圧のみによっ
て作動する。パイロット油圧弁４５はレバー４６を操作
することで補助ポンプ４７の吐出圧油を第１・第２パイ
ロット管路４８，４９で操作弁３１の第１・第２受圧部
５０，５１に供給して操作弁３１を中立位置３１ａから
第１位置３１ｂ、第２位置３１ｃに切換えるものであ
り、この第１・第２パイロット管路４８，４９には第１
・第２圧力スイッチ５２，５３が設けられて圧力が発生
すると電気信号をコントローラ５４に出力する。以上の
説明は図３において左側の油圧ポンプ３０のみを示し、
右側の油圧ポンプ３０も同様であるから符号を同一とし
て説明を省略する。[Example] A hydraulic circuit having a merging / branching function will be described with reference to FIG. As shown in FIG. 3, an operating valve 31 is provided in the discharge passage 30 a of the hydraulic pump 30, and the operating valve 3
A pressure compensating valve 34 is provided in a circuit 33 that connects 1 and the actuator 32, and the load pressure of the actuator 32 is introduced into a load pressure introducing passage 35 through a throttle in the operation valve 30. The swash plate 36 of the hydraulic pump 30 is tilted in the large capacity direction by the small diameter piston 37 and tilted in the small capacity direction by the large diameter piston 38, and the small diameter pressure receiving chamber 37a of the small diameter piston 37 is disposed in the discharge passage 30a. Is connected to the pump and the pump discharge pressure is supplied to the large-diameter pressure receiving chamber 3 of the large-diameter piston 38.
LS valve 39 controls communication between the discharge passage 30a and the tank 8a. The LS valve 39 is pushed to the drain position A by the load pressure and the spring 41, and is pushed to the supply position B by the pump discharge pressure, so that the pump discharge pressure is slightly higher than the load pressure, for example, 20 kg / cm 2. The swash plate 36 is tilted so that An unloading valve 42 is provided in the discharge passage 30a of the hydraulic pump 30, and the unloading valve 42 is pushed to the on-load position 42a by the load pressure supplied to the spring and the first pressure receiving portion 43, and the second pressure receiving portion 42a. It is pushed to the unload position 42b by the pump discharge pressure supplied to the pump 44, and the differential pressure between the pump discharge pressure and the load pressure is set pressure, for example, 30 kg / cm 2.
With the above, the unload position 42b is reached, and the hydraulic pumps are operated only by the individual pump discharge pressure and load pressure. The pilot hydraulic valve 45 supplies the discharge pressure oil of the auxiliary pump 47 to the first and second pressure receiving portions 50 and 51 of the operation valve 31 through the first and second pilot conduits 48 and 49 by operating the lever 46. The operation valve 31 is switched from the neutral position 31a to the first position 31b and the second position 31c, and the first and second pilot lines 48 and 49 have the first valve 31a.
Second pressure switches 52 and 53 are provided to output an electric signal to the controller 54 when pressure is generated. The above description shows only the hydraulic pump 30 on the left side in FIG.
Since the hydraulic pump 30 on the right side is also the same, the same reference numerals are used and the description thereof is omitted.
【００１１】前記左側の油圧ポンプ３０の吐出路３０ａ
と右側の油圧ポンプ３０の吐出路３０ａは第１合分流弁
５５で合流・分流可能となり、前記左側の負荷圧導入路
３５と右側の負荷圧導入路３５は第２合分流弁５６で合
流・分流可能となり、その第１・第２合分流弁５５，５
６はばね力で合流位置５５ａ，５６ａに押され、受圧部
５７，５８に供給されるパイロット圧油で分流位置５５
ｂ，５６ｂに切換える。前記補助ポンプ４７の吐出圧油
は電磁弁５９で受圧部５７，５８に供給制御され、その
電磁弁５９はばね力でドレーン位置５９ａに保持され、
ソレノイド６０に通電されると供給位置５９ｂに切換わ
り、そのソレノイド６０には前記コントローラ５４によ
り通電制御される。Discharge passage 30a of the left hydraulic pump 30
And the discharge passage 30a of the hydraulic pump 30 on the right side can be joined / split by the first joining / dividing valve 55, and the load pressure introducing passage 35 on the left side and the load pressure introducing passage 35 on the right side are joined by the second joining / dividing valve 56. Flow splitting becomes possible, and the first and second combined split valves 55, 5
6 is pushed by the spring force to the merging positions 55a and 56a, and the pilot pressure oil supplied to the pressure receiving portions 57 and 58 is used to divide the diverging position 55.
Switch to b, 56b. The pressure oil discharged from the auxiliary pump 47 is controlled to be supplied to the pressure receiving portions 57 and 58 by an electromagnetic valve 59, and the electromagnetic valve 59 is held at the drain position 59a by a spring force.
When the solenoid 60 is energized, it is switched to the supply position 59b, and the solenoid 60 is energized by the controller 54.
【００１２】前記左側の負荷圧導入路３５と右側の負荷
圧導入路３５は一対のチェック弁６１，６１を有する短
絡路６２で連通し、この短絡路６２にリリーフ弁６３が
設けてあり、前記左側の油圧ポンプ３０の吐出路３０ａ
と右側の油圧ポンプ３０の吐出路３０ａは一対のチェッ
ク弁６４，６４を有する短絡路６５で連通し、この短絡
路６５にアンロード弁６６が接続してある。このアンロ
ード弁６６はばね力と前記短絡路６２の負荷圧によって
オンロード位置６６ａに保持され、前記短絡路６５のポ
ンプ吐出圧でアンロード位置６６ｂとなるもので、この
アンロード弁６６のセット圧は前記個別のアンロード弁
４２のセット圧よりも低くしてある。つまり、アンロー
ドする時のポンプ吐出圧と負荷圧の差圧が低くしてもあ
る。The left-side load pressure introducing passage 35 and the right-side load pressure introducing passage 35 communicate with each other through a short circuit 62 having a pair of check valves 61, 61, and a relief valve 63 is provided in the short circuit 62. Discharge passage 30a of the left hydraulic pump 30
And the discharge passage 30a of the hydraulic pump 30 on the right side are communicated with each other by a short circuit 65 having a pair of check valves 64, 64, and an unload valve 66 is connected to the short circuit 65. The unload valve 66 is held at the on-load position 66a by the spring force and the load pressure of the short-circuit path 62 and becomes the unload position 66b by the pump discharge pressure of the short-circuit path 65. The pressure is lower than the set pressure of the individual unload valves 42. That is, the differential pressure between the pump discharge pressure and the load pressure when unloading may be low.
【００１３】次に作動を説明する。左側の操作レバー４
６でパイロット油圧弁４５を操作して第１パイロット管
路４８にパイロット圧油を供給すると操作弁３１の第１
受圧部５０にパイロット圧油が供給されて操作弁３１は
第１位置３１ｂとなり、左側の油圧ポンプ３０の吐出圧
油が左側のアクチュエータ３２に供給される。このアク
チュエータ３２の負荷圧は操作弁３１の第１位置３１ｂ
に設けた絞りを経て負荷圧導入路３５に導入される。こ
れにより、第１圧力スイッチ５２が電気信号をコントロ
ーラ５４に入力してコントローラ５４は左側の操作弁３
１が第１位置３１ｂとなったと判断し、それによって合
流するかしないかを予め設定したパターンに基づいて演
算し、合流する場合には電磁弁５９のソレノイド６０に
操作せずにドレーン位置５９ａとし、第１・第２合分流
弁５５，５６を合流位置５５ａ，５６ａとして左側と右
側の油圧ポンプ３０の吐出圧を合流して左側のアクチュ
エータ３２に供給する。分流する場合には電磁弁５９の
ソレノイド６０に通電して供給位置５９ｂとし、補助油
圧ポンプ４７の吐出圧油を第１・第２合分流弁５５，５
６の受圧部５７，５８に供給して分流位置５５ｂ，５６
ｂとし、左側の油圧ポンプ３０の吐出圧油のみを左側の
アクチュエータ３２に供給する。他方、負荷圧導入路３
５の負荷圧はＬＳ弁３９に作用して油圧ポンプ３０の斜
板３６を傾転しポンプ吐出圧と負荷圧の差圧を設定圧力
とすると共に、その負荷圧は圧力補償弁３４に作用して
圧力補償する。左側の操作レバー４６を前述と反対に操
作して第２パイロット管路４９にパイロット圧油を供給
した場合及び、右側の操作レバー４６を操作した場合も
前述と同様になる。Next, the operation will be described. Left operating lever 4
6 operates the pilot hydraulic valve 45 to supply pilot pressure oil to the first pilot line 48, and the first operation of the operation valve 31
The pilot pressure oil is supplied to the pressure receiving portion 50, the operation valve 31 is in the first position 31b, and the discharge pressure oil of the left hydraulic pump 30 is supplied to the left actuator 32. The load pressure of the actuator 32 is the first position 31b of the operation valve 31.
It is introduced into the load pressure introducing passage 35 through the throttle provided in the. As a result, the first pressure switch 52 inputs an electric signal to the controller 54, and the controller 54 causes the left operation valve 3 to operate.
1 is determined to be the first position 31b, and whether or not to join the first position 31b is calculated based on a preset pattern. , The first and second merging / dividing valves 55 and 56 are set as merging positions 55a and 56a, and the discharge pressures of the left and right hydraulic pumps 30 are merged and supplied to the left actuator 32. When the flow is divided, the solenoid 60 of the solenoid valve 59 is energized to the supply position 59b, and the pressure oil discharged from the auxiliary hydraulic pump 47 is divided into the first and second combined flow dividing valves 55 and 5.
6 to supply pressure to the pressure receiving portions 57 and 58, and the flow dividing positions 55b and 56
b, only the pressure oil discharged from the left hydraulic pump 30 is supplied to the left actuator 32. On the other hand, load pressure introduction path 3
The load pressure of 5 acts on the LS valve 39 to tilt the swash plate 36 of the hydraulic pump 30 to set the differential pressure between the pump discharge pressure and the load pressure as the set pressure, and the load pressure acts on the pressure compensating valve 34. To compensate the pressure. The same applies to the case where the left operation lever 46 is operated in the opposite manner to supply pilot pressure oil to the second pilot conduit 49 and the case where the right operation lever 46 is operated.
【００１４】次に合流時のアンロード弁４２のアンロー
ド動作（油圧ホンプの最高ポンプ吐出圧の制限動作）を
説明する。前述の状態で左側のアクチュエータ３２がス
トロークエンドとなった時、又はアクチュエータ３２の
負荷が非常に大きく、負荷圧が非常に高い時には、その
負荷圧はチェック弁６１より短絡路６２に流入してリリ
ーフ弁６３よりリリーフする。左右側の油圧ポンプ３
０，３０のポンプ吐出圧油はチェック弁６４より短絡路
６５に流入してアンロード弁６６の入口側に流入すると
同時にアンロード弁６６に作用する。これにより、アン
ロード弁６６に作用する負荷圧がポンプ吐出圧よりも低
下してアンロード弁６６がアンロード位置６６ｂとなっ
て左右側の油圧ポンプ３０の吐出圧の一部がアンロード
する。Next, the unloading operation of the unloading valve 42 at the time of merging (the operation of limiting the maximum pump discharge pressure of the hydraulic pump) will be described. When the left actuator 32 reaches the stroke end in the above-mentioned state, or when the load of the actuator 32 is very large and the load pressure is very high, the load pressure flows from the check valve 61 into the short circuit path 62 and the relief is performed. Relief from valve 63. Hydraulic pump 3 on the left and right
The pump discharge pressure oils of 0 and 30 flow from the check valve 64 into the short-circuit path 65, flow into the inlet side of the unload valve 66, and simultaneously act on the unload valve 66. As a result, the load pressure acting on the unload valve 66 becomes lower than the pump discharge pressure, and the unload valve 66 becomes the unload position 66b, so that part of the discharge pressure of the left and right hydraulic pumps 30 is unloaded.
【００１５】次に分流時のアンロード弁４２のアンロー
ド動作（油圧ポンプの最高ポンプ吐出圧の制限動作）を
説明する。左側の油圧ポンプ３０の吐出路３０ａと右側
の油圧ポンプ３０の吐出路３０ａとが分離すると同時に
左側の負荷圧導入路３５と右側の負荷圧導入路３５が分
離するので、前述の左側のアクチュエータ３２の負荷圧
が非常に高くなると、その負荷圧は左側のチェック弁６
１より短絡路６２に流入し右側のチェック弁６１で右側
の負荷圧導入路３５に流れることを阻止され、その負荷
圧は前述と同様にリリーフ弁６３よりリリーフする。左
側の油圧ポンプ３０の吐出圧は左側のチェック弁６４よ
り短絡路６５に流入して右側のチェック弁６４で右側の
油圧ポンプ３０の吐出路３０ａに流れることを阻止さ
れ、そのポンプ吐出圧はアンロード６６の入口側に作用
する。これにより合流時と同様にしてアンロード弁６６
がアンロード位置６６ｂとなってポンプ吐出圧の一部を
アンロードする。以上の動作において、右側の操作弁３
１が中立位置３１ａであると右側の負荷圧導入路３５は
操作弁３１の中立位置３１ａを経てタンクに接続される
から、その負荷圧はほぼ０ｋｇ／ｃｍ2 であり、右側の
アンロード弁４２の第１受圧部４３に作用する負荷圧が
ほぼ０ｋｇ／ｃｍ2 となってそのアンロード弁４２は第
２受圧部４４に作用する低圧のポンプ吐出圧でアンロー
ド位置４２ｂとなり、右側の油圧ポンプ３０のポンプ吐
出圧はごく低圧となる。Next, the unloading operation of the unloading valve 42 at the time of branching (the operation of limiting the maximum pump discharge pressure of the hydraulic pump) will be described. Since the discharge passage 30a of the left hydraulic pump 30 and the discharge passage 30a of the right hydraulic pump 30 are separated, the load pressure introduction passage 35 on the left side and the load pressure introduction passage 35 on the right side are separated from each other. When the load pressure on the check valve 6 becomes too high,
From 1 to the short-circuit path 62, the check valve 61 on the right side is blocked from flowing to the load pressure introducing path 35 on the right side, and the load pressure is relieved from the relief valve 63 as described above. The discharge pressure of the left hydraulic pump 30 flows into the short circuit path 65 from the left check valve 64 and is prevented from flowing to the discharge path 30a of the right hydraulic pump 30 by the right check valve 64. It acts on the inlet side of the load 66. As a result, the unloading valve 66 can be operated in the same manner as when merging
Becomes the unloading position 66b to unload a part of the pump discharge pressure. In the above operation, the operation valve 3 on the right side
When 1 is the neutral position 31a, the load pressure introducing passage 35 on the right side is connected to the tank via the neutral position 31a of the operation valve 31, so the load pressure is about 0 kg / cm 2 , and the unload valve 42 on the right side The load pressure acting on the first pressure receiving portion 43 becomes almost 0 kg / cm 2, and the unload valve 42 is at the unload position 42b due to the low-pressure pump discharge pressure acting on the second pressure receiving portion 44, and the right hydraulic pump The pump discharge pressure of 30 is very low.
【００１６】以上のように合流時でも分流時でも負荷圧
は１つのリリーフ弁６３よりリリーフするから、アンロ
ード弁６６がアンロードする差圧となるリリーフ流量が
リリーフ弁６３のオーバライド特性により決定され、そ
の際の負荷圧が図６に示すように同一となり、最高ポン
プ吐出圧を合流時と分流時で同一にできる。また、図５
においてリリーフ弁６３の流入側とタンクを小径のオリ
フィス６７で連通してあるが、これは操作弁３１を中立
位置３１ａとした時に一対のチェック弁６１，６１で遮
断されている短絡路６２の負荷圧をすみやかにタンクに
流出するためである。As described above, since the load pressure is relieved by one relief valve 63 during the merging or the diversion, the relief flow rate which is the differential pressure for unloading the unload valve 66 is determined by the override characteristic of the relief valve 63. At that time, the load pressure becomes the same as shown in FIG. 6, and the maximum pump discharge pressure can be made the same at the time of merging and the time of diverting. Also, FIG.
In the above, the inflow side of the relief valve 63 and the tank are communicated with each other by the small diameter orifice 67. This is because the load of the short circuit path 62 which is blocked by the pair of check valves 61, 61 when the operation valve 31 is set to the neutral position 31a. This is because the pressure quickly flows into the tank.
【００１７】次に第１・第２合分流弁５５，５６の取付
構造について説明する。図５に示すように、操作弁本体
７０は直方体形状となり、その相対向する両側面７０ａ
間に複数のスプール７１が摺動自在に嵌挿されて複数の
操作弁３１を有する操作弁装置７２を構成し、その操作
弁本体７０の両側面７０ａと隣接する一側面７０ｂに弁
ブロック７３の一側面７３ａがボルト７４で取付けてあ
る。前記弁ブロック７３には図６に示すように第１スプ
ール孔７５と第２スプール孔７６が上下に間隔を置いて
形成され、弁ブロック７３には、その第１スプール孔７
５に開口する第１・第２ポンプポート７７，７８及び第
１スプール孔７５と第２スプール孔７６を連通するパイ
ロット用ポート７９、空洞部８０並びに第２スプール孔
７６と一側面７３ａに開口した第１・第２・第３ポート
８１，８２，８３がそれぞれ形成してあり、前記第１・
第２ポンプポート７７，７８に図４の左側の油圧ポンプ
３０と右側の油圧ポンプ３０の吐出路３０ａがそれぞれ
接続し、その第１・第２ポンプポート７７，７８は操作
弁本体７０の各スプール７１により切換えられる各ポン
プポートに連通し、第１・第２・第３ポート８１，８
２，８３は操作弁本体７０の第１・第２・第３油孔８
４，８５，８６に連通し、その第１油孔８４が図４にお
ける左側の負荷圧導入路３５となり、第３油孔８６が右
側の負荷圧導入路３５となっている。前記パイロット用
ポート７９は電磁弁５９で補助ポンプ４７の吐出側に接
続している。前記第１スプール孔７５には第１スプール
８７が嵌挿され、この第１スプール８７は第１バネ８８
で第１・第２ポンプポート７７，７８を連通する合流位
置に保持され、パイロット用ポート７９にパイロット圧
油が供給されると第１・第２ポンプポート７７，７８を
遮断する分流位置となり、これにより第１合分流弁５５
を構成している。前記第２スプール孔７６には第２スプ
ール８９が嵌挿され、この第２スプール８９には軸孔９
０と第１・第２径方向孔９１，９２が形成してあり、そ
の第２スプール８９は第２バネ９３で前記第１・第３ポ
ート８１，８３を軸孔９０と第１・第２径方向孔９１，
９２で連通する合分流位置に保持され、前記パイロット
用ポート７９の圧油で遮断する分流位置に押されるよう
になって第２合分流弁５６を構成している。Next, the mounting structure of the first and second combined flow valves 55, 56 will be described. As shown in FIG. 5, the operation valve main body 70 has a rectangular parallelepiped shape, and the opposite side surfaces 70a thereof face each other.
A plurality of spools 71 are slidably inserted between them to form an operating valve device 72 having a plurality of operating valves 31, and a valve block 73 is provided on one side surface 70b adjacent to both side surfaces 70a of the operating valve body 70. One side surface 73a is attached with a bolt 74. As shown in FIG. 6, a first spool hole 75 and a second spool hole 76 are vertically spaced apart from each other in the valve block 73, and the valve block 73 has a first spool hole 7 formed therein.
5, the first and second pump ports 77 and 78, the pilot port 79 that communicates the first spool hole 75 and the second spool hole 76, the cavity 80, the second spool hole 76, and the one side surface 73a. First, second, and third ports 81, 82, and 83 are formed, respectively, and the first and second ports are formed.
The discharge passages 30a of the hydraulic pump 30 on the left side and the hydraulic pump 30 on the right side of FIG. 4 are connected to the second pump ports 77 and 78, and the first and second pump ports 77 and 78 are the spools of the operation valve body 70. The first, second, and third ports 81, 8 communicate with each pump port that is switched by 71.
2 and 83 are the first, second and third oil holes 8 of the operation valve body 70.
4, 85, 86 are communicated with each other, and the first oil hole 84 serves as the left load pressure introducing passage 35 in FIG. 4, and the third oil hole 86 serves as the right load pressure introducing passage 35. The pilot port 79 is connected to the discharge side of the auxiliary pump 47 by a solenoid valve 59. A first spool 87 is fitted in the first spool hole 75, and the first spool 87 has a first spring 88.
Is held at the merging position where the first and second pump ports 77 and 78 communicate with each other, and when pilot pressure oil is supplied to the pilot port 79, it becomes a diverting position that shuts off the first and second pump ports 77 and 78. As a result, the first combined flow valve 55
Are configured. A second spool 89 is fitted in the second spool hole 76, and the shaft hole 9 is inserted in the second spool 89.
0 and first and second radial holes 91 and 92 are formed, and the second spool 89 has a second spring 93 for connecting the first and third ports 81 and 83 to the shaft hole 90 and the first and second ports. Radial holes 91,
The second merging / dividing valve 56 is configured so that it is held at the merging / diverging position where it communicates with each other by 92 and is pushed to the diverting position where it is blocked by the pressure oil of the pilot port 79.
【００１８】次に作動を説明する。電磁弁５９によって
パイロット用ポート７９に圧油を供給しない時には図６
に示すように第１・第２スプール８７，８９が第１・第
２スプリング８８，８９で合流位置となる。これによ
り、第１・第２ポンプポート７７，７８が連通して左側
の油圧ポンプ３０の吐出油と右側の油圧ポンプ３０の吐
出圧油が合流し、第１ポート８１と第２ポート８３が連
通し、左側の負荷圧導入路３５と右側の負荷圧導入路３
５が連通して合流モードとなる。電磁弁５９を切換えて
パイロット用ポート７９に圧油を供給すると図７に示す
ように第１・第２ポンプポート７７，７８が遮断して左
側の油圧ポンプ３０と右側の油圧ポンプ３０が分離し、
第１・第３ポート８１，８３が遮断して左側の負荷圧導
入路３５と右側の負荷圧導入路３５が分離して分流モー
ドとなる。Next, the operation will be described. When pressure oil is not supplied to the pilot port 79 by the solenoid valve 59, as shown in FIG.
As shown in (1), the first and second spools 87 and 89 are brought to the merging position by the first and second springs 88 and 89. As a result, the first and second pump ports 77 and 78 communicate with each other, and the discharge oil of the left hydraulic pump 30 and the discharge hydraulic oil of the right hydraulic pump 30 merge, and the first port 81 and the second port 83 communicate with each other. However, the load pressure introducing path 35 on the left side and the load pressure introducing path 3 on the right side
5 communicate with each other, and the merging mode is set. When the solenoid valve 59 is switched to supply pressure oil to the pilot port 79, the first and second pump ports 77 and 78 are shut off and the left hydraulic pump 30 and the right hydraulic pump 30 are separated as shown in FIG. ,
The first and third ports 81 and 83 are shut off, and the left load pressure introducing passage 35 and the right load pressure introducing passage 35 are separated from each other to be in the shunt mode.
【００１９】また、第１・第２スプール８７，８９を第
１・第２バネ８８，９３で図６に示す合流位置に保持し
たので、第１又は第２ポンプポートの７７，７８に１つ
の油圧ポンプの吐出圧油を供給することで１ポンプ多ア
クチュエータの油圧回路に容易に変更できる。Since the first and second spools 87 and 89 are held at the merging position shown in FIG. 6 by the first and second springs 88 and 93, one of the first and second pump ports 77 and 78 is provided. By supplying the hydraulic fluid discharged from the hydraulic pump, it is possible to easily change the hydraulic circuit to one-pump multi-actuator.
【００２０】[0020]
【発明の効果】操作弁本体７０に取付けた弁ブロック７
３に第１・第２スプール８７，８９を設けて第１・第２
合分流弁５５，５６としたので、全体をコンパクトにで
きるばかりか操作弁３１と第１・第２合分流弁５５，５
６に配管する必要がなく配管が簡単となる。The valve block 7 mounted on the operation valve body 70
The first and second spools 87 and 89 are provided on the first and second spools.
Since the merging / dividing valves 55 and 56 are used, not only the whole can be made compact, but also the operation valve 31 and the first and second merging / dividing valves 55 and 5
Piping becomes simple because there is no need to connect to 6.
【図面の簡単な説明】[Brief description of drawings]
【図１】従来の油圧回路図である。FIG. 1 is a conventional hydraulic circuit diagram.
【図２】改良した従来の油圧回路図である。FIG. 2 is an improved conventional hydraulic circuit diagram.
【図３】本発明の実施例を示す油圧回路図である。FIG. 3 is a hydraulic circuit diagram showing an embodiment of the present invention.
【図４】リリーフ流量と負荷圧の関係を示す図表であ
る。FIG. 4 is a chart showing the relationship between relief flow rate and load pressure.
【図５】合分流弁を取付けた操作弁の正面図である。FIG. 5 is a front view of an operation valve to which a merging / branching valve is attached.
【図６】図５の−断面図である。FIG. 6 is a − sectional view of FIG. 5;
【図７】動作説明図である。FIG. 7 is an operation explanatory diagram.
【符号の説明】 ３０…油圧ポンプ、３０ａ…吐出路、３１…操作弁、３
２…アクチュエータ、３４…圧力補償弁、３５…負荷圧
導入路、５５…第１合分流弁、５６…第２合分流弁、７
０…操作弁本体、７３…弁ブロック、７７…第１ポンプ
ポート、７８…第２ポンプポート、７９…パイロット用
ポート、８１…第１ポート、８３…第３ポート、８７…
第１スプール、８８…第１バネ、８９…第２スプール、
９３…第２バネ。[Explanation of Codes] 30 ... Hydraulic Pump, 30a ... Discharge Path, 31 ... Operation Valve, 3
2 ... Actuator, 34 ... Pressure compensating valve, 35 ... Load pressure introducing passage, 55 ... First merging / dividing valve, 56 ... Second merging / dividing valve, 7
0 ... Operation valve main body, 73 ... Valve block, 77 ... First pump port, 78 ... Second pump port, 79 ... Pilot port, 81 ... First port, 83 ... Third port, 87 ...
1st spool, 88 ... 1st spring, 89 ... 2nd spool,
93 ... Second spring.
Claims (2)
４を有する複数の操作弁３１と、複数の操作弁３１の負
荷圧を検出して圧力補償弁３４にフィードバックする複
数の負荷圧導入路３５と、複数の油圧ポンプ３０の吐出
路３０ａを合流、分離させる第１合分流弁５５と、複数
の負荷圧導入路３５を合流、分離させる第２合分流弁５
６を有する油圧回路において、 前記操作弁３１の操作弁本体７０に弁ブロック７３を取
付け、この弁ブロック７３に複数のポンプポートを連
通、遮断する第１スプール８７を設けて前記第１合分流
弁５５とし、前記弁ブロック７３に複数の負荷圧導入路
３５を連通、遮断する第２スプール８９を設けて前記第
２合分流弁５６として成る油圧回路における合分流装
置。1. A plurality of hydraulic pumps 30 and a pressure compensating valve 3.
4, a plurality of operation valves 31 having a plurality of four, a plurality of load pressure introduction passages 35 for detecting load pressures of the plurality of operation valves 31 and feeding back to the pressure compensation valve 34, and a discharge passage 30a of a plurality of hydraulic pumps 30 are joined, The first merging / dividing valve 55 for separating and the second merging / dividing valve 5 for merging and separating the plurality of load pressure introducing passages 35.
In the hydraulic circuit having 6, the valve block 73 is attached to the operation valve body 70 of the operation valve 31, and the valve block 73 is provided with the first spool 87 for communicating and blocking a plurality of pump ports. 55, and a second spool 89 that connects and disconnects the plurality of load pressure introducing passages 35 to the valve block 73, and serves as the second merging / dividing valve 56.
１・第２バネ８８，９３で連通位置に保持した請求項１
記載の油圧回路における合分流装置。2. The first and second spools 87, 89 are held in a communicating position by first and second springs 88, 93.
A merging / branching device in the described hydraulic circuit.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP04092502A JP3109619B2 (en) | 1992-04-13 | 1992-04-13 | Combining device in hydraulic circuit |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP04092502A JP3109619B2 (en) | 1992-04-13 | 1992-04-13 | Combining device in hydraulic circuit |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| JPH05296207A true JPH05296207A (en) | 1993-11-09 |
| JP3109619B2 JP3109619B2 (en) | 2000-11-20 |
Family
ID=14056090
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP04092502A Expired - Fee Related JP3109619B2 (en) | 1992-04-13 | 1992-04-13 | Combining device in hydraulic circuit |
Country Status (1)
| Country | Link |
|---|---|
| JP (1) | JP3109619B2 (en) |
-
1992
- 1992-04-13 JP JP04092502A patent/JP3109619B2/en not_active Expired - Fee Related
Also Published As
| Publication number | Publication date |
|---|---|
| JP3109619B2 (en) | 2000-11-20 |
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|---|---|---|---|
| LAPS | Cancellation because of no payment of annual fees |