JPH07502936A - Electrohydraulic control device and pressure reducing valve - Google Patents
Electrohydraulic control device and pressure reducing valveInfo
- Publication number
- JPH07502936A JPH07502936A JP6511699A JP51169994A JPH07502936A JP H07502936 A JPH07502936 A JP H07502936A JP 6511699 A JP6511699 A JP 6511699A JP 51169994 A JP51169994 A JP 51169994A JP H07502936 A JPH07502936 A JP H07502936A
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- JP
- Japan
- Prior art keywords
- control
- pressure
- reducing valve
- piston
- pressure reducing
- 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.)
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Classifications
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
- F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
- F15B11/00—Servomotor systems without provision for follow-up action; Circuits therefor
- F15B11/02—Systems essentially incorporating special features for controlling the speed or actuating force of an output member
- F15B11/028—Systems essentially incorporating special features for controlling the speed or actuating force of an output member for controlling the actuating force
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
- F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
- F15B2211/00—Circuits for servomotor systems
- F15B2211/20—Fluid pressure source, e.g. accumulator or variable axial piston pump
- F15B2211/205—Systems with pumps
- F15B2211/20507—Type of prime mover
- F15B2211/20515—Electric motor
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
- F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
- F15B2211/00—Circuits for servomotor systems
- F15B2211/20—Fluid pressure source, e.g. accumulator or variable axial piston pump
- F15B2211/205—Systems with pumps
- F15B2211/2053—Type of pump
- F15B2211/20538—Type of pump constant capacity
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
- F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
- F15B2211/00—Circuits for servomotor systems
- F15B2211/20—Fluid pressure source, e.g. accumulator or variable axial piston pump
- F15B2211/21—Systems with pressure sources other than pumps, e.g. with a pyrotechnical charge
- F15B2211/212—Systems with pressure sources other than pumps, e.g. with a pyrotechnical charge the pressure sources being accumulators
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
- F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
- F15B2211/00—Circuits for servomotor systems
- F15B2211/30—Directional control
- F15B2211/305—Directional control characterised by the type of valves
- F15B2211/30505—Non-return valves, i.e. check valves
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
- F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
- F15B2211/00—Circuits for servomotor systems
- F15B2211/30—Directional control
- F15B2211/305—Directional control characterised by the type of valves
- F15B2211/30525—Directional control valves, e.g. 4/3-directional control valve
- F15B2211/3053—In combination with a pressure compensating valve
- F15B2211/30535—In combination with a pressure compensating valve the pressure compensating valve is arranged between pressure source and directional control valve
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
- F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
- F15B2211/00—Circuits for servomotor systems
- F15B2211/30—Directional control
- F15B2211/31—Directional control characterised by the positions of the valve element
- F15B2211/3138—Directional control characterised by the positions of the valve element the positions being discrete
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
- F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
- F15B2211/00—Circuits for servomotor systems
- F15B2211/30—Directional control
- F15B2211/32—Directional control characterised by the type of actuation
- F15B2211/327—Directional control characterised by the type of actuation electrically or electronically
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
- F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
- F15B2211/00—Circuits for servomotor systems
- F15B2211/50—Pressure control
- F15B2211/505—Pressure control characterised by the type of pressure control means
- F15B2211/50509—Pressure control characterised by the type of pressure control means the pressure control means controlling a pressure upstream of the pressure control means
- F15B2211/50536—Pressure control characterised by the type of pressure control means the pressure control means controlling a pressure upstream of the pressure control means using unloading valves controlling the supply pressure by diverting fluid to the return line
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
- F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
- F15B2211/00—Circuits for servomotor systems
- F15B2211/50—Pressure control
- F15B2211/52—Pressure control characterised by the type of actuation
- F15B2211/528—Pressure control characterised by the type of actuation actuated by fluid pressure
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
- F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
- F15B2211/00—Circuits for servomotor systems
- F15B2211/50—Pressure control
- F15B2211/55—Pressure control for limiting a pressure up to a maximum pressure, e.g. by using a pressure relief valve
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
- F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
- F15B2211/00—Circuits for servomotor systems
- F15B2211/60—Circuit components or control therefor
- F15B2211/615—Filtering means
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
- F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
- F15B2211/00—Circuits for servomotor systems
- F15B2211/70—Output members, e.g. hydraulic motors or cylinders or control therefor
- F15B2211/705—Output members, e.g. hydraulic motors or cylinders or control therefor characterised by the type of output members or actuators
- F15B2211/7051—Linear output members
- F15B2211/7053—Double-acting output members
Landscapes
- Engineering & Computer Science (AREA)
- Physics & Mathematics (AREA)
- Fluid Mechanics (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Fluid-Pressure Circuits (AREA)
- Control Of Fluid Pressure (AREA)
- Servomotors (AREA)
- Multiple-Way Valves (AREA)
Abstract
Description
【発明の詳細な説明】 電気流体圧式制御装置及び減圧弁 本発明は、請求の範囲第1項の前提部による電気流体圧式制御装置と共に請求の 範囲第8項の前提部による直接制御減圧弁に関する。[Detailed description of the invention] Electrohydraulic control device and pressure reducing valve The present invention comprises an electrohydraulic control device according to the preamble of claim 1 as well as Relating to a directly controlled pressure reducing valve according to the preamble of scope item 8.
工作機械たとえば自動旋盤の保持取付具内の加工品の固定を確実にするように、 工作機械の制御システムは、所要の締付は圧力が得られると肯定応答信号を又は 締付11圧力が所要の値より低いと誤り信号をこの工作機械に送る。締付は圧力 に達しないと、肯定応答信号は現われない、締(1if圧力は、先ず調整し次い で供給圧力に関係なく減圧弁を介し自動的に保持する。この締付は圧力の圧力値 は減圧弁における各要求に合うように調整する。To ensure the fixation of workpieces in holding fixtures of machine tools, e.g. automatic lathes, The machine tool control system issues an acknowledgment signal or an acknowledgment signal when the required tightening pressure is achieved. If the clamping 11 pressure is lower than the required value, an error signal is sent to the machine tool. Tightening is pressure If the pressure is not reached, the acknowledgment signal will not appear. is automatically maintained via the pressure reducing valve regardless of the supply pressure. This tightening is the pressure value of the pressure is adjusted to meet each requirement at the pressure reducing valve.
互いに異なる加工品又はこれ等の加工品を構成する互いに異なる材料は、互いに 異なる締付は圧力を必要とする。Different processed products or different materials constituting these processed products are different from each other. Different tightening requires pressure.
ドイツ国)J、ルバ・ソファ市D−7012のへりオン・ベルヶ(Herion W crke) K Gの86年5月2日付刊行の出版物7501614号に は、保持取付具に通ずる各機器管路には、締付は圧力の変るときに新たな締付は 圧力に再調整しなければならない別個の調整できる圧力スイッチをV;A11I +させである。このことは安全上の危険がある。その理由は、圧力スイッチの正 しい調整は時に無視され又は不正確に実施されることが多いからである。前記の 同じ刊行物には、この安全上の危険をなくすように圧力スイッチを減圧弁に一体 化する手段を記載しである。この圧力スイッチの調整は、減圧弁の調整を変えた ときに自動的に適応できる0問題の減圧弁は、両方の機器管路に共通のシャツト ル弁を介し、作用を受けた各機器管路からパイロット圧力を供給した間接制御減 圧弁である。Herion Belga (Germany) J, Luba Sofa City D-7012 W crke) KG Publication No. 7501614 dated May 2, 1986 For each equipment line leading to the retaining fitting, the tightening will be replaced by a new tightening when the pressure changes. A separate adjustable pressure switch that must be readjusted to the pressure V;A11I +Let's do it. This poses a safety risk. The reason is that the pressure switch This is because correct adjustments are sometimes ignored or performed incorrectly. the above The same publication states that the pressure switch should be integrated into the pressure reducing valve to eliminate this safety hazard. This section describes the means for converting the data. This pressure switch adjustment changed the pressure reducing valve adjustment A zero-problem pressure reducing valve, which can sometimes automatically adapt, is installed on a common shirt shirt for both equipment lines. Indirectly controlled reduction by supplying pilot pressure from each affected equipment line through a double valve. It is a pressure valve.
DE−C−3532592号明細書には、自体のばねの作用を受け計測ピストン として作用し圧力に無関係に圧力スイッチを作動する別個のポット形ピストンを 制御ピストンのほかに設けた直接制御減圧弁について記載しである。DE-C-3532592 discloses that the measuring piston is actuated by its own spring. A separate pot-shaped piston that acts as a pressure switch and operates the pressure switch independently of pressure. A direct control pressure reducing valve provided in addition to the control piston is described.
DE−C−3039002号明細書には、この場合別個の絞りピストンを2個の 圧力スイッチを作動する計測ピストンとして制御ピストンのほかに設けた電気流 体圧式制御装置内の直接制御減圧弁について記載しである。DE-C-3039002 discloses that in this case two separate throttle pistons are used. An electric current installed in addition to the control piston as a measuring piston that activates the pressure switch. A direct control pressure reducing valve in a body pressure control device is described.
絞りピストンは2個のばねにより中央に位置させる。パイロット圧力は、この減 圧弁の出口から誘導する。The throttle piston is centered by two springs. The pilot pressure is Directed from the outlet of the pressure valve.
DE−C−3204055号明細書から知られている、工作機械部品用の電気流 体圧式制御装置に設けた間接制御減圧弁では、圧力スイッチは減圧弁の制御ピス トンのパイロット弁により作動する。制御ピストンとパイロット弁の閉鎖部材と に対するパイロット圧力は、@機器管路に共通のシャツトル弁を介し直接制御弁 を経て作用を受ける機器管路から誘導される。Electric current for machine tool parts as known from DE-C-3204055 In an indirect control pressure reducing valve installed in a body pressure control device, the pressure switch is connected to the pressure reducing valve's control piston. Operated by a ton pilot valve. control piston and pilot valve closing member; The pilot pressure for It is guided from the equipment conduit where it is acted upon.
DE−C−2310193号明細書から知られている、工作機械部品用の電気流 体圧式制御装置に設けた減圧弁では、制御ばね及びパイロット圧力の作用を受け る制御ピストンは、受ける圧力に応答して制御ばねのカに無関係に調整され計測 ピストンとして作用し圧力スイッヂを作動する補助ピストンの内部に配置しであ る。この制御ピストンに対するパイロット圧力は減圧弁の下流鋼に配置した方向 制御弁の上流側で誘導されるが、補助ピストン及び圧力スイッチに対する切換え 圧力は作用を受ける機器圧力管路がらパイロット管路及び予備張力を加久た逆止 め弁を介して誘導する。安全に機能するために、逆止め弁を備えた2本のパイロ ット管路と放出穴を持つ1本の共通の漏れ管路とが必要である。これ等の付加的 部品により、一方では構造上の費用が増し、又他方ではこれ等の部品は安全機能 に関して付加的な潜在的な誤差の源になる。この減圧弁は、複雑であり多(の部 品から成る。Electric current for machine tool parts as known from DE-C-2310193 The pressure reducing valve installed in the body pressure control device is affected by the control spring and pilot pressure. The control piston is adjusted and measured in response to the pressure it is subjected to, independent of the force of the control spring. It can be placed inside the auxiliary piston that acts as a piston and operates the pressure switch. Ru. The pilot pressure for this control piston is in the direction placed on the downstream steel of the pressure reducing valve. Induced upstream of the control valve, but switching to the auxiliary piston and pressure switch Pressure is applied to equipment pressure lines, pilot lines and non-return checks with increased pre-tension. Induction through a valve. Two pyros equipped with check valves for safe functioning A common leakage line with a cut line and a discharge hole is required. These additional On the one hand, these components increase the construction cost, and on the other hand, these components do not have a safety function. is an additional potential source of error. This pressure reducing valve is complex and has many parts. consisting of goods.
本発明の目的は、前記したような電気流体圧式制御装置と共に、その他の制御装 置のうちでこのような制御装置に使うようにした直接制御減圧弁を提供しようと するにある。前記の電気流体圧制御装置及び減圧弁は、構造的に簡単であるが、 なお目標とする安全機能に関して信頼性が極めて高く少数の個別部品だけから成 り、潜在的な誤差の源の数を低減できる。この減圧弁は又、圧力スイッチ手段に より圧力を監視する他の制御装置と組合せて普遍的に使用できるようにしである 。An object of the present invention is to provide an electro-hydraulic control device as described above as well as other control devices. We have attempted to provide a direct control pressure reducing valve for use in such a control device at home. There is something to do. The electrohydraulic pressure control device and pressure reducing valve described above are structurally simple, but Furthermore, it is highly reliable with respect to the target safety function and consists of only a small number of individual parts. can reduce the number of potential sources of error. This pressure reducing valve also serves as a pressure switch means. Can be used universally in combination with other pressure monitoring devices .
本発明によればこの目的は、請求の範囲第1項に述べる構成と共に並記の請求の 範囲としてあげた請求の範囲第8項に述べた構成により達成できる。According to the present invention, this object is achieved by the configuration stated in claim 1 as well as the concomitant claims. This can be achieved by the configuration described in claim 8 listed as the scope.
請求の範囲第1項による電気流体圧式制御装置では、パイロット圧力は方向制御 弁内で直接l1lI造的に簡単に取出され、方向制御弁により機器管路を所期の ように減圧弁の出口に連結するだけでこのようになる。方向制御弁はその正しい 機能に関してもはや別個に監視する必要がなくなり、そして各別のパイロット管 路、シャツトル弁又は逆止め弁も同様に設けないで済ませることができる。この 制御弁は、簡単で少数の部品から成っている。In the electrohydraulic control device according to claim 1, the pilot pressure is used for directional control. Directly inside the valve, it is easy to take out the device, and the directional control valve allows the equipment line to be routed to the desired location. Just connect it to the outlet of the pressure reducing valve like this. directional control valve is that correct Functions no longer need to be monitored separately and each separate pilot tube ducts, shuttle valves or check valves can likewise be dispensed with. this Control valves are simple and consist of a few parts.
この方向制御弁が所期のように機能すれば圧力スイッチ手段を作動するだけであ るから、安全機能の信頼性が高い、減圧弁の調整を変えるときは、この圧力スイ ッチ手段はすぐに減圧弁と共に新たな要求にIN!!!することができる。方向 制御弁が作動過程に固着し監視された制御位置を正確に占めることができなくな ると、減圧弁に対し、又圧力スイッチ手段も応答させるパイロット圧力を生ずる 。圧力スイッチ手段は、肯定応答信号を供給しないか又は誤り信号を供給し、警 報が5久られ又は損傷を防ぐ手段が取られる。パイロット圧力は、保持取付具の 適当な供給が高い信頼性のもとに保証されるような程度に方向制御弁が変位する までは圧力取出し点から誘導されない、この場合方向制御弁の残りの変位はなお 生ずる。保持取付具の締付は圧力は最も重要な安全基準であるから、保持取付具 の緊張用の機器管路に作用するだけで供給圧力の低減のためのパイロット圧力を 誘導するのがよい、しかし保持取付具を解放するには圧力低減を行わないで供給 圧力を使う、このために他の機器管路をパイロット圧力は誘導しないで方向制御 弁を介し減圧弁の出口に連結し、この場合この減圧弁が完全に開き制御作用は行 わないようにする。If this directional control valve functions as intended, it will only actuate the pressure switch means. This pressure switch provides a reliable safety function when changing the adjustment of the pressure reducing valve. The switch means immediately responds to new demands with the pressure reducing valve! ! ! can do. direction The control valve becomes stuck in the operating process and cannot accurately occupy the monitored control position. This creates a pilot pressure for the pressure reducing valve and also for the pressure switch means to respond. . The pressure switch means either does not provide an acknowledgment signal or provides an error signal and 5. If the damage has been reported for a long time, or measures are taken to prevent damage. The pilot pressure is The directional control valve is displaced to such an extent that adequate supply is reliably guaranteed. up to the pressure take-off point, in which case the remaining displacement of the directional valve is still arise. Since pressure is the most important safety criterion when tightening holding fittings, The equipment for tensioning the pilot pressure for the reduction of the supply pressure only acting on the pipe line. It is better to induce, but to release the holding fixture, supply without pressure reduction. Pressure is used to control the direction of other equipment lines without inducing pilot pressure. It is connected to the outlet of the pressure reducing valve through a valve, in which case the pressure reducing valve is fully opened and no control action is performed. Make sure not to
請求の範囲第8項による方向制御減圧弁は、タペットを介し制御ピストンにより 直接作動されるから、少数の個別の部品、コンパクトな構造及び高い信頼性を特 徴とする。減圧弁の制御ばわの調整を変えるときは、圧力スイッチ手段を別個に 再調整する必要がない、安全機能に必要な圧力スイッヂ手段の応答がパイロット 圧力により制御ピストンを変位させる方式に関係なく又制御ピストンを変位させ るパイロット圧力の性質に関係なく保証されるので、圧力スイッチ手段によって 監視する圧力としてパイロット圧力を利用できる場合に流体圧制御装置に対し減 圧弁を普遍的に使用することができる。The directional pressure reducing valve according to claim 8 is provided by a control piston via a tappet. Because it is directly actuated, it features a small number of individual parts, compact construction and high reliability. be a sign. When changing the adjustment of the pressure reducing valve control, use the pressure switch means separately. The response of the pressure switch means required for the safety function is piloted without the need for readjustment. Regardless of the method of displacing the control piston by pressure, is guaranteed regardless of the nature of the pilot pressure used by the pressure switch means. Reduced pressure for fluid pressure controllers when pilot pressure is available as the pressure to monitor. Pressure valves can be used universally.
請求の範囲第2項により適宜の実施例を記載しである。制御ピストン及び圧力ス イッチ手段の間の運動伝達連結に基づいて、圧力スイッヂ手段が制御ピストンの 運動又は位置に直接応答するので安全機能は信頼性の高いままになっている。Appropriate embodiments are described in the second claim. control piston and pressure Based on the motion transmission connection between the switch means, the pressure switch means The safety function remains reliable because it responds directly to movement or position.
請求の範囲第3項による手段は、方向制御弁の中間位置及び又は中央位置におい てパイロット圧力が発生しないでこれに反し潜在的に存在する圧力の低下も生ず ることを保証する。圧力を逃がす最も簡単な方法は戻し管路への連結である。The means according to claim 3 is provided in the intermediate and/or central position of the directional control valve. Therefore, no pilot pressure is generated and, conversely, there is no potential pressure drop. We guarantee that The simplest way to relieve pressure is to connect to a return line.
請求の範囲第4項による実施例では、ケーシング内に制御通路を設けた低価格の 4/2方又は4/3方滑り弁を使う、前記制御通路の口は、機器圧力取出し点の 一部を形成する。この圧力取出し点に適応するのに、方向制御弁の基本的考え方 を変更する必要はない、必要に応じ圧力取出し点は一方の機器管路だけに又は両 方の機器管路に対し使うことができる。前者の場合に機器管路は栓により非作動 にすることができる。An embodiment according to claim 4 provides a low-cost construction with a control passage in the casing. Using a 4/2-way or 4/3-way slide valve, the mouth of the control passage should be located at the equipment pressure take-off point. form part of The basic concept of directional control valves is necessary to adapt to this pressure takeoff point. There is no need to change the It can be used for both equipment lines. In the former case, the equipment line is deactivated by the stopper. It can be done.
請求の範囲第5項による実施例では滑りピストンに。In the embodiment according to claim 5, it is a sliding piston.
各制御位置において又は1個所の制御位置だし−5で圧力を取出すように切削に より形成した縦方向通路を設けである。この縦方向通路の構造及び配置により、 パイロット圧力は中間位置では誘導されなくて又方向制御弁を所期のように開い た場合に圧力スイッチ手段が信号を生ずるだけであることが保証される。m器管 路の付加的監視は行わな(て済む。Cutting to take out pressure at each control position or at one control position -5 A vertical passageway formed by the above is provided. Due to the structure and arrangement of this longitudinal passage, Pilot pressure is not induced in the intermediate position and does not open the directional control valve as expected. It is ensured that the pressure switch means will only generate a signal if the m organ No additional monitoring of the road is required.
請求の範囲第6項による実施例では、溜め連結部に通ずる横方向満尺を介し直接 圧力逃がしを保証できる。圧力取出し点を使わない場合は溜め連結部を閉じる。In an embodiment according to claim 6, it is possible to directly Pressure relief can be guaranteed. Close the sump connection when the pressure take-off point is not in use.
前記間を節約し短い低損失の流路を形成するようにスイッチ手段と共に共通のコ ンパクトなケーシング内に配置すればよい。A common common connector is used with the switching means to save time and form a short, low-loss flow path. It can be placed inside a compact casing.
請求の範囲第7項による手段は、各流路が常に所定の方式で開き又閉じることを 保証するのに重要である。戻り止め手段は、ttt流の供給が途絶えた場合に滑 りピストンを制御位置に保持し、保持取付具がすぐには解放されないようにする 。戻り止め手段が所期のようにgt錠したかどうかを2つの検知装置によって監 視し方向制御弁の正しい切換えを表わす信号を取出すようにすることが考えられ る。このことは、パイロット圧力を圧力取出し点を介してでなく減圧弁の若干の 他の点で取出す場合の実施例に適している1作動磁石又は滑りピストンは変位ピ ックアップ装置により交互に監視できる。The means according to claim 7 ensures that each channel always opens and closes in a predetermined manner. Important to ensure. The detent means is designed to prevent slipping if the supply of ttt flow is interrupted. to hold the piston in a controlled position and prevent the retaining fixture from releasing too quickly. . Two detection devices monitor whether the detent means locks as intended. It may be possible to output a signal indicating correct switching of the directional control valve. Ru. This means that the pilot pressure is not routed through the pressure take-off point, but at some point at the pressure reducing valve. 1 actuating magnet or sliding piston suitable for the embodiment in case of removal at other points Can be monitored alternately by backup device.
請求の範囲第9項による減圧弁の実施例は、圧力スイッチを制御ピストンにより 直接作動するという利点がある。減圧弁は少数の各別の部品だけから成り密実な 構造を持つ。An embodiment of the pressure reducing valve according to claim 9 provides that the pressure switch is controlled by a control piston. It has the advantage of being directly actuated. Pressure reducing valves are compact and consist of only a few separate parts. Has a structure.
請求の範囲第10項記載の実施例では、制御ピストンの運動又は位置はタペット を介し圧力スイッチタペットに機械的に伝える。まわりの圧力に応答しないで制 御ピストンの各変位に従って、タペットは制御ピストンにより変位する。圧力ス イッチは横方向に配置することができ、この場合減圧弁はコンパクトな構造寸法 にすることができ圧力スイッチは正確に調整することができる。In an embodiment according to claim 10, the movement or position of the control piston is controlled by the tappet. Mechanically transmits the pressure to the tappet via the pressure switch. control without responding to surrounding pressure. According to each displacement of the control piston, the tappet is displaced by the control piston. pressure The switch can be arranged laterally, in which case the pressure reducing valve has compact construction dimensions. The pressure switch can be adjusted accurately.
ばね又はばね構造の累進的特性によって請求の範囲第11項による実施例では、 圧力スイッチの切換え点において、たとえば減圧弁の出口で圧力が生成するとき 又は供給割合を変えるときに最小許容圧力鎖が得られる。In the embodiment according to claim 11, due to the progressive nature of the spring or spring structure: At the switching point of a pressure switch, for example when pressure is generated at the outlet of a pressure reducing valve Or the minimum permissible pressure chain is obtained when changing the feed rate.
請求の範囲第12項による実施例では、運動を伝える構造的に簡単なモードが得 られる。ばねによる衝合によって結合が行われるから普通の制御ピストンを使う ことができる。In the embodiment according to claim 12, a structurally simple mode of transmitting the movement is obtained. It will be done. A common control piston is used since the connection is made by spring abutment. be able to.
請求の範囲第13項による実施例では、作用を及ぼす各機器管路から直接又は減 圧弁で直接パイロット圧力を誘導する。減圧弁は又、パイロット圧力が機器管路 に通ずる作用路から誘導されない場合に他の作動モードに使うことができる。In the embodiment according to claim 13, the Pilot pressure is directly induced by a pressure valve. Pressure reducing valves also allow pilot pressure to flow through equipment lines. It can be used for other modes of operation if it is not guided from the working path leading to the
請求の範囲第14項による実施例は、所要の各通路を連結し又他の通路を閉じる ことにより種々の作動モードに普遍的に適合させることができる。The embodiment according to claim 14 connects each of the required passages and closes the other passages. This allows universal adaptation to various operating modes.
以下本発明の主題の各実施例を添付図面により説明する。Embodiments of the subject matter of the present invention will be described below with reference to the accompanying drawings.
第1図は本発明による電気流体圧式制御装置のブロック図である。FIG. 1 is a block diagram of an electrohydraulic control device according to the present invention.
第2図及び第3図はそれぞれ本発明による減圧弁を示す第3図のI I−I I 線及び第2図のIII−III線に沿う断面図である。FIGS. 2 and 3 are I-I in FIG. 3 showing a pressure reducing valve according to the present invention, respectively. FIG. 3 is a cross-sectional view taken along line III--III of FIG. 2;
第4図、第5図及び第6図はそれぞれ本発明による方向制御弁を示しIV−IV 線、V−V線及びVI−VI線に沿う断面図である。4, 5 and 6 each show a directional control valve according to the invention IV-IV FIG.
第7図は本発明減圧弁の一変形の断面図である。FIG. 7 is a sectional view of a modification of the pressure reducing valve of the present invention.
第8図は本発明減圧弁の他の変形の断面図である。FIG. 8 is a sectional view of another modification of the pressure reducing valve of the present invention.
第1図による電気流体圧式制御装置Sは、工作機械部品にたとえば自動旋盤の保 持取付具の複動流体圧シリンダの安全監視作動を行うのに使う、伝動機Mにより 駆動する空気冷却の定容量形ポンプ1は、溜め2から流体媒体を吸引し、圧力貯 蔵手段4に圧力管路3を経て圧力制限弁を介し充填する。減圧弁Vに通ずる管路 3aは圧力管路3から技分かれする。戻し管路5aは減圧弁Vから戻し管路5に 又溜め2に通ずる。圧力スイッチ手段りは減圧弁■に構造的に連結しである。減 圧弁Vの出口側は、管路6を介し方向制御弁Wにすなわち4/2方滑り弁に連結 しである。この制御弁から戻し管路5bが戻し管路5に通ずる(方向制御弁Wの 連結部P、T)、方向制御弁Wの出口側は機器管路11、12を介し工作機械部 品にに連結しである(連結部A、B)、方向制御弁Wには機器圧力取出し点Z( 方向制御弁Wの標識内に概略的に示しである)を設けである。取出し点Zは、パ イロ・ノド管路7を介し減圧弁Vの制御入力20に連結しである。方向制御弁W は、2個の作動磁石9、10により2つの制御位置a、bの間で切換えるように しである滑りピストン8を有する。2つの制御位置の間の中間位置で、圧力取出 し点Zは戻し管路5bに連結され、パイロット管路7が零圧力になる。The electrohydraulic control device S according to FIG. By the transmission M used to perform the safety monitoring operation of the double-acting hydraulic cylinder of the holding fixture. A driven air-cooled constant displacement pump 1 sucks fluid medium from a reservoir 2 and creates a pressure reservoir. The storage means 4 is filled via the pressure line 3 via the pressure limiting valve. Pipe line leading to pressure reducing valve V 3a separates from the pressure pipe 3. The return pipe 5a is connected from the pressure reducing valve V to the return pipe 5. It also leads to reservoir 2. The pressure switch means is structurally connected to the pressure reducing valve. decrease The outlet side of the pressure valve V is connected to a directional control valve W, that is, a 4/2-way sliding valve, via a pipe 6. It is. A return line 5b leads from this control valve to the return line 5 (direction control valve W). connection parts P, T) and the outlet side of the directional control valve W are connected to the machine tool part via equipment pipes 11 and 12. The directional control valve W has an equipment pressure take-off point Z (connection parts A and B). (schematically shown in the markings of the directional control valve W). Take-out point Z is It is connected to a control input 20 of a pressure reducing valve V via a line 7. Directional control valve W is switched between two control positions a and b by two operating magnets 9 and 10. It has a sliding piston 8. Pressure take-off at intermediate position between two control positions The point Z is connected to the return line 5b, and the pilot line 7 becomes zero pressure.
減圧弁Vの構造は第2図及び第3図(第1実施例)に詳細に説明しである。減圧 弁Vは、出口を連結する2つの制御縁部15を持つ制御ピストン14をケーシン グ穴13内に含む、出口は管路6に連結され、この出口の開口18は、ケーシン グ穴13を出口6内の特定の圧力を調整するように圧力連結部19(戻し管路3 8に連結しである)と溜め連結部17(戻し管路5aに連結しである)とに交互 に交差させる。制御ピストン14は、制御入口20で送給されるパイロット圧力 により作用を受けるようにしたピストン端部16を持つ、ピストン端部16は、 圧力から解放される室28内に配置したばね22の力に対向する作用を受ける。The structure of the pressure reducing valve V is explained in detail in FIGS. 2 and 3 (first embodiment). Decompression The valve V casing a control piston 14 with two control edges 15 connecting the outlets. The outlet contained in the casing hole 13 is connected to the conduit 6, and the opening 18 of this outlet is connected to the conduit 6. The pressure connection 19 (return line 3 8) and the reservoir connecting portion 17 (connected to the return pipe 5a). to cross. Control piston 14 receives pilot pressure delivered at control inlet 20 The piston end 16 has a piston end 16 adapted to be acted upon by It is counteracted by the force of a spring 22 placed in a chamber 28 which is relieved of pressure.
ばね22の付勢力は調整されるようにしである。ばね22は、ばね衝合体23を 介し制御ピストン14に作用する。ばね衝合体23には、タペット26の頭部2 7に能動的にはまり合う満24を設けである。タペット26は、ケーシング穴1 3に平行に延びる穴25内で変位するようにしである。タペット26は運動伝達 自在にばね衝合体23を介し制御ピストン14に機械的に連結しである。タペッ ト26は、押圧タペット28に整合する。タペット28は穴25を越えて突出し 、穴25に対し密封され圧力スイ・ノチ手段りの圧力スイッチ29を作動するの に使うようにしである。The biasing force of the spring 22 is adjusted. The spring 22 connects the spring abutment body 23 via which it acts on the control piston 14. The head 2 of the tappet 26 is attached to the spring abutment 23. 7 is provided with a filler 24 that is positively engaged. The tappet 26 is the casing hole 1 3 and is adapted to be displaced within a hole 25 extending parallel to the 3. Tappet 26 transmits motion It is mechanically coupled to the control piston 14 via a spring abutment 23 at will. Tape The tappet 26 is aligned with the pressure tappet 28. Tappet 28 projects beyond hole 25 , actuating a pressure switch 29 sealed against the hole 25 and having a pressure switch notch means. It is intended to be used for
2条の通路30.32は、連結通路33を介し制御入口20に連結しである。通 路30は、開口18に引続いて通路33に交差する0通路32は、減圧弁Vの外 側に設けられパイロット管路7を連結するようにした連結部7゛に通じている0 図示の実施例では通路30は、開口18及び通路33間の栓によりふさがれねじ 栓31により外側に対し密封しである。しかし連結部7′は開いておりパイロッ ト管路7に連結しである。連結部7゛を閉じると、開口18に通ずる連結部が開 かれ、出口6からのパイロット圧力が制御入口20に加わる。連結部7′には又 、2本の機器管路11.12の高い方の検器圧力をシャツトル弁を介し受けるパ イロット管路を連結しである。The two passages 30,32 are connected to the control inlet 20 via a connecting passage 33. General The passage 30 intersects the passage 33 following the opening 18, and the passage 32 crosses the passage 33 outside the pressure reducing valve V. 0 connected to a connecting part 7' provided on the side and connecting the pilot pipe 7. In the illustrated embodiment, the passageway 30 is closed by a plug between the opening 18 and the passageway 33 and is threaded. It is sealed from the outside by a stopper 31. However, the connecting part 7' is open and the pilot It is connected to the top pipe line 7. When the connecting part 7' is closed, the connecting part leading to the opening 18 is opened. The pilot pressure from the outlet 6 is then applied to the control inlet 20. There is also a connection part 7'. , a pipe which receives the higher pressure of the two instrument lines 11 and 12 via the shuttle valve. Connect the pilot pipes.
ばね22は累進的(非線形)特性を持つばね構造を持つ、このために段階的に有 効になる複数個のばね又は互いに異なる巻き区間を備えた1個のばねを設けるこ とができる。累進的ばね特性は、増大する供給割合又はむしろ増大する作用圧力 によって圧力スイッチ29の切換え圧力が作用圧力に近づくという利点がある。The spring 22 has a spring structure with progressive (non-linear) characteristics, so that the spring It is possible to provide several active springs or one spring with different winding sections. I can do it. The progressive spring characteristic is characterized by an increasing supply rate or rather an increasing working pressure. This has the advantage that the switching pressure of the pressure switch 29 approaches the operating pressure.
第4図、第5図及び第6図によれば方向制御弁は、滑りピストン用穴34内で移 動できるように案内され、穴34に対し密封した滑りピストン8を備えている。According to FIGS. 4, 5 and 6, the directional control valve is moved in the bore 34 for the sliding piston. It is provided with a sliding piston 8 which is movably guided and sealed against the bore 34.
滑りビス]・ン8はタペット37により交互に移動するようにしである。タペッ ト37は作動磁石9、10により移動する。戻り止め手段36は滑りピストン3 5の2つの制御位置を機械的に確保する。減圧弁Vの出口6に連結した人口38 は、滑りピストン用穴34の中央に位置させである。旋削により形成した溝の形 の出口39.40は、入口38の両側に配置しである。溜め連結部43、Tは、 入口38から遠ざかる方に向いた各出口39.40の側に設けである。戻し管路 5b(第1図)は溜め連結部43、Tに連結しである1円筒形密封区間42を設 けた滑りピストン8には、直径に沿い互いに対向する流れポケット41を形成し である。各ポケット41は、滑りピストン8の内部に連結され入口38を各制御 位置で出口39又は出口40に連結するが、他方の出口40.39は隣接する溜 め連結部43に滑りピストン8の狭めた部分35を介し連結される。滑りピスト ン8の一方の側に1つの流れポケット41を設ければ十分である。圧力補正によ り又滑りピストン8の平滑走行によって、直径に沿い互いに対向する流れポケッ ト41が役立つ。The sliding screws 8 are arranged to be alternately moved by a tappet 37. Tape The shaft 37 is moved by actuating magnets 9 and 10. The detent means 36 is the sliding piston 3 Mechanically secure the two control positions of 5. Population 38 connected to outlet 6 of pressure reducing valve V is located at the center of the sliding piston hole 34. Groove shape formed by turning The outlets 39,40 are located on either side of the inlet 38. The reservoir connecting portion 43, T is It is provided on the side of each outlet 39,40 facing away from the inlet 38. return line 5b (FIG. 1) is a reservoir connecting portion 43, which is connected to T and has one cylindrical sealed section 42. The girder-sliding piston 8 is formed with flow pockets 41 diametrically opposed to each other. It is. Each pocket 41 is connected to the interior of the sliding piston 8 and controls each inlet 38. outlet 39 or outlet 40, the other outlet 40.39 connects to the adjacent reservoir. The sliding piston 8 is connected to the connecting part 43 via the narrowed part 35 of the sliding piston 8. sliding piste It is sufficient to provide one flow pocket 41 on one side of the tube 8. By pressure compensation Also, due to the smooth running of the sliding piston 8, flow pockets opposite each other along the diameter are formed. 41 is helpful.
直径に沿い互いに対向する2条の縦方向通路44(切削により密封区間42に形 成した?11I)は円周方向に形成しである。縦方向通路44は、流れポケット 41に対して移動、斜めの貫通穴48により相互に連結しである。Two diametrically opposed longitudinal passages 44 (shaped into sealed sections 42 by cutting) Did it happen? 11I) is formed in the circumferential direction. The longitudinal passage 44 is a flow pocket. 41, and are interconnected by diagonal through holes 48.
滑りピストン用穴34の制御通路口45は、縦方向通路44のうちの1つ(第5 図の低い方の通路)に連通している。制御通路口45は制御通路51の一部(パ イロット管路7に連結した)を形成する0反対側の縦方向通路44は横方向溝穴 49に交差する。溝穴49は、滑りピストン8の運動中に溜め通路50の溜め連 結部46を越え、次いで縦方向通路44及び戻し管路5b(第1図)の間に流れ 連結部を生成する。パイロット管路7は前記流れ連結部を介し圧力から解放され る。溜め連結部46は縦方向通路44に対し側方に移動し、横方向溝穴49だけ が溜め連結部46を越えるようにする。The control passage opening 45 of the sliding piston hole 34 is connected to one of the longitudinal passages 44 (the fifth (lower passage in the figure). The control passage port 45 is a part (part) of the control passage 51. The longitudinal passage 44 on the opposite side forms a transverse slot (connected to the pilot pipe 7). Intersect with 49. The slot 49 provides a reservoir connection in the reservoir passage 50 during movement of the sliding piston 8. The flow passes over the junction 46 and then between the longitudinal passage 44 and the return line 5b (FIG. 1). Generate connections. The pilot line 7 is released from pressure via said flow connection. Ru. The sump connection 46 is moved laterally with respect to the longitudinal passage 44 and only the transverse slot 49 so that it exceeds the reservoir connection part 46.
第4図ないし第6図は、滑りピストン8をその中央位lbで示す、この中央位置 では、出口40は入口38に連結されるが、出口39は溜め連結部43に連結さ れる。機器管路12内の圧力は、パイロット圧力として中央通路口45に加わり 、この圧力がパイロット管路7を介し減圧弁(第1図)の制御入力路20に送ら れるようにする。溜め連結部46への連結部は、横方向溝穴49(第5図)が溜 め連結部のそばにその右側に位置するために存在しない、又一方では機器管路1 2間の正しい圧力はこのようにしてパイロット圧力として伝達され、他方では又 滑りピストン8が実際上その正しい制御位置すに達していることが保証される。4 to 6 show the sliding piston 8 in its central position lb. , the outlet 40 is connected to the inlet 38 while the outlet 39 is connected to the sump connection 43. It will be done. The pressure in the equipment line 12 is applied to the central passageway port 45 as pilot pressure. , this pressure is sent to the control input line 20 of the pressure reducing valve (Fig. 1) via the pilot line 7. make it possible to do so. The connection to the reservoir connection 46 is provided by a transverse slot 49 (FIG. 5). It is not present because it is located to the right of the connection, and on the other hand the equipment line 1 The correct pressure between the two is thus transmitted as pilot pressure, and on the other hand It is ensured that the sliding piston 8 has virtually reached its correct control position.
滑りピストン8がたとえば戻り止め手段36に対しはまらないで中間位置に固着 すると、制御通路口45は溜めに横方向溝穴49を介し連結され、パイロット圧 力が伝えられない。For example, the sliding piston 8 does not engage against the detent means 36 and is stuck in an intermediate position. The control passageway port 45 is then connected to the reservoir via the transverse slot 49, and the pilot pressure I can't convey my power.
特に重要な態様は、減圧弁の全部の実施例の場合に、減圧弁及び圧力スイッチ手 段りの調整はばね又はばね構造22の付勢力に対し、信号制御部材すなわち調整 ねじにより同期的に変えることができる。A particularly important aspect is that in all embodiments of the pressure reducing valve, the pressure reducing valve and the pressure switch hand Adjustment of the step is performed by a signal control member, that is, adjustment, against the biasing force of the spring or spring structure 22. It can be changed synchronously by screws.
減圧弁■の制御ピストンたとえば第2図のピストン14は、圧力スイッチ29の 計測ピストンとして同時に便宜的に使われる。その理由は、まわりの圧力に応答 して変位できる部材を制御ピストン及び圧力スイッチの間にもはや設けてないか らである。The control piston of the pressure reducing valve ■, for example, the piston 14 in FIG. It is also conveniently used as a measuring piston. The reason is that it responds to the surrounding pressure. Is there no longer a member between the control piston and the pressure switch that can be displaced by It is et al.
第7図による実施例では、減圧弁V°の制御ピストン14°に軸線方向タペット 54を設けである。タペット54は、制御ピストンに取付けられ制御人口20に 隣接して位置し、圧力スイッチ29に整合し、この圧力スイッチ29を作動する のに使う、タペット54はケーシング穴の密封構造を貫いて延びている。この場 合パイロット圧力は出口6から通路30.33を介して誘導する。この通路を閉 じると、制御人口20は図示のように又第1図の圧力取出し点Zに、又は直接シ ャツトル弁を介し2本のII器管路11.12に連結しである。In the embodiment according to FIG. 7, an axial tappet is provided on the control piston 14° of the pressure reducing valve V°. 54 is provided. A tappet 54 is attached to the control piston and connected to the control valve 20. located adjacent to and aligned with the pressure switch 29 to actuate the pressure switch 29; A tappet 54 extends through the sealing structure of the casing bore. this place The combined pilot pressure is conducted from the outlet 6 via the passage 30.33. close this passage 1, the control mass 20 is then connected to the pressure take-off point Z of FIG. 1 or directly to the system as shown. It is connected to two II vessel lines 11 and 12 via a shuttle valve.
第8図による減圧弁V”の実施例ではタペット26゜は、第2図の場合と同様に ばね衝合体を介し制御ピストン14に運動を伝達するように結合しである。タペ ット26°には、圧力スイッチ29°のカムフォロアアームが衝合するカム面5 6を設けである。このカムフォロアアームは減圧弁V“の−左側で外部に配置さ れ、圧力スイッチ手段りの一部を構成する。In the embodiment of the pressure reducing valve V" according to FIG. 8, the tappet 26° is the same as in FIG. It is coupled to transmit motion to the control piston 14 via a spring abutment. Tape At 26°, there is a cam surface 5 that the cam follower arm of the pressure switch 29° abuts against. 6 is provided. This cam follower arm is located externally on the -left side of the pressure reducing valve V". This constitutes a part of the pressure switch means.
4/2方滑り弁の代りに473方弁を方向制御弁W(第1図に示しである)とし て設けることができる。機器圧力取出し点Zは、これが溜め連結部に連通ずるこ とによって又はこれが戻し管路に連結した機器管路に連通ずることによって、正 しい制御位置(a及び又はb)を除いて解放される。4/3方滑り弁を使うとき は、パイロット圧力用のパイロット管路は中央位置で戻し管路に直接連結される が、両橢器管路は閉塞され又は戻し管路に連結される。パイロット圧力を一方の 制御位置だけで誘導すると、パイロット管路は他方の制御位置で戻し管路に対し ちょうど開口した機器管路に連結され、このパイロット管路が解放する。各別に 又は組合せて取ったこれ等の手段は、固定取付具の優れた制御システムが他の点 で応答する圧力スイッチ手段の正しくない肯定応答信号を除外する作用をする。Instead of the 4/2-way sliding valve, a 473-way valve is used as the directional control valve W (as shown in Figure 1). It can be provided as follows. The device pressure take-off point Z is connected to the sump connecting part. or by communicating with an equipment line connected to the return line. released except for the new control position (a and/or b). When using a 4/3 way sliding valve The pilot line for pilot pressure is connected directly to the return line in a central position. However, both ejector lines are blocked or connected to a return line. Pilot pressure on one side If guided only at the control position, the pilot line will be connected to the return line at the other control position. It is connected to the equipment line that has just been opened, and this pilot line is released. each separately or a combination of these measures, if a good control system of the fixed fixture This serves to filter out incorrect acknowledgment signals of the pressure switch means responding at .
Claims (1)
Applications Claiming Priority (3)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
DE4237901A DE4237901C2 (en) | 1992-11-10 | 1992-11-10 | Electro-hydraulic control device and pressure reducing valve |
DE4237901.6 | 1992-11-10 | ||
PCT/EP1993/003129 WO1994011797A1 (en) | 1992-11-10 | 1993-11-09 | Electro-hydraulic control device and pressure reducing valve |
Publications (2)
Publication Number | Publication Date |
---|---|
JPH07502936A true JPH07502936A (en) | 1995-03-30 |
JP3632927B2 JP3632927B2 (en) | 2005-03-30 |
Family
ID=6472511
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
JP51169994A Expired - Lifetime JP3632927B2 (en) | 1992-11-10 | 1993-11-09 | Electro-hydraulic control device |
Country Status (8)
Country | Link |
---|---|
EP (1) | EP0620932B1 (en) |
JP (1) | JP3632927B2 (en) |
KR (1) | KR100238784B1 (en) |
AT (1) | ATE169132T1 (en) |
DE (1) | DE4237901C2 (en) |
ES (1) | ES2119145T3 (en) |
TW (1) | TW273588B (en) |
WO (1) | WO1994011797A1 (en) |
Families Citing this family (8)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
DE9413273U1 (en) | 1994-08-17 | 1994-10-06 | Heilmeier & Weinlein Fabrik für Oel-Hydraulik GmbH & Co KG, 81673 München | Clamping module for machine tool clamping device |
DE29518705U1 (en) | 1995-11-24 | 1996-01-18 | Heilmeier & Weinlein Fabrik für Oel-Hydraulik GmbH & Co KG, 81673 München | Clamping module |
DE29605911U1 (en) * | 1996-03-29 | 1997-07-24 | Heilmeier & Weinlein Fabrik für Oel-Hydraulik GmbH & Co KG, 81673 München | Electro-hydraulic control device |
DE19637256A1 (en) * | 1996-09-13 | 1998-03-19 | Index Werke Kg Hahn & Tessky | Workpiece spindle device for a machine tool |
DE29808294U1 (en) | 1998-05-07 | 1998-08-13 | Heilmeier & Weinlein Fabrik für Oel-Hydraulik GmbH & Co KG, 81673 München | Electro-hydraulic clamping module |
DE29808295U1 (en) | 1998-05-07 | 1998-08-13 | Heilmeier & Weinlein Fabrik für Oel-Hydraulik GmbH & Co KG, 81673 München | Seat valve |
DE19935473B4 (en) * | 1999-07-13 | 2006-02-02 | Bosch Rexroth Aktiengesellschaft | Hydraulic pressure control valve |
CN103437752B (en) * | 2013-09-12 | 2015-10-21 | 中煤科工集团西安研究院有限公司 | A kind of for the long-range hydraulic control system of coal mine gallery drilling rig |
Family Cites Families (8)
Publication number | Priority date | Publication date | Assignee | Title |
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DE2249743A1 (en) * | 1972-10-11 | 1974-04-18 | Kloeckner Humboldt Deutz Ag | VALVE UNIT |
DE2310193C2 (en) * | 1973-03-01 | 1974-11-21 | Index-Werke Kg Hahn & Tessky, 7300 Esslingen | Safety pressure control valve for setting a constant working pressure |
DE2602844B2 (en) * | 1976-01-27 | 1978-08-17 | Eisenwerk Weserhuette Ag, 4970 Bad Oeynhausen | Electrically controlled pressure control valve |
DE3039002C2 (en) * | 1980-10-15 | 1983-02-10 | Lutz 7306 Denkendorf Leupold | Pressure control valve |
DE3204055C2 (en) * | 1982-02-06 | 1984-06-28 | Lutz 7306 Denkendorf Leupold | Pressure relief or control valve |
DE3532592A1 (en) * | 1985-09-12 | 1987-03-19 | Rexroth Mannesmann Gmbh | 3-WAY PRESSURE REDUCER VALVE WITH SECONDARY PRESSURE MONITORING |
DE3918418A1 (en) * | 1989-04-17 | 1990-10-18 | Rexroth Mannesmann Gmbh | Electrical measurement value acquisition for control valve - using pressure sensors interacting with chamber of holder body, enabling use of standard value |
ES2027502A6 (en) * | 1990-11-19 | 1992-06-01 | Bendix Espana | Fluid pressure regulating valve. |
-
1992
- 1992-11-10 DE DE4237901A patent/DE4237901C2/en not_active Expired - Fee Related
-
1993
- 1993-11-09 WO PCT/EP1993/003129 patent/WO1994011797A1/en active IP Right Grant
- 1993-11-09 JP JP51169994A patent/JP3632927B2/en not_active Expired - Lifetime
- 1993-11-09 AT AT94900117T patent/ATE169132T1/en not_active IP Right Cessation
- 1993-11-09 KR KR1019940701984A patent/KR100238784B1/en not_active IP Right Cessation
- 1993-11-09 ES ES94900117T patent/ES2119145T3/en not_active Expired - Lifetime
- 1993-11-09 EP EP94900117A patent/EP0620932B1/en not_active Expired - Lifetime
- 1993-12-18 TW TW082110756A patent/TW273588B/zh active
Also Published As
Publication number | Publication date |
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JP3632927B2 (en) | 2005-03-30 |
WO1994011797A1 (en) | 1994-05-26 |
DE4237901A1 (en) | 1994-05-11 |
KR100238784B1 (en) | 2000-01-15 |
TW273588B (en) | 1996-04-01 |
DE4237901C2 (en) | 1996-02-01 |
ATE169132T1 (en) | 1998-08-15 |
EP0620932B1 (en) | 1998-07-29 |
ES2119145T3 (en) | 1998-10-01 |
EP0620932A1 (en) | 1994-10-26 |
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