EP0473030A1 - Proportional 4-way seat valve - Google Patents

Proportional 4-way seat valve Download PDF

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Publication number
EP0473030A1
EP0473030A1 EP91113761A EP91113761A EP0473030A1 EP 0473030 A1 EP0473030 A1 EP 0473030A1 EP 91113761 A EP91113761 A EP 91113761A EP 91113761 A EP91113761 A EP 91113761A EP 0473030 A1 EP0473030 A1 EP 0473030A1
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EP
European Patent Office
Prior art keywords
valves
valve
proportional
proportional throttle
seat
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.)
Withdrawn
Application number
EP91113761A
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German (de)
French (fr)
Inventor
Hans Schwelm
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Hydrolux SARL
Original Assignee
Hydrolux SARL
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Filing date
Publication date
Application filed by Hydrolux SARL filed Critical Hydrolux SARL
Publication of EP0473030A1 publication Critical patent/EP0473030A1/en
Withdrawn legal-status Critical Current

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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
    • F15B13/00—Details of servomotor systems ; Valves for servomotor systems
    • F15B13/02—Fluid distribution or supply devices characterised by their adaptation to the control of servomotors
    • F15B13/04—Fluid distribution or supply devices characterised by their adaptation to the control of servomotors for use with a single servomotor
    • F15B13/0401—Valve members; Fluid interconnections therefor
    • F15B13/0402—Valve members; Fluid interconnections therefor for linearly sliding valves, e.g. spool valves
    • 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
    • F15B11/003—Systems with load-holding valves
    • 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
    • F15B11/006—Hydraulic "Wheatstone bridge" circuits, i.e. with four nodes, P-A-T-B, and on-off or proportional valves in each link
    • 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
    • F15B13/00—Details of servomotor systems ; Valves for servomotor systems
    • F15B13/02—Fluid distribution or supply devices characterised by their adaptation to the control of servomotors
    • F15B13/04—Fluid distribution or supply devices characterised by their adaptation to the control of servomotors for use with a single servomotor
    • F15B13/0401—Valve members; Fluid interconnections therefor
    • F15B13/0405—Valve members; Fluid interconnections therefor for seat valves, i.e. poppet valves
    • 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
    • F15B2211/20546—Type of pump variable capacity
    • F15B2211/20553—Type of pump variable capacity with pilot circuit, e.g. for controlling a swash plate
    • 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
    • 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
    • F15B2211/3051—Cross-check valves
    • 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
    • F15B2211/30515—Load holding valves
    • 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
    • F15B2211/3056—Assemblies of multiple valves
    • F15B2211/30565—Assemblies of multiple valves having multiple valves for a single output member, e.g. for creating higher valve function by use of multiple valves like two 2/2-valves replacing a 5/3-valve
    • F15B2211/3057—Assemblies of multiple valves having multiple valves for a single output member, e.g. for creating higher valve function by use of multiple valves like two 2/2-valves replacing a 5/3-valve having two valves, one for each port of a double-acting output member
    • 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
    • F15B2211/3056—Assemblies of multiple valves
    • F15B2211/30565—Assemblies of multiple valves having multiple valves for a single output member, e.g. for creating higher valve function by use of multiple valves like two 2/2-valves replacing a 5/3-valve
    • F15B2211/30575—Assemblies of multiple valves having multiple valves for a single output member, e.g. for creating higher valve function by use of multiple valves like two 2/2-valves replacing a 5/3-valve in a Wheatstone Bridge arrangement (also half bridges)
    • 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
    • F15B2211/315—Directional control characterised by the connections of the valve or valves in the circuit
    • F15B2211/3157—Directional control characterised by the connections of the valve or valves in the circuit being connected to a pressure source, an output member and a return line
    • F15B2211/31576—Directional control characterised by the connections of the valve or valves in the circuit being connected to a pressure source, an output member and a return line having a single pressure source and a single output member
    • 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
    • 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
    • F15B2211/329—Directional control characterised by the type of actuation actuated by fluid pressure
    • 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
    • F15B2211/40—Flow control
    • F15B2211/405—Flow control characterised by the type of flow control means or valve
    • F15B2211/40515—Flow control characterised by the type of flow control means or valve with variable throttles or orifices
    • 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
    • F15B2211/40—Flow control
    • F15B2211/41—Flow control characterised by the positions of the valve element
    • F15B2211/413—Flow control characterised by the positions of the valve element the positions being continuously variable, e.g. as realised by proportional valves
    • 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
    • F15B2211/40—Flow control
    • F15B2211/415—Flow control characterised by the connections of the flow control means in the circuit
    • F15B2211/41581—Flow control characterised by the connections of the flow control means in the circuit being connected to an output member and a return line
    • 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
    • F15B2211/40—Flow control
    • F15B2211/46—Control of flow in the return line, i.e. meter-out control
    • 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
    • F15B2211/50563—Pressure control characterised by the type of pressure control means the pressure control means controlling a differential pressure
    • F15B2211/50572—Pressure control characterised by the type of pressure control means the pressure control means controlling a differential pressure using a pressure compensating valve for controlling the pressure difference across a flow control valve
    • 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
    • F15B2211/515—Pressure control characterised by the connections of the pressure control means in the circuit
    • F15B2211/5151—Pressure control characterised by the connections of the pressure control means in the circuit being connected to a pressure source and a directional control valve
    • 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
    • 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
    • F15B2211/605—Load sensing circuits
    • F15B2211/6051—Load sensing circuits having valve means between output member and the load sensing circuit
    • F15B2211/6054—Load sensing circuits having valve means between output member and the load sensing circuit using shuttle valves
    • 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
    • F15B2211/715—Output members, e.g. hydraulic motors or cylinders or control therefor having braking means
    • 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
    • F15B2211/80—Other types of control related to particular problems or conditions
    • F15B2211/86—Control during or prevention of abnormal conditions
    • F15B2211/8609—Control during or prevention of abnormal conditions the abnormal condition being cavitation
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
    • Y10T—TECHNICAL SUBJECTS COVERED BY FORMER US CLASSIFICATION
    • Y10T137/00—Fluid handling
    • Y10T137/8593—Systems
    • Y10T137/87169—Supply and exhaust
    • Y10T137/87193—Pilot-actuated
    • Y10T137/87209—Electric
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
    • Y10T—TECHNICAL SUBJECTS COVERED BY FORMER US CLASSIFICATION
    • Y10T137/00—Fluid handling
    • Y10T137/8593—Systems
    • Y10T137/87169—Supply and exhaust
    • Y10T137/87233—Biased exhaust valve
    • Y10T137/87241—Biased closed

Definitions

  • the invention relates to a proportional 4-way valve in seat construction, in particular a proportional directional valve with individually controlled 2-way cartridge valves, which are combined into a compact unit by mounting on a common valve housing.
  • proportional and servo valves in a piston valve design are predominantly used as the link between signal processing electronics and the hydraulic power section.
  • valves with a hermetic sealing function are required to ensure position locking and pressure maintenance functions.
  • the leaks caused by the fitting play require additional downstream seat valves at high cost.
  • the proportional valves in the spool design according to the prior art require complex external position control of the spool.
  • FIG. 1 An electrohydraulic drive is shown in FIG. 1, a hydraulic cylinder 4 being selected as an application example as the hydraulic power unit.
  • a hydraulic cylinder 4 In certain areas of application, e.g. in the aforementioned, such a cylinder must be able to be locked in a given position for safety and functional reasons, which is basically done by providing seat valves which prevent the hydraulic fluid from flowing back out of the cylinder chamber into the supply lines ZA and ZB of the cylinder.
  • a proportional 4-way valve 6 essentially consisting of two proportional throttle valves C1 and C3 with integrated spring return which are manufactured by the applicant under the designation DPCMEE 16S8, and two pilot-controlled lowering brake valves C2 and C4 in the seat version, whereby check valves R1 and R3 are assigned to the outputs of valves C1 and C3.
  • valve C1 is opened according to the desired piston speed of the cylinder 4 by its control magnet a, whereby the supply line ZA is supplied with pressure oil via the check valve R1 and the working line connection A of the valve 6.
  • valve C4 is opened via control line X1 for throttled oil return from cylinder port ZB to tank port T of valve 6.
  • valve C1 For stopping the hydraulic cylinder piston 8 in a locked position, the valve C1 is closed, so that the connection ZA now lies on the check valve R1, and the connection ZB on the seat valve C4; The control line X1 is relieved via the valve C1 and the leakage oil return 10 to the tank connection T.
  • valves C3 and C2 are activated in an analogous manner (this via the control line X2), while the locking takes place in a similar manner to that previously described.
  • the lowering brake valves C2 or C4 are opened as far as the proportional valve C1 or C3 specifies via control line X1 or X2, i.e. Valves C1 and C4, or C3 and C2 interact depending on the load pressure, with negative loads they act as a discharge throttle and prevent the load from advancing and cavitation on the inflow side.
  • Each function of the hydraulic cylinder can be controlled and regulated accordingly.
  • the invention provides an option part O upstream of the proportional directional control valve 6 according to the invention, essentially consisting of a compensator K with a pressure connection P 'with a superimposed proportional pressure setting PA, PB, for load-independent flow control.
  • a load pressure tap L (connection LS) for flow rate adjustment is also possible when using a control pump RP.
  • part O only serves to supply energy to the proportional 4-way valve according to the invention.
  • FIG 2 shows a practical embodiment of the new proportional directional control valve in section (without option O from Figure 1).
  • the individual valves C1, C2, C3, C4 are designed as production-optimized screw-in valves for cost reduction and screwed into a common valve housing 12, resulting in a compact and robust valve unit (cartridge technology).
  • the newly developed proportional throttle valves C1, C3 have high dynamics and positioning accuracy due to the integrated spring return between the active cartridge of the main stage for pilot control without additional electrical feedback. Opening and closing times of 40 ms are achieved with 100% signal control and approx. 2% hysteresis.
  • valve arrangement shown can, however, be switched over in the simplest manner to differential operation of the cylinder 4, in which the valves C1 and C3 are opened simultaneously by their control magnets a and b for simultaneous pressurized oil application to the cylinder sides A and B, with a corresponding circuit (not shown) that the seat valves C2 and C4 remain closed and the check valve R3 is deactivated.
  • valves in the seat design provides hermetic tightness and thus maximum operational safety by blocking the cylinder 4 in the event of a power and / or pressure oil failure.

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  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Fluid Mechanics (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Fluid-Pressure Circuits (AREA)
  • Servomotors (AREA)

Abstract

Das Ventil besteht aus zwei Proportional-Drosselventilen (C1, C3) denen austrittseitig ein Rückschlagventil (R1, R3) zugeordnet ist und aus zwei durch die Proportional-Drosselventile vorgesteuerten Sitzventile (C2, C4) welche alle in einem Ventilgehäuse mit genormter Schnittstelle untergebracht sind. Die Proportional-Drosselventile (C1, C3) besitzen eine magnetische Aussteuerung wobei jede Funktion eines Hydraulikzylinders proportional angesteuert und geregelt werden kann. <IMAGE>The valve consists of two proportional throttle valves (C1, C3) to which a check valve (R1, R3) is assigned on the outlet side and two seat valves (C2, C4) pilot-controlled by the proportional throttle valves, all of which are housed in a valve housing with a standardized interface. The proportional throttle valves (C1, C3) have a magnetic control, whereby each function of a hydraulic cylinder can be controlled and regulated proportionally. <IMAGE>

Description

Die Erfindung betrifft ein Proportional-4-Wegeventil in Sitzbauweise, insbesondere ein Proportional-Wegeventil mit einzeln gesteuerten 2-Wege-Einbauventilen, welche durch Montage an einem gemeinsamen Ventilgehäuse zu einer kompakten Einheit zusammengefasst sind.The invention relates to a proportional 4-way valve in seat construction, in particular a proportional directional valve with individually controlled 2-way cartridge valves, which are combined into a compact unit by mounting on a common valve housing.

In elektrohydraulischen Antrieben werden als Bindeglied zwischen signalverarbeitender Elektronik und dem hydraulischen Leistungsteil überviegend Proportional-und Servoventile in Kolbenschieber-Bauweise eingesetzt. Für Anwendungen wie z.B. im Pressenbau, bei Kunststoffsowie Metallspritzgiessmaschinen und Hubvorrichtungen werden Ventile mit hermetischer Dichtfunktion benötigt, um Positionsverriegelungen und Druckhaltefunktionen zu gewährleisten. Beim Kolbenschieber erfordern die durch das Einpasspiel bedingten Leckagen zusätzliche nachgeschaltete Sitzventile mit hohem Kostenaufwand. Desweiteren benötigen die Proportionalventile in Kolbenschieber-Bauweise nach dem bisherigen Stand der Technik eine aufwendige externe Lageregelung des Kolbenschiebers.In electrohydraulic drives, proportional and servo valves in a piston valve design are predominantly used as the link between signal processing electronics and the hydraulic power section. For applications such as In press construction, plastics, metal injection molding machines and lifting devices, valves with a hermetic sealing function are required to ensure position locking and pressure maintenance functions. In the case of the spool, the leaks caused by the fitting play require additional downstream seat valves at high cost. Furthermore, the proportional valves in the spool design according to the prior art require complex external position control of the spool.

Ausserdem müssen die einzelnen Ventile sowohl untereinander wie auch mit dem Pump-und Tankanschluss separat verbunden werden.In addition, the individual valves must be connected to each other as well as to the pump and tank connection separately.

Zur Vermeidung dieser Nachteile des Standes der Technik ist es deshalb Aufgabe der Erfindung, ein Proportional-Wegeventil vorzuschlagen, bei welchem eine hermetische Dichtfunktion gewährleistet ist und gleichzeitig auf eine externe Lageregelung von Kolbenschiebern verzichtet werden kann und wobei die einzelnen Ventile in kompakter Weise in einem Gehäuse untergebracht werden können.To avoid these disadvantages of the prior art, it is therefore an object of the invention to propose a proportional directional control valve in which a hermetic sealing function is guaranteed and at the same time an external position control of piston spools can be dispensed with and the individual valves in a compact manner in one housing can be accommodated.

Diese Aufgabe wird, ausgehend von einem Proportional-Wegeventil der eingangs genannten Gattung, durch die im Kennzeichen des Hauptanspruchs angeführten Merkmale gelöst. Zusätzliche Merkmale befinden sich in den Unteransprüchen.Starting from a proportional directional control valve of the type mentioned at the outset, this object is achieved by the features stated in the characterizing part of the main claim. Additional features are in the subclaims.

Ein Ausführungsbeispiel der Erfindung ist in den Zeichnungen dargestellt und wird im folgenden näher beschrieben. Es zeigen:

  • Figur 1, die Ansteuerung eines Hydraulikzylinders mittels des erfindungsgemässen Proportional-4-Wegeventils in sinnbildlicher Darstellung;
  • Figur 2, eine Schnittansicht des erfindungsgemässen Proportional-Wegeventils.
An embodiment of the invention is shown in the drawings and will be described in more detail below. Show it:
  • Figure 1, the control of a hydraulic cylinder by means of the proportional 4-way valve according to the invention in a symbolic representation;
  • Figure 2 is a sectional view of the proportional directional control valve according to the invention.

In Figur 1 ist ein elektrohydraulischer Antrieb dargestellt, wobei als hydraulischer Leistungsteil ein Hydraulikzylinder 4 als Anwendungsbeispiel gewählt wurde. In bestimmten Anwendungsbereichen, wie z.B. in den eingangs erwähnten, muss ein solcher Zylinder aus Sicherheits- und funktionsbedingten Gründen in einer gegebenen Position verriegelt werden können, was grundsätzlich durch das Vorsehen von Sitzventilen erfolgt, welche ein Zurückströmen der Hydraulikflüssigkeit aus dem Zylinderraum in die Zuleitungen ZA und ZB des Zylinders verunmöglicht.An electrohydraulic drive is shown in FIG. 1, a hydraulic cylinder 4 being selected as an application example as the hydraulic power unit. In certain areas of application, e.g. in the aforementioned, such a cylinder must be able to be locked in a given position for safety and functional reasons, which is basically done by providing seat valves which prevent the hydraulic fluid from flowing back out of the cylinder chamber into the supply lines ZA and ZB of the cylinder.

Erfindungsgemäss wird dies realisiert durch ein Proportional-4-Wegeventil 6, im wesentlichen bestehend aus zwei Proportional-Drosselventile C1 und C3 mit integrierter Federrückführung welche vom Anmelder unter der Bezeichnung DPCMEE 16S8 hergestellt werden, sowie aus zwei vorgesteuerten Senkbremsventilen C2 und C4 in Sitzausführung, wobei den Ausgängen der Ventile C1 und C3 Rückschlagventile R1, bzw. R3 zugeordnet sind.According to the invention, this is realized by a proportional 4-way valve 6, essentially consisting of two proportional throttle valves C1 and C3 with integrated spring return which are manufactured by the applicant under the designation DPCMEE 16S8, and two pilot-controlled lowering brake valves C2 and C4 in the seat version, whereby check valves R1 and R3 are assigned to the outputs of valves C1 and C3.

Soll die Zuleitung ZA des Zylinders 4 druckölbeaufschlagt werden, so wird das Ventil C1 entsprechend der gewünschten Kolbengeschwindigkeit des Zylinders 4 durch seinen Ansteuermagnet a geöffnet, wodurch die Zuleitung ZA über das Rückschlagventil R1 und den Arbeitsleitungsanschluss A des Ventils 6 mit Drucköl versorgt wird. Gleichzeitig wird über die Steuerleitung X1 das Ventil C4 geöffnet für gedrosselten Ölrücklauf vom Zylinderanschluss ZB zum Tankanschluss T des Ventils 6.If the supply line ZA of the cylinder 4 is to be pressurized with oil, the valve C1 is opened according to the desired piston speed of the cylinder 4 by its control magnet a, whereby the supply line ZA is supplied with pressure oil via the check valve R1 and the working line connection A of the valve 6. At the same time, valve C4 is opened via control line X1 for throttled oil return from cylinder port ZB to tank port T of valve 6.

Für das Anhalten des Hydraulikzylinderkolbens 8 in einer verriegelten Stellung wird das Ventil C1 geschlossen, so dass nunmehr der Anschluss ZA an dem Rückschlagventil R1 liegt, und der Anschluss ZB an dem Sitzventil C4; die Steuerleitung X1 wird über das Ventil C1 und die Leckölrückführung 10 zum Tankanschluss T hin entlastet.For stopping the hydraulic cylinder piston 8 in a locked position, the valve C1 is closed, so that the connection ZA now lies on the check valve R1, and the connection ZB on the seat valve C4; The control line X1 is relieved via the valve C1 and the leakage oil return 10 to the tank connection T.

Für eine Versorgung des Anschlusses ZB werden in analoger Weise die Ventile C3 und C2 (dieses über die Steuerleitung X2) aktiviert, während die Verriegelung in ähnlicher Weise wie vorher beschrieben erfolgt.To supply the connection ZB, the valves C3 and C2 are activated in an analogous manner (this via the control line X2), while the locking takes place in a similar manner to that previously described.

Die Senkbremsventile C2, bzw. C4 sind bei positiver Zylinderlast so weit geöffnet, wie das proportionale Ventil C1 bzw. C3 es über die Steuerleitung X1 bzw. X2 vorgibt d.h. es besteht eine gegenseitige Beeinflussung der Ventile C1 und C4, bzw. C3 und C2 je nach Lastdruck, bei negativer Last wirken sie als Abflussdrossel und verhindern ein Voreilen der Last und Kavitation auf der Zuflusseite. Jede Funktion des Hydraulikzylinders kann demgemäss proprotional angesteuert und geregelt werden.With a positive cylinder load, the lowering brake valves C2 or C4 are opened as far as the proportional valve C1 or C3 specifies via control line X1 or X2, i.e. Valves C1 and C4, or C3 and C2 interact depending on the load pressure, with negative loads they act as a discharge throttle and prevent the load from advancing and cavitation on the inflow side. Each function of the hydraulic cylinder can be controlled and regulated accordingly.

Fakultativ sieht die Erfindung ein dem erfindungsgemässen Proportional-Wegeventil 6 vorgeschaltetes Optionsteil O, im wesentlichen bestehend aus einem Kompensator K mit Druckanschluss P' mit überlagerter proportionaler Druckeinstellung PA, PB, zur lastunabhängigen Durchflussregelung vor. Auch ist ein Lastdruckabgriff (loadsensing) L (Anschluss LS) zur Förderstromanpassung bei Einsatz einer Regelpumpe RP möglich. Teil O dient jedoch lediglich zur Energieversorgung des erfindungsgemässen Proportional-4-Wegeventils.Optionally, the invention provides an option part O upstream of the proportional directional control valve 6 according to the invention, essentially consisting of a compensator K with a pressure connection P 'with a superimposed proportional pressure setting PA, PB, for load-independent flow control. A load pressure tap L (connection LS) for flow rate adjustment is also possible when using a control pump RP. However, part O only serves to supply energy to the proportional 4-way valve according to the invention.

Figur 2 zeigt ein praktisches Ausführungsbeispiel des neuen Proportional-Wegeventils im Schnitt (ohne die Option O aus Figur 1). Die Einzelventile C1, C2, C3, C4 sind als fertigungsoptimierte Einschraubventile zur Kostenreduktion ausgeführt und in ein gemeinsames Ventilgehäuse 12 eingeschraubt, wodurch eine kompakte und robuste Ventileinheit entsteht (Cartridge- Technik). Die neu entwickelten Proportional- Drossel-ventile C1, C3 verfügen durch die integrierte Federrückführung zwischen aktivem Cartridge der Hauptstufe zur Vorsteuerung über hohe Dynamik und Stellgenauigkeit ohne zusätzlich erforderliche elektrische Rückführungen. Es werden Öffnungs- und Schliesszeiten von 40 ms bei 100 % Signalaussteuerung und ca. 2 % Hysterese erreicht.Figure 2 shows a practical embodiment of the new proportional directional control valve in section (without option O from Figure 1). The individual valves C1, C2, C3, C4 are designed as production-optimized screw-in valves for cost reduction and screwed into a common valve housing 12, resulting in a compact and robust valve unit (cartridge technology). The newly developed proportional throttle valves C1, C3 have high dynamics and positioning accuracy due to the integrated spring return between the active cartridge of the main stage for pilot control without additional electrical feedback. Opening and closing times of 40 ms are achieved with 100% signal control and approx. 2% hysteresis.

Sowohl die einzelnen Ventilkomponenten als auch das hiermit aufgebaute Proportional-Wegeventil wurden industriell erprobt. Im Anwendungsbereich Kunststoff-Spritzgiessmaschinen wird das Proportional-Drosselventil erfolgreich zur Steuerung des Einspritzvorganges sowie der Schneckendrehzahl beim Plastifizieren eingesetzt. Das gesamte Proportional-Wegeventil erbrachte ausgezeichnete Resultate in der Schliesseinheit und der Auswerferfunktion beim Entformen. Weitere positive Ergebnisse liegen aus Anwendungen bei Gleichlaufsteuerungen von Kalandern und Hubeinrichtungen vor.Both the individual valve components and the proportional directional control valve built with them have been tested industrially. In the plastic injection molding machine application area, the proportional throttle valve is successfully used to control the injection process and the screw speed during plasticizing. The entire proportional directional valve gave excellent results in the clamping unit and the ejector function during demolding. There are further positive results from applications in synchronous control of calenders and lifting devices.

Das erfindungsgemässe Proportional-Wegeventil in Sitzbauweise wurde im vorstehenden in seiner Anwendung mit Senkbremsventilen C2 und C4 beschrieben.The proportional directional control valve according to the invention in the seat construction was described in the above in its application with lowering brake valves C2 and C4.

Die dargestellte Ventilanordung kann jedoch in einfachster Weise auch auf Differentialbetrieb des Zylinders 4 umgeschaltet werden, in dem für eine gleichzeitige Druckölbeaufschlagung der Zylinderseiten A und B die Ventile C1 und C3 gleichzeitig durch ihre Ansteuermagnete a und b geöffnet werden, wobei durch eine entsprechende Schaltung (nicht gezeigt) dafür gesorgt wird, dass die Sitzventile C2 und C4 geschlossen bleiben und das Rückschlagventil R3 ausser Funktion gesetzt wird.The valve arrangement shown can, however, be switched over in the simplest manner to differential operation of the cylinder 4, in which the valves C1 and C3 are opened simultaneously by their control magnets a and b for simultaneous pressurized oil application to the cylinder sides A and B, with a corresponding circuit (not shown) that the seat valves C2 and C4 remain closed and the check valve R3 is deactivated.

Es sei desweiteren darauf hingewiesen, dass das vorgestellte Proportional-Wegeventil in Sitzbauweise durch seine kompakte Bauweise gemäss Figur 2 und Dank seiner genormten Schnittstelle einen direkten Anbau im Zylinderboden ermöglicht (nicht gezeigt).It should also be pointed out that the proportional directional control valve in seat construction, thanks to its compact design according to FIG. 2 and thanks to its standardized interface, enables direct mounting in the cylinder base (not shown).

Dies ist besonders vorteilhaft bei Anlagen und Maschinen mit mehreren Hydraulikzylindern wie z.B. eine Maschine mit einem mehrteiligen Ausleger und verschiedenen Freiheitsgraden des Arbeitsgerätes. Eine Maschine mit z.B. 6 Hydraulikzylinder benötigte bis jetzt für jeden Zylinder zwei Steuerleitungen zwischen dem Zylinder und dem Steuerteil, also 12 Leitungen. Werden die erfindungsgemässen Proportionalventile jedoch wie vorgeschlagen im Zylinderboden eingebaut, so können sie alle an eine gemeinsame Pumpleitung und eine gemeinsame Arbeitsleitung angeschlossen werden, so dass nur mehr zwei Leitungen erforderlich sind weil die Ansteuermagnete elektrisch oder sogar über Funk bedient werden können.This is particularly advantageous for systems and machines with several hydraulic cylinders, e.g. a machine with a multi-part boom and different degrees of freedom of the implement. A machine with e.g. Up to now, 6 hydraulic cylinders required two control lines for each cylinder between the cylinder and the control part, i.e. 12 lines. However, if the proportional valves according to the invention are installed in the cylinder base as suggested, they can all be connected to a common pump line and a common working line, so that only two lines are required because the control magnets can be operated electrically or even by radio.

Ebenfalls sei abschliessend nochmals hervorgehoben, dass durch das Ausführen der Ventile in Sitzbauweise hermetische Dichtheit und damit höchste Betriebssicherheit durch das Blockieren des Zylinders 4 bei Strom-und/oder Druckölausfall gegeben ist.Finally, it should also be emphasized once again that the execution of the valves in the seat design provides hermetic tightness and thus maximum operational safety by blocking the cylinder 4 in the event of a power and / or pressure oil failure.

Claims (5)

1. Proportional-4-Wegeventil in Sitzbauweise, gekennzeichnet durch ein Ventilgehäuse (12) nach DIN genormter Schnittstelle und je zwei einzeln daran montierten Proportional-Drosselventilen (C1, C3), denen austrittseitig je ein Rückschlagventil (R1 bzw. R3) zugeordnet ist, sowie ebenfalls je zwei einzeln am Ventilgehäuse (12) montierten, durch die Proportional-Drosselventile vorgesteuerten Sitzventilen (C2, C4), wobei für eine Druckölbeaufschlagung eines angeschlossenen hydraulischen Leistungsaggregates die Ventile (C1, C4) bzw. die Ventile (C3 und C2) zusammenwirken und die Ventile (C1 und C3) Proportional-Drosselventile mit integrierter interner Federrückführung sind.1.Proportional 4-way valve in seat design, characterized by a valve housing (12) according to the DIN standardized interface and two individually mounted proportional throttle valves (C1, C3), each of which is assigned a check valve (R1 or R3) on the outlet side, as well as two seat valves (C2, C4), each pilot-operated by the proportional throttle valves, which are individually mounted on the valve housing (12), whereby the valves (C1, C4) and the valves (C3 and C2) work together to apply pressure oil to a connected hydraulic power unit and the valves (C1 and C3) are proportional throttle valves with integrated internal spring return. 2. Ventil nach Anspruch 1, dadurch gekennzeichnet, dass das Ventilgehäuse (12) ein genormetes Anschlussbild nach DIN 24340 aufweist.2. Valve according to claim 1, characterized in that the valve housing (12) has a standardized connection diagram according to DIN 24340. 3. Ventil nach Anspruch 1, gekennzeichnet durch einen im Druckzulauf vorgeschalteten Kompensator (K) mit überlagerter proportionaler Druckeinstellung (PA, PB).3. Valve according to claim 1, characterized by an upstream in the pressure compensator (K) with a superimposed proportional pressure setting (PA, PB). 4. Ventil nach Anpruch 3 gekennzeichnet durch einen Lastdruckabgriff LS zur Förderstromanpassung beim Einsatz einer Regelpumpe.4. Valve according to claim 3 characterized by a load pressure tap LS for adjusting the flow when using a control pump. 5. Ventil nach einem der Ansprüche 1 bis 3, dadurch gekennzeichnet dass für eine Differentialschaltung eines angeschlossenen Arbeitszylinders (4) die Ventile (C1) und (C3) gleichzeitig geöffnet werden können, wobei die Ventile (C2) und (C4) geschlossen bleiben und das Rückschlagventil (R3) ausser Funktion gesetzt wird.5. Valve according to one of claims 1 to 3, characterized in that for a differential circuit of a connected working cylinder (4), the valves (C1) and (C3) can be opened simultaneously, the valves (C2) and (C4) remain closed and the check valve (R3) is deactivated.
EP91113761A 1990-08-31 1991-08-16 Proportional 4-way seat valve Withdrawn EP0473030A1 (en)

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LU87794A LU87794A1 (en) 1990-08-31 1990-08-31 PROPORTIONAL-WEGEVENTIL IN SITZBAUWEISE
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EP2320094A3 (en) * 2009-11-06 2014-08-06 CLAAS Industrietechnik GmbH Valve assembly
RU2529543C2 (en) * 2009-11-06 2014-09-27 КЛААС ИНДУСТРИТЕХНИК ГмбХ Valve cluster
WO2022195006A1 (en) * 2021-03-18 2022-09-22 Norgren Gmbh A pressure adjustment apparatus

Also Published As

Publication number Publication date
FI914098A0 (en) 1991-08-30
LU87794A1 (en) 1991-02-18
NO913406D0 (en) 1991-08-30
CA2049792A1 (en) 1992-03-01
FI914098A (en) 1992-03-01
US5211196A (en) 1993-05-18
NO913406L (en) 1992-03-02

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