EP0823559B1 - Dispositif de commande hydraulique - Google Patents

Dispositif de commande hydraulique Download PDF

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Publication number
EP0823559B1
EP0823559B1 EP97112410A EP97112410A EP0823559B1 EP 0823559 B1 EP0823559 B1 EP 0823559B1 EP 97112410 A EP97112410 A EP 97112410A EP 97112410 A EP97112410 A EP 97112410A EP 0823559 B1 EP0823559 B1 EP 0823559B1
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EP
European Patent Office
Prior art keywords
valve
proportional throttle
control device
line
throttle valve
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Expired - Lifetime
Application number
EP97112410A
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German (de)
English (en)
Other versions
EP0823559A3 (fr
EP0823559A2 (fr
Inventor
Heinrich Loedige
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Robert Bosch GmbH
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Robert Bosch GmbH
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Publication date
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Publication of EP0823559A2 publication Critical patent/EP0823559A2/fr
Publication of EP0823559A3 publication Critical patent/EP0823559A3/fr
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Publication of EP0823559B1 publication Critical patent/EP0823559B1/fr
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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
    • F15B11/003—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
    • F15B11/16—Servomotor systems without provision for follow-up action; Circuits therefor with two or more servomotors
    • F15B11/161—Servomotor systems without provision for follow-up action; Circuits therefor with two or more servomotors with sensing of servomotor demand or load
    • F15B11/165—Servomotor systems without provision for follow-up action; Circuits therefor with two or more servomotors with sensing of servomotor demand or load for adjusting the pump output or bypass in response to demand
    • 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
    • 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
    • F15B2211/30525—Directional control valves, e.g. 4/3-directional control valve
    • F15B2211/3053—In combination with a pressure compensating valve
    • F15B2211/3054—In combination with a pressure compensating valve the pressure compensating valve is arranged between directional control valve and 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
    • F15B2211/31—Directional control characterised by the positions of the valve element
    • F15B2211/3144—Directional 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
    • F15B2211/30—Directional control
    • F15B2211/315—Directional control characterised by the connections of the valve or valves in the circuit
    • F15B2211/31523—Directional control characterised by the connections of the valve or valves in the circuit being connected to a pressure source and an output member
    • F15B2211/31529—Directional control characterised by the connections of the valve or valves in the circuit being connected to a pressure source and an output member 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
    • F15B2211/40—Flow control
    • F15B2211/405—Flow control characterised by the type of flow control means or valve
    • F15B2211/40507—Flow control characterised by the type of flow control means or valve with constant 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
    • F15B2211/405—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
    • F15B2211/411—Flow control characterised by the positions of the valve element the positions being discrete
    • 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
    • F15B2211/41509—Flow control characterised by the connections of the flow 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
    • F15B2211/40—Flow control
    • F15B2211/42—Flow control characterised by the type of actuation
    • F15B2211/428—Flow 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
    • F15B2211/455—Control of flow in the feed line, i.e. meter-in 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
    • F15B2211/50509—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
    • 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
    • F15B2211/51—Pressure control characterised by the positions of the valve element
    • F15B2211/513—Pressure 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
    • F15B2211/50—Pressure control
    • F15B2211/57—Control of a differential 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
    • F15B2211/60—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
    • F15B2211/6055—Load sensing circuits having valve means between output member and the load sensing circuit using pressure relief 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
    • F15B2211/60—Circuit components or control therefor
    • F15B2211/63—Electronic controllers
    • F15B2211/6303—Electronic controllers using input signals
    • F15B2211/6346—Electronic controllers using input signals representing a state of input means, e.g. joystick position
    • 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
    • F15B2211/65—Methods of control of the load sensing pressure
    • F15B2211/652—Methods of control of the load sensing pressure the load sensing pressure being different from the load 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
    • F15B2211/70—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
    • F15B2211/7052—Single-acting output members

Definitions

  • the invention is based on a hydraulic Control device according to the preamble of claim 1 specified genus.
  • Such a hydraulic control device is already out DE 44 46 145 A1 known for controlling a single-acting Motor serves and for lifting and lowering the load has two proportional throttle valves that act as two-way valves are trained, electromagnetically controlled and are structurally separate from each other.
  • a additional pressure compensator ensures a load-compensated Volume flow control when lifting. Although one Load compensation when lifting in many applications such a load pressure compensated control is sufficient in some cases also desirable when lowering, which is the case with previously known control device is not possible. Since the Control device to safely shut off the simple Acting load should be particularly tight, are seat valves used to shut off the motor connection.
  • the pressure compensator is here upstream of the Proportional throttle valve switched, being optional is designed as a two-way or four-way valve. The The load is lowered depending on the load pressure.
  • DE 34 22 978 is a hydraulic one Control device known in the in a working line between a proportional valve and a motor Pressure compensator is switched.
  • the hydraulic motor is here trained as a double-acting consumer and accordingly the one used for control Proportional valve designed as a four-way valve that for the load pressure feedback additional control connections having.
  • the pressure compensator here in the inlet flow and once in the drain current, is to switch to the Pressure compensator acting pressure difference a magnetic Actuable 4/2 switching valve provided, which depends on actuation of the proportional valve got to.
  • This control device is not suitable for one Circuit with 2-way proportional throttle valves; is also the effort for the control circuit of the pressure compensator is relatively high.
  • This control device also does not use seat valves in the working line influenced by the pressure compensator, so that it is not easy to shut off a leak acting load is suitable.
  • the hydraulic control device according to the invention with the characteristic features of claim 1 has in contrast the advantage that they can be low-leakage design a pressure-compensated Volume flow control also possible with sinks, so that now a load pressure independent control of the engine in its is possible in both directions.
  • the advantages of building with Two-way proportional valves remain unchanged maintained. While in the working group itself no additional effort is required, it is only relatively simple, space-saving and cost-effective changes in the control circuit the control device.
  • the figure shows a in a simplified representation hydraulic control device 10 for load-compensated Volume flow control for a hydraulic motor 11, the is designed as a single-acting cylinder, like in hoists for lifting, holding and lowering loads, is used in particular in forklifts or tractors.
  • the control device 10 here has a valve block 12 on the between a connecting plate 13 and one additional valve block 14 is flanged and that of one continuous pump channel 15 and a continuous Return channel 16 is penetrated.
  • these Pump channel 15 outgoing and to a motor connection 17th leading inlet line 18 are a first one after the other Proportional throttle valve 19, a motor 11 securing Check valve 21 and a pressure compensator 22 switched.
  • one of the return channel 16 to Motor connection 17 leading drain line 23 a second Proportional throttle valve 24 switched that as a seat valve is executed.
  • the inlet line 18 and the return line 23 form in the area between the motor connection 17 and one Branch 25 a common line section 26 in which the pressure compensator 22 is located.
  • the check valve 21 is in the feed line 18 upstream of the branch 25.
  • Both proportional throttle valves 19, 24 are related to their working flows run as two-way valves that each work proportionally and operated electromagnetically what their proportional magnets from one electronic control unit 27 can be controlled. Accordingly, the proportional throttle valves 19, 24 each have two working connections P, A, of which in the P position is blocked in the respective starting position.
  • the first proportional throttle valve 19 has a first one Control connection 28 with a first control line 31 the non-spring-loaded end face of the pressure compensator 22 in Connection is established.
  • a second control line 32 also leads from the working port A of the first proportional valve 19 to that end face of the pressure compensator 22, which by a Control spring 33 is loaded.
  • a shuttle valve 34 is also connected, which via a third control line 35 with the working connection P of the second proportional throttle valve 24 is connected.
  • the shuttle valve 34 is arranged in the control circuit and switched that it was the higher pressure in the first Control port 28 or in the working port P of the second Proportional throttle valve 24 selects and to the pressure compensator 22 forwards.
  • the first Proportional throttle valve 19 In the shown starting position 29 of the first proportional throttle valve 19 is its first Control connection 28 via a fourth control line 40 to Return channel 16 relieved, this relief via a Cross connection 30 in the control element of the first Proportional throttle valve 19 also for the working connection A is effective.
  • the control link of the first Proportional throttle valve 19 is from his Proportional magnets against the force of a spring from the Starting position 29 adjustable in working positions 36, a measuring choke 37 proportional to the size of the electrical input signal is controllable. In the Working positions 36, the pressure upstream of the Measuring throttle 37 always led to the first control connection 28.
  • the second Proportional throttle valve 24 Like the simplified representation of the second Proportional throttle valve 24 shows, it is despite its proportional mode of operation as a throttle valve too designed as a seat valve so that it is in its Starting position 38 the motor 11 safely hydraulically cordoned off. In the working positions 39 is accordingly Function as a proportional throttle valve the measuring throttle more or stepped up less.
  • a control slide 41 arranged in the pressure compensator 22 becomes from the control spring 33 in the direction of a connection in Line section 26 opening position 42 pressed while moving from a pressure differential against the Force of the control spring 33 in the direction of a blocking position 43 is deflectable.
  • the pressure in the feed line 18 in the area between the first Proportional throttle valve 19 and check valve 21 is tapped from a fifth control line 44 and to one second shuttle valve 45, which in a control circuit 46 is switched for a system pressure compensator 47.
  • a system pressure compensator 47 lies the system pressure compensator 47 in a bypass 48 between that of a pump 49 supplied with pressure medium pump channel 15 and the return duct 16.
  • control device 10 The operation of the control device 10 is as follows explained, the basic function of such Proportional throttle valves 19, 24 as known per se is assumed.
  • the first Proportional throttle valve 19 To lift the motor 11 is the first Proportional throttle valve 19 in the direction of it Working position 36 deflected so that the pump channel 15th a volume flow through the inlet line 18, the first Proportional throttle valve 19, the check valve 21 and the pressure compensator 22 flows to the motor 11.
  • the first Proportional throttle valve 19 arises at the Measuring throttle 37 a pressure drop, the pressure tapped upstream of the measuring throttle 37 and over the first control connection 28, the first control line 31 with the Shuttle valve 34 to the springless end face of the pressure compensator 22 is conducted while the pressure downstream of the Measuring choke 37 via the second control line 32 to the of the end of the pressure compensator 22 acted upon by the control spring 33 works.
  • the Pressure compensator 22 the pressure drop at the measuring throttle 37 constant, so that a load-compensated when lifting Volume flow control to the engine 11 is achieved, the Measuring throttle 37 with the pressure compensator 22 a two-way flow controller forms.
  • the control unit 27 uses the Proportional solenoid on the second proportional throttle valve 24 controlled, whereby its control member against the force of Spring is deflected into the working position 39.
  • the on Working port P existing load pressure of the engine 11 is tapped from the third control line 35 and via the Shuttle valve 34 and part of the first control line 31 led to the springless end face of the pressure compensator 22.
  • the end face of the pressure compensator 22 loaded by the control spring 33 is via the second control line 32, the in Starting position 29 located first Proportional throttle valve 19 and the fourth control line 40 with the working connection A of the second Proportional throttle valve 24 connected and thus to Return channel 16 relieved.
  • the pressure compensator 22 is now upstream of the second proportional throttle valve 24 in switched the volume flow, being known in itself Way the pressure drop across the orifice in the second Proportional throttle valve 24 keeps constant. Thus, too load-compensated volume flow control when lowering reached.
  • the pump 49 conveyed volume flow either via the system pressure compensator 47 and the bypass 48 returned to the tank 52 are not closer or if necessary to supply one drawn additional motor via the pump channel 15 be led to this consumer.

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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)

Claims (11)

  1. Dispositif hydraulique de commande servant à commander un moteur (11) à simple effet, comprenant une première vanne proportionnelle d'étranglement (19), montée dans une conduite d'amenée (18) pour soulever une charge et une deuxième vanne proportionnelle d'étranglement (24), montée dans une conduite de départ (23) pour abaisser la charge ainsi qu'une balance de pression (22) pour commander le débit compensé en fonction de la charge lors du levage, la chute de pression qui se produit sur la première vanne proportionnelle d'étranglement (19) étant amenée pour cela par l'intermédiaire de deux conduites de commande (31, 32) à la balance de pression (22), pressée par un ressort,
    caractérisé en ce que
    la balance de pression (22) est montée dans une section de conduite (26) associée en commun à la conduite d'arrivée (18) et à la conduite de départ (23),
    la première vanne proportionnelle d'étranglement (19) commande la première (31) des deux conduites de commande (31, 32), et
    dans cette première conduite de commande (31) est montée une vanne à alternance (34), au moyen de laquelle la balance de pression (22) peut être inversée et passée sur une sollicitation de pression dépendant de la deuxième vanne proportionnelle d'étranglement (24).
  2. Dispositif hydraulique de commande selon la revendication 1,
    caractérisé en ce que
    un clapet anti-retour (21) assurant la sécurité du moteur (11) est monté dans la conduite d'arrivée (18) en aval de la première vanne proportionnelle d'étranglement (19) et en amont de la section commune de conduite (26).
  3. Dispositif hydraulique de commande selon la revendication 1 ou 2,
    caractérisé en ce que
    les deux vannes proportionnelles d'étranglement (19, 24) sont constituées sous la forme de vannes à deux voies actionnées de façon électromagnétique à l'encontre de la force d'un ressort.
  4. Dispositif hydraulique de commande selon l'une quelconque des revendications 1 à 3,
    caractérisé en ce que
    la deuxième vanne proportionnelle d'étranglement (24) est réalisée selon le mode de construction d'une vanne à siège.
  5. Dispositif hydraulique de commande selon l'une quelconque des revendications 1 à 4,
    caractérisé en ce que
    la première vanne proportionnelle d'étranglement (19) présente un premier raccord de commande (28), à partir duquel la première conduite de commande (31) va par l'intermédiaire de la vanne à alternance (34) à la balance de pression (22), et sollicite celle-ci à l'encontre de la force de son ressort de réglage (33).
  6. Dispositif hydraulique de commande selon la revendication 5,
    caractérisé en ce que
    la première vanne proportionnelle d'étranglement (19) fait passer dans ses positions de travail (36) la pression en amont de son étranglement de mesure (37) vers le premier raccord de commande (28), qui dans sa position de départ est déchargé par l'intermédiaire d'une quatrième conduite de commande (40) vers un canal de retour (16), et qui en outre est en liaison par l'intermédiaire d'une liaison transversale (30) avec le raccord de travail (A), situé du côté du moteur.
  7. Dispositif hydraulique de commande selon la revendication 5 ou 6,
    caractérisé en ce que
    la pression en aval de l'étranglement de mesure (37) dans la première vanne proportionnelle d'étranglement (19) sollicite par l'intermédiaire d'une deuxième conduite de commande (32) la balance de pression (22) dans le même sens en direction du ressort de réglage (33).
  8. Dispositif hydraulique de commande selon l'une quelconque des revendications 1 à 7,
    caractérisé en ce que
    la vanne à alternance (34) a par l'intermédiaire d'une troisième conduite de commande (35) une liaison avec la conduite de départ (23) dans une zone en amont de l'étranglement de mesure dans la deuxième vanne proportionnelle d'étranglement (24).
  9. Dispositif hydraulique de commande selon l'une quelconque des revendications 1 à 8,
    caractérisé en ce que
    la pression est prélevée dans la conduite d'arrivée (18) dans la zone comprise entre la première vanne proportionnelle d'étranglement (19) et la vanne de non retour (21) par une cinquième conduite de commande (44), et est amenée par l'intermédiaire d'une deuxième vanne à alternance (45) à un système d'alimentation en fluide sous pression, qui est en particulier constitué par une balance de pression (47) d'un système fonctionnant comme une vanne d'inversion.
  10. Dispositif hydraulique de commande selon l'une quelconque des revendications 1 à 9,
    caractérisé en ce que
    les deux vannes proportionnelles d'étranglement (19, 24) sont commandées avec leurs électroaimants proportionnels par un appareil électronique de commande (27).
  11. Dispositif hydraulique de commande selon l'une quelconque des revendications 1 à 10,
    caractérisé en ce que
    la balance de pression (22) constituée sous la forme d'une vanne à deux voies, est pressée par son ressort de réglage (33) dans une position de départ ouverte (42) et est pressée par la différence de pression qui s'applique sur elle dans le sens d'une position d'obturation (43).
EP97112410A 1996-08-09 1997-07-19 Dispositif de commande hydraulique Expired - Lifetime EP0823559B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE19632201 1996-08-09
DE19632201A DE19632201A1 (de) 1996-08-09 1996-08-09 Hydraulische Steuereinrichtung

Publications (3)

Publication Number Publication Date
EP0823559A2 EP0823559A2 (fr) 1998-02-11
EP0823559A3 EP0823559A3 (fr) 1998-07-15
EP0823559B1 true EP0823559B1 (fr) 2001-10-31

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Application Number Title Priority Date Filing Date
EP97112410A Expired - Lifetime EP0823559B1 (fr) 1996-08-09 1997-07-19 Dispositif de commande hydraulique

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EP (1) EP0823559B1 (fr)
DE (2) DE19632201A1 (fr)

Families Citing this family (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE29810860U1 (de) 1998-06-17 1998-08-13 Heilmeier & Weinlein Fabrik für Oel-Hydraulik GmbH & Co KG, 81673 München Hydraulische Steuervorrichtung
US6116263A (en) * 1998-07-23 2000-09-12 Hydraforce, Inc. Proportional priority flow regulator with reverse flow control
DE10023583B4 (de) * 2000-05-13 2012-05-24 Robert Bosch Gmbh Elektrohydraulischer Senken-Modul
US6457487B1 (en) * 2001-05-02 2002-10-01 Husco International, Inc. Hydraulic system with three electrohydraulic valves for controlling fluid flow to a load
DE102004014375A1 (de) * 2004-03-17 2005-10-06 Hydac System Gmbh Vorrichtung zum Ansteuern und Betätigen einer Rüttelmechanik
CN102979774B (zh) * 2012-05-24 2015-05-06 山东弘宇农机股份有限公司 一种拖拉机液压悬挂专用控制阀块
CN105035979B (zh) * 2015-08-05 2017-05-03 常德中联重科液压有限公司 平衡阀组和液压系统

Family Cites Families (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE3422978C2 (de) * 1984-06-22 1995-07-20 Bosch Gmbh Robert Vorrichtung zur Steuerung einer hydraulischen Stelleinrichtung
DE3844400C2 (de) * 1988-12-30 1993-12-02 Rexroth Mannesmann Gmbh Ventilanordnung für ein hydraulisches System
DE4307872C2 (de) * 1993-03-12 2001-05-17 Orenstein & Koppel Ag Lastdruckunabhängige Steuerung der Geschwindigkeit von hydraulischen Stellelementen
DE9405872U1 (de) * 1994-04-08 1994-05-26 Heilmeier & Weinlein Fabrik für Oel-Hydraulik GmbH & Co KG, 81673 München Senkbremsventil und Mengenregel-Vorrichtung für die Hochdruck-Hydraulik
DE4446145A1 (de) * 1994-12-23 1996-06-27 Bosch Gmbh Robert Hydraulische Steuerung in Monoblockbauweise zum Heben und Senken einer Last mit mindestens zwei elektromagnetisch betätigbaren Proportionalwegeventilelementen

Also Published As

Publication number Publication date
EP0823559A3 (fr) 1998-07-15
DE19632201A1 (de) 1998-02-12
EP0823559A2 (fr) 1998-02-11
DE59705151D1 (de) 2001-12-06

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