EP0823559B1 - Hydraulic control device - Google Patents

Hydraulic control device Download PDF

Info

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
Authority
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
Other languages
German (de)
French (fr)
Other versions
EP0823559A2 (en
EP0823559A3 (en
Inventor
Heinrich Loedige
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.)
Robert Bosch GmbH
Original Assignee
Robert Bosch GmbH
Priority date (The priority date 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 date listed.)
Filing date
Publication date
Application filed by Robert Bosch GmbH filed Critical Robert Bosch GmbH
Publication of EP0823559A2 publication Critical patent/EP0823559A2/en
Publication of EP0823559A3 publication Critical patent/EP0823559A3/en
Application granted granted Critical
Publication of EP0823559B1 publication Critical patent/EP0823559B1/en
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

Links

Images

Classifications

    • 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.

Description

Stand der TechnikState of the art

Die Erfindung geht aus von einer hydraulischen Steuereinrichtung nach der im Oberbegriff des Anspruchs 1 näher angegebenen Gattung.The invention is based on a hydraulic Control device according to the preamble of claim 1 specified genus.

Es ist schon eine solche hydraulische Steuereinrichtung aus der DE 44 46 145 A1 bekannt, die zum Steuern eines einfachwirkenden Motors dient und zum Heben und Senken der Last zwei Proportionaldrosselventile aufweist, die als Zwei-Wege-Ventile ausgebildet sind, elektromagnetisch angesteuert werden und baulich voneinander getrennt sind. Eine zusätzliche Druckwaage sorgt für eine lastkompensierte Volumenstromsteuerung beim Heben. Obwohl eine Lastkompensation beim Heben in vielen Anwendungsfällen ausreicht, ist eine solche lastdruckkompensierte Steuerung in manchen Fällen auch beim Senken erwünscht, was bei der vorbekannten Steuereinrichtung nicht möglich ist. Da die Steuereinrichtung zum sicheren Absperren der einfach wirkenden Last besonders dicht sein soll, werden Sitzventile zum Absperren des Motoranschlusses verwendet. Die Druckwaage ist hier zulaufseitig stromaufwärts des Proportionaldrosselventils geschaltet, wobei sie wahlweise als Zwei-Wege- bzw. Vier-Wege-Ventil ausgebildet ist. Das Senken der Last erfolgt lastdruckabhängig.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.

Weiterhin ist aus der DE 34 22 978 eine hydraulische Steuereinrichtung bekannt, bei der in eine Arbeitsleitung zwischen einem Proportionalventil und einem Motor eine Druckwaage geschaltet ist. Der hydraulische Motor ist hier als doppeltwirkender Verbraucher ausgebildet und dementsprechend das zur Steuerung dienende Proportionalventil als Vier-Wege-Ventil ausgeführt, das für die Lastdruckrückführung zusätzliche Steueranschlüsse aufweist. Da die Druckwaage hier einmal im Zulaufstrom und einmal im Ablaufstrom liegt, ist zur Umschaltung der auf die Druckwaage einwirkenden Druckdifferenz ein magnetisch betätigbares 4/2-Schaltventil vorgesehen, das abhängig von der Betätigung des Proportionalventils umgeschaltet werden muß. Diese Steuereinrichtung eignet sich nicht für eine Schaltung mit 2-Wege-Proportionaldrosselventilen; zudem ist der Aufwand für den Steuerkreis der Druckwaage relativ hoch. Auch verwendet diese Steuereinrichtung keine Sitzventile in der von der Druckwaage beeinflußten Arbeitsleitung, so daß es sich nicht zum leckarmen Absperren einer einfach wirkenden Last eignet.Furthermore, 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. Because 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.

Vorteile der ErfindungAdvantages of the invention

Die erfindungsgemäße hydraulische Steuereinrichtung mit den kennzeichnenden Merkmalen des Anspruchs 1 hat demgegenüber den Vorteil, daß sie auch unter Beibehaltung einer dichten, leckagearmen Bauweise eine druckkompensierte Volumenstromsteuerung auch bei Senken ermöglicht, so daß nun eine lastdruckunabhängige Steuerung des Motors in dessen beiden Richtungen möglich ist. Die Vorteile der Bauweise mit Zwei-Wege-Proportionalventilen werden dabei unverändert beibehalten. Während im Arbeitskreis selbst kein Mehraufwand erforderlich ist, bedarf es lediglich relativ einfacher, platzsparender und kostengünstiger Änderungen im Steuerkreis der Steuereinrichtung.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.

Durch die in den Unteransprüchen aufgeführten Maßnahmen sind vorteilhafte Weiterbildungen und Verbesserungen der im Anspruch 1 angegebenen Steuereinrichtung möglich. Besonders zweckmäßig ist eine Ausbildung nach Anspruch 2, wodurch das erste Proportionaldrosselventil für die Funktion Heben als kostengünstiges Schieberventil ausgeführt werden kann, wobei ein billiges Rückschlagventil die Funktion der Dichtheit in der Schaltung übernimmt. Vorteilhaft ist ferner, wenn die beiden Proportionaldrosselventile gemäß Anspruch 3 ausgeführt und dementsprechend angesteuert werden. Für die Dichtheit der Schaltung ist es vorteilhaft, wenn gemäß Anspruch 4 das zweite Proportionaldrosselventil in Sitzventilbauweise ausgeführt und damit die Funktion der sicheren Abdichtung integriert ist. Besonders zweckmäßige und einfache Bauweisen lassen sich erreichen, wenn die Steuerkreise gemäß den Ansprüchen 5 bis 8 ausgeführt werden. Weitere vorteilhafte Ausgestaltungen ergeben sich aus den übrigen Ansprüchen, der Beschreibung sowie der Zeichnung.By the measures listed in the subclaims advantageous developments and improvements in Claim 1 specified control device possible. Especially is appropriate training according to claim 2, whereby the first proportional throttle valve for the lifting function inexpensive slide valve can be executed, wherein a cheap check valve the function of the tightness in the circuit takes over. It is also advantageous if the two proportional throttle valves according to claim 3 executed and controlled accordingly. For the Tightness of the circuit, it is advantageous if according to Claim 4 in the second proportional throttle valve Seat valve design and thus the function of secure sealing is integrated. Particularly useful and simple designs can be achieved if the Control circuits are carried out according to claims 5 to 8. Further advantageous configurations result from the other claims, the description and the drawing.

Zeichnungdrawing

Ein Ausführungsbeispiel der Erfindung ist in der Zeichnung dargestellt und in der nachfolgenden Beschreibung näher erläutert. Es zeigen die einzige Figur ein Ausführungsbeispiel der erfindungsgemäßen hydraulischen Steuereinrichtung in vereinfachter Darstellung.An embodiment of the invention is in the drawing shown and in the following description explained. It show the only figure Embodiment of the hydraulic according to the invention Control device in a simplified representation.

Beschreibung des AusführungsbeispielsDescription of the embodiment

Die Figur zeigt in vereinfachter Darstellung eine hydraulische Steuereinrichtung 10 zur lastkompensierten Volumenstromsteuerung für einen hydraulischen Motor 11, der hier als einfachwirkender Arbeitszylinder ausgebildet ist, wie er in Hubwerken zum Heben, Halten und Senken von Lasten, insbesondere in Staplern oder Traktoren verwendet wird.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.

Die Steuereinrichtung 10 weist hier einen Ventilblock 12 auf, der zwischen eine Anschlußplatte 13 und einen zusätzlichen Ventilblock 14 geflanscht ist und der von einem durchgehenden Pumpenkanal 15 sowie einem durchgehenden Rücklaufkanal 16 durchdrungen ist. In eine von diesem Pumpenkanal 15 abgehende und zu einem Motoranschluß 17 führende Zulaufleitung 18 sind hintereinander ein erstes Proportionaldrosselventil 19, ein den Motor 11 absicherndes Rückschlagventil 21 sowie eine Druckwaage 22 geschaltet. Ferner ist in eine von dem Rücklaufkanal 16 zum Motoranschluß 17 führende Ablaufleitung 23 ein zweites Proportionaldrosselventil 24 geschaltet, das als Sitzventil ausgeführt ist. Die Zulaufleitung 18 und die Rücklaufleitung 23 bilden im Bereich zwischen Motoranschluß 17 und einer Abzweigung 25 einen gemeinsamen Leitungsabschnitt 26, in dem die Druckwaage 22 liegt. Das Rückschlagventil 21 liegt in der Zulaufleitung 18 stromaufwärts von der Abzweigung 25.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. In one of 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. Furthermore, 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.

Beide Proportionaldrosselventile 19, 24 sind in Bezug auf ihre Arbeitsströme als Zwei-Wege-Ventile ausgeführt, die jeweils proportional arbeiten und elektromagnetisch betätigt werden, wozu ihre Proportionalmagnete von einem elektronischen Steuergerät 27 ansteuerbar sind. Dementsprechend weisen die Proportionaldrosselventile 19, 24 jeweils zwei Arbeitsanschlüsse P, A auf, von denen in der jeweiligen Ausgangsstellung der P-Anschluß abgesperrt ist.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.

Das erste Proportionaldrosselventil 19 hat einen ersten Steueranschluß 28, der über eine erste Steuerleitung 31 mit der nicht federbelasteten Stirnseite der Druckwaage 22 in Verbindung steht. Ferner führt eine zweite Steuerleitung 32 vom Arbeitsanschluß A des ersten Proportionalventils 19 zu derjenigen Stirnseite der Druckwaage 22, die von einer Regelfeder 33 belastet ist. In die erste Steuerleitung 31 ist ferner ein Wechselventil 34 geschaltet, das über eine dritte Steuerleitung 35 mit dem Arbeitsanschluß P des zweiten Proportionaldrosselventils 24 in Verbindung steht. Das Wechselventil 34 ist dabei im Steuerkreis so angeordnet und geschaltet, daß es den höheren Druck im ersten Steueranschluß 28 bzw. im Arbeitsanschluß P des zweiten Proportionaldrosselventils 24 auswählt und an die Druckwaage 22 weiterleitet. In der gezeigten Ausgangsstellung 29 des ersten Proportionaldrosselventils 19 ist dessen erster Steueranschluß 28 über eine vierte Steuerleitung 40 zum Rücklaufkanal 16 entlastet, wobei diese Entlastung über eine Querverbindung 30 im Steuerglied des ersten Proportionaldrosselventils 19 auch für den Arbeitsanschluß A wirksam ist. Das Steuerglied des ersten Proportionaldrosselventils 19 ist von seinem Proportionalmagneten gegen die Kraft einer Feder aus der Ausgangsstellung 29 in Arbeitsstellungen 36 verstellbar, wobei eine Meßdrossel 37 proportional zur Größe des elektrischen Eingangssignals aufsteuerbar ist. In den Arbeitsstellungen 36 wird der Druck stromaufwärts der Meßdrossel 37 stets zum ersten Steueranschluß 28 geführt.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. In the first control line 31 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. 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.

Wie die vereinfachte Darstellung des zweiten Proportionaldrosselventils 24 näher zeigt, ist es trotz seiner proportionalen Arbeitsweise als Drosselventil auch als Sitzventil ausgeführt, so daß es in seiner Ausgangsstellung 38 den Motor 11 sicher hydraulisch absperrt. In den Arbeitsstellungen 39 wird entsprechend der Funktion als Proportionaldrosselventil die Meßdrossel mehr oder weniger stark aufgesteuert. 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.

Ein in der Druckwaage 22 angeordneter Regelschieber 41 wird von der Regelfeder 33 in Richtung einer die Verbindung im Leitungsabschnitt 26 aufsteuernden Ausgangsstellung 42 gedrückt, während er von einer Druckdifferenz gegen die Kraft der Regelfeder 33 in Richtung einer Sperrstellung 43 auslenkbar ist.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.

Der Druck in der Zulaufleitung 18 im Bereich zwischen erstem Proportionaldrosselventil 19 und Rückschlagventil 21 wird von einer fünften Steuerleitung 44 abgegriffen und zu einem zweiten Wechselventil 45 geführt, das in einen Steuerkreis 46 für eine System-Druckwaage 47 geschaltet ist. Dabei liegt die System-Druckwaage 47 in einem Bypaß 48 zwischen dem von einer Pumpe 49 mit Druckmittel versorgten Pumpenkanal 15 und dem Rücklaufkanal 16.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. Here 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.

Die Wirkungsweise der Steuereinrichtung 10 wird wie folgt erläutert, wobei die grundsätzliche Funktion von derartigen Proportionaldrosselventilen 19, 24 als an sich bekannt vorausgesetzt wird.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.

Werden beide Proportionaldrosselventile 19, 24 von dem elektronischen Steuergerät 27 nicht angesteuert, so nehmen sie ihre federzentrierten Ausgangsstellungen 29 bzw. 38 ein. Eine Last im Motor 11 wird einerseits in der Zulaufleitung 18 durch das Rückschlagventil 21 und in der Ablaufleitung 23 durch die Sitzfunktion des zweiten Proportionaldrosselventils 24 sicher abgesperrt. Ferner sorgt das Wechselventil 34 im Steuerkreis für eine sichere Abdichtung, so daß eine hohe Dichtheit der Steuereinrichtung 10 erreicht wird, wodurch der Motor 11 weitestgehend leckagefrei gehalten werden kann. Lediglich zwischen einer Steuerkante in der Druckwaage 22 und dessen zugeordnetem Federraum kann sich ein Leckölstrom ausbilden, der sich aber durch eine entsprechende Gestaltung der Druckwaage, zum Beispiel in Sitzbauweise oder mit langer Schieberführung, beeinflussen läßt. In der Ausgangsstellung 29 des ersten Proportionaldrosselventils 19 ist der erste Steueranschluß 28 ebenso wie der zugeordnete Arbeitsanschluß A über die vierte Steuerleitung 40 zum Rücklaufkanal 16 entlastet. Somit kann sich an der von der Regelfeder 33 belasteten Stirnseite der Druckwaage 22 kein Druck aufbauen. Ein im Motor 11 herrschender Lastdruck kann sich allenfalls über die Druckwaage 22 am Arbeitsanschluß P des zweiten Proportionaldrosselventils 24 aufbauen und über die dritte Steuerleitung 35 und das Wechselventil 34 auf die nicht von der Feder belastete Stirnseite der Druckwaage 22 wirken und diese in Richtung Sperrstellung 43 verschieben.Are both proportional throttle valves 19, 24 by the electronic control unit 27 is not controlled, so take they enter their spring-centered starting positions 29 and 38, respectively. A load in the engine 11 is on the one hand in the feed line 18 through the check valve 21 and in the drain line 23 through the seat function of the second Proportional throttle valve 24 securely shut off. Further the shuttle valve 34 in the control circuit ensures safe Sealing, so that the control device is tight 10 is reached, whereby the motor 11 largely can be kept leak-free. Only between one Control edge in the pressure compensator 22 and its associated one A spring oil flow can form in the spring chamber, but it does through an appropriate design of the pressure compensator, for Example in seat construction or with long slide guide, can influence. In the starting position 29 of the first Proportional throttle valve 19 is the first control connection 28 as well as the assigned work port A via the fourth control line 40 to the return channel 16 relieved. Thus can be loaded on the control spring 33 Do not build up pressure on the front of the pressure compensator 22. An im Engine 11 prevailing load pressure can at most over the pressure compensator 22 at the working port P of the second Build proportional throttle valve 24 and the third Control line 35 and the shuttle valve 34 on the not of the spring-loaded end face of the pressure compensator 22 act and move them towards the locked position 43.

Bei nicht betätigtem Ventilblock 12 kann auch der Steuerkreis 46 über das zweite Wechselventil 45, die fünfte Steuerleitung 44 und das erste Proportionaldrosselventil 19 zum Rücklaufkanal 16 entlastet werden, so daß die System-Druckwaage 47 als Umschaltventil arbeitet und das von der Pumpe 49 geförderte Druckmittel über den Bypaß 48 zurück in einen Tank 52 strömt.When the valve block 12 is not actuated, the Control circuit 46 via the second shuttle valve 45, the fifth Control line 44 and the first proportional throttle valve 19 to the return channel 16 are relieved, so that the system pressure compensator 47 works as a changeover valve and that of Pump 49 delivered pressure medium via the bypass 48 back in a tank 52 flows.

Zum Heben des Motors 11 wird das erste Proportionaldrosselventil 19 in Richtung seiner Arbeitsstellung 36 ausgelenkt, so daß von dem Pumpenkanal 15 ein Volumenstrom über die Zulaufleitung 18, das erste Proportionaldrosselventil 19, das Rückschlagventil 21 und die Druckwaage 22 zum Motor 11 strömt. Im ersten Proportionaldrosselventil 19 entsteht dabei an der Meßdrossel 37 ein Druckgefälle, wobei der Druck stromaufwärts der Meßdrossel 37 abgegriffen und über den ersten Steueranschluß 28, die erste Steuerleitung 31 mit dem Wechselventil 34 zu der federlosen Stirnseite der Druckwaage 22 geführt wird, während der Druck stromabwärts der Meßdrossel 37 über die zweite Steuerleitung 32 auf die von der Regelfeder 33 beaufschlagte Stirnseite der Druckwaage 22 wirkt. In an sich bekannter Weise hält dadurch die Druckwaage 22 das Druckgefälle an der Meßdrossel 37 konstant, so daß beim Heben eine lastkompensierte Volumenstromsteuerung zum Motor 11 erreicht wird, wobei die Meßdrossel 37 mit der Druckwaage 22 einen Zwei-Wege-Stromregler bildet.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. In 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. In a manner known per se, 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.

In der Arbeitsstellung 36 des ersten Proportionaldrosselventils 19 ist auch die Entlastung über die vierte Steuerleitung 40 gesperrt, so daß der Lastdruck über die fünfte Steuerleitung 44 an der System-Druckwaage 47 wirken kann, wodurch dieses den Bypaß 48 androsselt bzw. schließt und der von der Pumpe 49 geförderte Volumenstrom in den Pumpenkanal 15 fließt. Zum Beenden des Hebenvorgangs wird die Erregung des ersten Proportionaldrosselventils 36 abgeschaltet, wodurch es in seine federbelastete Ausgangsstellung 29 zurückgestellt wird.In working position 36 of the first Proportional throttle valve 19 is also the relief the fourth control line 40 blocked so that the load pressure via the fifth control line 44 on the system pressure compensator 47 can act, which throttles the bypass 48 or closes and the volume flow delivered by the pump 49 in the pump channel 15 flows. To end the lifting process the excitation of the first proportional throttle valve 36 turned off, causing it to spring loaded Starting position 29 is reset.

Zum Senken des Motors 11 wird von dem Steuergerät 27 der Proportionalmagnet am zweiten Proportionaldrosselventil 24 angesteuert, wodurch sein Steuerglied gegen die Kraft der Feder in die Arbeitsstellung 39 ausgelenkt wird. Der am Arbeitsanschluß P vorhandene Lastdruck des Motors 11 wird von der dritten Steuerleitung 35 abgegriffen und über das Wechselventil 34 und einen Teil der ersten Steuerleitung 31 auf die federlose Stirnseite der Druckwaage 22 geführt. Die von der Regelfeder 33 belastete Stirnseite der Druckwaage 22 ist über die zweite Steuerleitung 32, das in Ausgangsstellung 29 befindliche erste Proportionaldrosselventil 19 und die vierte Steuerleitung 40 mit dem Arbeitsanschluß A des zweiten Proportionaldrosselventils 24 verbunden und damit zum Rücklaufkanal 16 entlastet. Die Druckwaage 22 ist nun stromaufwärts vom zweiten Proportionaldrosselventil 24 in den Volumenstrom geschaltet, wobei sie in an sich bekannter Weise das Druckgefälle über die Meßblende im zweiten Proportionaldrosselventil 24 konstant hält. Somit wird auch beim Senken eine lastkompensierte Volumenstromsteuerung erreicht. Beim Senken des Motors 11 kann der von der Pumpe 49 geförderte Volumenstrom entweder über die System-Druckwaage 47 und den Bypaß 48 zum Tank 52 zurückgeleitet werden oder bei Bedarf zur Versorgung einens nicht näher gezeichneten, zusätzlichen Motors über den Pumpenkanal 15 zu diesem Verbraucher geführt werden.To lower the motor 11, 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. When lowering the motor 11, 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.

Selbstverständlich sind an der gezeigten Ausführungsform Änderungen möglich, ohne von der Erfindung abzuweichen, wie sie im Anspruch 1 definiert ist.Of course, are shown on the embodiment shown Changes possible without departing from the invention to deviate as defined in claim 1.

Claims (11)

  1. Hydraulic control device for controlling a single-acting motor (11), with a first proportional throttle valve (19) connected into an inflow line (18) and intended for raising a load, and with a second proportional throttle valve (24) connected into an outflow line (23) and intended for lowering the load, and also with a pressure balance (22) for load-compensated volume-flow control during raising, for which purpose the pressure drop occurring at the first proportional throttle valve (19) is led via two control lines (31, 32) to the spring-loaded pressure balance (22), characterized in that the pressure balance (22) is connected into a line section (26) assigned jointly to the inflow line (18) and to the outflow line (23), in that the first proportional throttle valve (19) controls a first (31) of the two control lines (31, 32), and in that this first control line (31) has connected into it a change-over valve (34), via which the pressure balance (22) can be changed over to a pressure load dependent on the second proportional throttle valve (24).
  2. Hydraulic control device according to Claim 1, characterized in that a non-return valve (21) protecting the motor (11) is connected into the inflow line (18) downstream of the first proportional throttle valve (19) and upstream of the joint line section (26).
  3. Hydraulic control device according to Claim 1 or 2, characterized in that the two proportional throttle valves (19, 24) are designed as two-way valves actuated electromagnetically counter to spring force.
  4. Hydraulic control device according to one of Claims 1 to 3, characterized in that the second proportional throttle valve (24) is designed in the manner of a seat valve.
  5. Hydraulic control device according to one of Claims 1 to 4, characterized in that the first proportional throttle valve (19) has a first control connection (28), from which the first control line (31) leads via the change-over valve (34) to the pressure balance (22) and loads the latter counter to the force of its regulating spring (33).
  6. Hydraulic control device according to Claim 5, characterized in that the first proportional throttle valve (19), in its working positions (36), leads the pressure upstream of its measuring throttle (37) to the first control connection (28) which, in the initial position (29), is relieved to a return duct (16) via a fourth control line (40) and which is also connected to the motor-side working connection (A) via a cross connection (30).
  7. Hydraulic control device according to Claim 5 or 6, characterized in that the pressure downstream of the measuring throttle (37) in the first proportional throttle valve (19) loads the pressure balance (22) in the same direction as the regulating spring (33) via a second control line (32).
  8. Hydraulic control device according to one of Claims 1 to 7, characterized in that the change-over valve (34) is connected via a third control line (35) to the outflow line (23) in a region upstream of the measuring throttle in the second proportional throttle valve (24).
  9. Hydraulic control device according to one of Claims 1 to 8, characterized in that the pressure in the inflow line (18) is tapped, in the region between the first proportional throttle valve (19) and the non-return valve (21), by a fifth control line (44) and is led via a second change-over valve (45) to a pressure-medium supply system which is designed, in particular, as a fixed-displacement pump (49) with a system pressure balance (47) operating as a reversing valve.
  10. Hydraulic control device according to one of Claims 1 to 9, characterized in that the two proportional throttle valves (19, 24) are activated by means of their proportional magnets by an electronic control unit (27).
  11. Hydraulic control device according to one of Claims 1 to 10, characterized in that the pressure balance (22) designed as a two-way valve is loaded by its regulating spring (33) into an open initial position (42) and by the prevailing pressure difference in the direction of a blocking position (43).
EP97112410A 1996-08-09 1997-07-19 Hydraulic control device Expired - Lifetime EP0823559B1 (en)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE19632201 1996-08-09
DE19632201A DE19632201A1 (en) 1996-08-09 1996-08-09 Hydraulic control device

Publications (3)

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

Family

ID=7802252

Family Applications (1)

Application Number Title Priority Date Filing Date
EP97112410A Expired - Lifetime EP0823559B1 (en) 1996-08-09 1997-07-19 Hydraulic control device

Country Status (2)

Country Link
EP (1) EP0823559B1 (en)
DE (2) DE19632201A1 (en)

Families Citing this family (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE29810860U1 (en) 1998-06-17 1998-08-13 Heilmeier & Weinlein Hydraulic control device
US6116263A (en) * 1998-07-23 2000-09-12 Hydraforce, Inc. Proportional priority flow regulator with reverse flow control
DE10023583B4 (en) * 2000-05-13 2012-05-24 Robert Bosch Gmbh Electrohydraulic lowering module
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 (en) * 2004-03-17 2005-10-06 Hydac System Gmbh Device for activating and actuating a vibrating mechanism
CN102979774B (en) * 2012-05-24 2015-05-06 山东弘宇农机股份有限公司 Control valve block special for tractor hydraulic suspension
CN105035979B (en) * 2015-08-05 2017-05-03 常德中联重科液压有限公司 Balance valve group and hydraulic system

Family Cites Families (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE3422978C2 (en) * 1984-06-22 1995-07-20 Bosch Gmbh Robert Device for controlling a hydraulic actuating device
DE3844400C2 (en) * 1988-12-30 1993-12-02 Rexroth Mannesmann Gmbh Valve arrangement for a hydraulic system
DE4307872C2 (en) * 1993-03-12 2001-05-17 Orenstein & Koppel Ag Load pressure-independent control of the speed of hydraulic control elements
DE9405872U1 (en) * 1994-04-08 1994-05-26 Heilmeier & Weinlein Lowering brake valve and flow control device for the high pressure hydraulics
DE4446145A1 (en) * 1994-12-23 1996-06-27 Bosch Gmbh Robert Hydraulic control in monoblock design for lifting and lowering a load with at least two electromagnetically actuated proportional directional control valve elements

Also Published As

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

Similar Documents

Publication Publication Date Title
DE102004050294B3 (en) Hydraulic valve arrangement
EP0546300B1 (en) Electrohydraulic control system
EP1369598B1 (en) Electro-hydraulic lifting control device for industrial use vehicles
EP2171285B1 (en) Hydraulic control arrangement
DE102005011395A1 (en) Hydraulic control arrangement
EP0016719B1 (en) Hydraulic motor control device
EP0777829B1 (en) Electro-hydraulic control device for a double acting consumer
DE4140408A1 (en) Electrohydraulic control of linear hydraulic actuator - has proportional flow control valve responding to pressure feedback to provide load compensating action
EP2142808A1 (en) Hydraulic control arrangement
EP0823559B1 (en) Hydraulic control device
DE102008064139A1 (en) Hydraulic control arrangement for pressure medium supply of differential cylinder of e.g. backhoe loader, has forward pressure medium supply path arranged downstream from control valve and lowering brake valve
DE102008064064A1 (en) Hydraulic control arrangement for supplying pressurizing medium to load of e.g. mobile working device, has brake valve arranged in return line, and feeding-sided way valve actuated towards opening position of brake valve depending on signal
EP0115590A2 (en) Hydraulic control device
EP2157320B1 (en) Hydraulic device for a hydro motor
DE19709958B4 (en) Hydrostatic drive system
EP2157319B1 (en) Hydraulic device for a hydro motor
EP2466154B1 (en) Electrohydraulic control device
EP0057355B1 (en) Hydraulic lifting device
EP3135924B1 (en) Hydraulic device
EP0219052A2 (en) Hydraulic control device
EP1729014B1 (en) Control block and section of a control block
DE10224740B4 (en) Hydraulic control valve device with a flow control device
DE10023583B4 (en) Electrohydraulic lowering module
EP1574720B1 (en) Electro-hydraulic control circuit and method of its deactivation
DE102008064136A1 (en) Hydraulic control arrangement for pressurizing medium supply to load, has valve unit, by which inlet to load is connected with pump, and return from load is connected with tank

Legal Events

Date Code Title Description
PUAI Public reference made under article 153(3) epc to a published international application that has entered the european phase

Free format text: ORIGINAL CODE: 0009012

AK Designated contracting states

Kind code of ref document: A2

Designated state(s): DE FR GB IT

PUAL Search report despatched

Free format text: ORIGINAL CODE: 0009013

AK Designated contracting states

Kind code of ref document: A3

Designated state(s): AT BE CH DE DK ES FI FR GB GR IE IT LI LU MC NL PT SE

RHK1 Main classification (correction)

Ipc: F15B 11/05

17P Request for examination filed

Effective date: 19990115

AKX Designation fees paid

Free format text: DE FR GB IT

RBV Designated contracting states (corrected)

Designated state(s): DE FR GB IT

GRAG Despatch of communication of intention to grant

Free format text: ORIGINAL CODE: EPIDOS AGRA

17Q First examination report despatched

Effective date: 20000904

GRAG Despatch of communication of intention to grant

Free format text: ORIGINAL CODE: EPIDOS AGRA

GRAH Despatch of communication of intention to grant a patent

Free format text: ORIGINAL CODE: EPIDOS IGRA

GRAH Despatch of communication of intention to grant a patent

Free format text: ORIGINAL CODE: EPIDOS IGRA

GRAA (expected) grant

Free format text: ORIGINAL CODE: 0009210

AK Designated contracting states

Kind code of ref document: B1

Designated state(s): DE FR GB IT

REF Corresponds to:

Ref document number: 59705151

Country of ref document: DE

Date of ref document: 20011206

REG Reference to a national code

Ref country code: GB

Ref legal event code: IF02

GBT Gb: translation of ep patent filed (gb section 77(6)(a)/1977)

Effective date: 20020124

ET Fr: translation filed
PLBE No opposition filed within time limit

Free format text: ORIGINAL CODE: 0009261

STAA Information on the status of an ep patent application or granted ep patent

Free format text: STATUS: NO OPPOSITION FILED WITHIN TIME LIMIT

26N No opposition filed
PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: FR

Payment date: 20040720

Year of fee payment: 8

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: FR

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20060331

REG Reference to a national code

Ref country code: FR

Ref legal event code: ST

Effective date: 20060331

PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: IT

Payment date: 20100729

Year of fee payment: 14

PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: GB

Payment date: 20100726

Year of fee payment: 14

GBPC Gb: european patent ceased through non-payment of renewal fee

Effective date: 20110719

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: IT

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20110719

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: GB

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20110719

PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: DE

Payment date: 20120927

Year of fee payment: 16

REG Reference to a national code

Ref country code: DE

Ref legal event code: R119

Ref document number: 59705151

Country of ref document: DE

Effective date: 20140201

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: DE

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20140201