EP0823559A2 - Hydraulic control device - Google Patents
Hydraulic control device Download PDFInfo
- Publication number
- EP0823559A2 EP0823559A2 EP97112410A EP97112410A EP0823559A2 EP 0823559 A2 EP0823559 A2 EP 0823559A2 EP 97112410 A EP97112410 A EP 97112410A EP 97112410 A EP97112410 A EP 97112410A EP 0823559 A2 EP0823559 A2 EP 0823559A2
- Authority
- EP
- European Patent Office
- Prior art keywords
- valve
- proportional throttle
- control
- throttle valve
- pressure
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
- Granted
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Classifications
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
- F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
- F15B11/00—Servomotor systems without provision for follow-up action; Circuits therefor
- F15B11/003—Systems with load-holding valves
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
- F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
- 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
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
- F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
- F15B2211/00—Circuits for servomotor systems
- F15B2211/20—Fluid pressure source, e.g. accumulator or variable axial piston pump
- F15B2211/205—Systems with pumps
- F15B2211/2053—Type of pump
- F15B2211/20538—Type of pump constant capacity
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
- F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
- F15B2211/00—Circuits for servomotor systems
- F15B2211/30—Directional control
- F15B2211/305—Directional control characterised by the type of valves
- F15B2211/30505—Non-return valves, i.e. check valves
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
- F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
- F15B2211/00—Circuits for servomotor systems
- F15B2211/30—Directional control
- F15B2211/305—Directional control characterised by the type of valves
- F15B2211/30525—Directional control valves, e.g. 4/3-directional control valve
- F15B2211/3053—In combination with a pressure compensating valve
- F15B2211/3054—In combination with a pressure compensating valve the pressure compensating valve is arranged between directional control valve and output member
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
- F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
- F15B2211/00—Circuits for servomotor systems
- F15B2211/30—Directional control
- F15B2211/31—Directional control characterised by the positions of the valve element
- F15B2211/3144—Directional control characterised by the positions of the valve element the positions being continuously variable, e.g. as realised by proportional valves
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
- F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
- F15B2211/00—Circuits for servomotor systems
- F15B2211/30—Directional control
- F15B2211/315—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
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
- F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
- F15B2211/00—Circuits for servomotor systems
- F15B2211/30—Directional control
- F15B2211/32—Directional control characterised by the type of actuation
- F15B2211/327—Directional control characterised by the type of actuation electrically or electronically
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
- F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
- F15B2211/00—Circuits for servomotor systems
- F15B2211/40—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
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
- F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
- F15B2211/00—Circuits for servomotor systems
- F15B2211/40—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
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
- F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
- F15B2211/00—Circuits for servomotor systems
- F15B2211/40—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
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
- F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
- F15B2211/00—Circuits for servomotor systems
- F15B2211/40—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
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
- F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
- F15B2211/00—Circuits for servomotor systems
- F15B2211/40—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
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
- F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
- F15B2211/00—Circuits for servomotor systems
- F15B2211/40—Flow control
- F15B2211/455—Control of flow in the feed line, i.e. meter-in control
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
- F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
- F15B2211/00—Circuits for servomotor systems
- F15B2211/50—Pressure control
- F15B2211/505—Pressure control characterised by the type of pressure control means
- F15B2211/50509—Pressure control characterised by the type of pressure control means the pressure control means controlling a pressure upstream of the pressure control means
- F15B2211/50536—Pressure control characterised by the type of pressure control means the pressure control means controlling a pressure upstream of the pressure control means using unloading valves controlling the supply pressure by diverting fluid to the return line
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
- F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
- F15B2211/00—Circuits for servomotor systems
- F15B2211/50—Pressure control
- F15B2211/51—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
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
- F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
- F15B2211/00—Circuits for servomotor systems
- F15B2211/50—Pressure control
- F15B2211/57—Control of a differential pressure
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
- F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
- F15B2211/00—Circuits for servomotor systems
- F15B2211/60—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
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
- F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
- F15B2211/00—Circuits for servomotor systems
- F15B2211/60—Circuit components or control therefor
- F15B2211/605—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
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
- F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
- F15B2211/00—Circuits for servomotor systems
- F15B2211/60—Circuit components or control therefor
- F15B2211/63—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
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
- F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
- F15B2211/00—Circuits for servomotor systems
- F15B2211/60—Circuit components or control therefor
- F15B2211/65—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
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
- F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
- F15B2211/00—Circuits for servomotor systems
- F15B2211/70—Output members, e.g. hydraulic motors or cylinders or control therefor
- F15B2211/705—Output members, e.g. hydraulic motors or cylinders or control therefor characterised by the type of output members or actuators
- F15B2211/7051—Linear output members
- F15B2211/7052—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)
Abstract
Description
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,
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. Fur 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.
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.
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
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 Rucklaufleitung
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
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
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
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
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
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
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
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
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
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
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
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
Selbstverständlich sind an der gezeigten Ausführungsform Änderungen möglich, ohne vom Gedanken der Erfindung abzuweichen.Of course, are shown on the embodiment shown Changes possible without departing from the spirit of the invention to deviate.
Claims (11)
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 true EP0823559A2 (en) | 1998-02-11 |
EP0823559A3 EP0823559A3 (en) | 1998-07-15 |
EP0823559B1 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) |
Cited By (5)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
EP0965763A1 (en) | 1998-06-17 | 1999-12-22 | HEILMEIER & WEINLEIN Fabrik für Oel-Hydraulik GmbH & Co. KG | Hydraulic control device |
EP0987444A3 (en) * | 1998-09-18 | 2002-07-31 | HydraForce, Inc. | Proportional priority flow regulator with reverse flow control |
WO2005093164A1 (en) * | 2004-03-17 | 2005-10-06 | Hydac System Gmbh | Device for controlling and actuating a vibrating mechanism |
CN102979774A (en) * | 2012-05-24 | 2013-03-20 | 山东弘宇机械有限公司 | Control valve block special for tractor hydraulic suspension |
CN105035979A (en) * | 2015-08-05 | 2015-11-11 | 常德中联重科液压有限公司 | Balance valve group and hydraulic system |
Families Citing this family (2)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
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 |
Citations (2)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
DE3422978A1 (en) | 1984-06-22 | 1986-01-02 | Robert Bosch Gmbh, 7000 Stuttgart | Arrangement for controlling a hydraulic actuating device |
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 |
Family Cites Families (3)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
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 Fabrik für Oel-Hydraulik GmbH & Co KG, 81673 München | Lowering brake valve and flow control device for the high pressure hydraulics |
-
1996
- 1996-08-09 DE DE19632201A patent/DE19632201A1/en not_active Withdrawn
-
1997
- 1997-07-19 EP EP97112410A patent/EP0823559B1/en not_active Expired - Lifetime
- 1997-07-19 DE DE59705151T patent/DE59705151D1/en not_active Expired - Lifetime
Patent Citations (2)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
DE3422978A1 (en) | 1984-06-22 | 1986-01-02 | Robert Bosch Gmbh, 7000 Stuttgart | Arrangement for controlling a hydraulic actuating device |
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 |
Cited By (7)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
EP0965763A1 (en) | 1998-06-17 | 1999-12-22 | HEILMEIER & WEINLEIN Fabrik für Oel-Hydraulik GmbH & Co. KG | Hydraulic control device |
US6176261B1 (en) | 1998-06-17 | 2001-01-23 | Heilmeier & Weinlein Fabrik F. Oel-Hydraulik Gmbh & Co. Kg | Hydraulic control device |
EP0987444A3 (en) * | 1998-09-18 | 2002-07-31 | HydraForce, Inc. | Proportional priority flow regulator with reverse flow control |
WO2005093164A1 (en) * | 2004-03-17 | 2005-10-06 | Hydac System Gmbh | Device for controlling and actuating a vibrating mechanism |
CN102979774A (en) * | 2012-05-24 | 2013-03-20 | 山东弘宇机械有限公司 | Control valve block special for tractor hydraulic suspension |
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 |
CN105035979A (en) * | 2015-08-05 | 2015-11-11 | 常德中联重科液压有限公司 | Balance valve group and hydraulic system |
Also Published As
Publication number | Publication date |
---|---|
EP0823559B1 (en) | 2001-10-31 |
DE59705151D1 (en) | 2001-12-06 |
DE19632201A1 (en) | 1998-02-12 |
EP0823559A3 (en) | 1998-07-15 |
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