EP0823559A2 - Hydraulische Steuereinrichtung - Google Patents
Hydraulische Steuereinrichtung 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
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.
Landscapes
- Engineering & Computer Science (AREA)
- Physics & Mathematics (AREA)
- Fluid Mechanics (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Fluid-Pressure Circuits (AREA)
Abstract
Description
Claims (11)
- Hydraulische Steuereinrichtung zum Steuern eines einfach wirkenden Motors mit einem in eine Zulaufleitung geschalteten, ersten Proportionaldrosselventil zum Heben einer Last und mit einem in eine Ablaufleitung geschalteten, zweiten Proportionaldrosselventil zum Senken der Last sowie mit einer Druckwaage zur lastkompensierten Volumenstromsteuerung beim Heben, wozu das am ersten Proportionaldrosselventil auftretende Druckgefälle über zwei Steuerleitungen zur federbelasteten Druckwaage geführt ist, dadurch gekennzeichnet, daß die Druckwaage (22) in einen der Zulaufleitung (18) und der Ablaufleitung (23) gemeinsam zugeordneten Leitungsabschnitt (26) geschaltet ist, daß das erste Proportionaldrosselventil (19) eine erste (31) der beiden Steuerleitungen (31, 32) steuert und daß in diese erste Steuerleitung (31) ein Wechselventil (34) geschaltet ist, über das die Druckwaage (22) auf eine Druckbeaufschlagung abhängig vom zweiten Proportionaldrosselventil (24) umschaltbar ist.
- Hydraulische Steuereinrichtung nach Anspruch 1, dadurch gekennzeichnet, daß in die Zulaufleitung (18) stromabwärts vom ersten Proportionaldrosselventil (19) und stromaufwärts vom gemeinsamen Leitungsabschnitt (26) ein den Motor (11) absicherndes Rückschlagventil (21) geschaltet ist.
- Hydraulische Steuereinrichtung nach Anspruch 1 oder 2, dadurch gekennzeichnet, daß beide Proportionaldrosselventile (19, 24) als elektromagnetisch gegen Federkraft betätigte Zwei-Wege-Ventile ausgebildet sind.
- Hydraulische Steuereinrichtung nach einem der Ansprüche 1 bis 3, dadurch gekennzeichnet, daß das zweite Proportionaldrosselventil (24) in Sitzventilbauweise ausgeführt ist.
- Hydraulische Steuereinrichtung nach einem der Ansprüche 1 bis 4, dadurch gekennzeichnet, daß das erste Proportionaldrosselventil (19) einen ersten Steueranschluß (28) aufweist, von dem die erste Steuerleitung (31) über das Wechselventil (34) zur Druckwaage (22) führt und diese gegen die Kraft ihrer Regelfeder (33) beaufschlagt.
- Hydraulische Steuereinrichtung nach Anspruch 5, dadurch gekennzeichnet, daß das erste Proportionaldrosselventil (19) in seinen Arbeitsstellungen (36) den Druck stromaufwärts seiner Meßdrossel (37) zum ersten Steueranschluß (28) führt, welcher in Ausgangsstellung (29) über eine vierte Steuerleitung (40) zu einem Rücklaufkanal (16) entlastet ist und welcher zudem über eine Querverbindung (30) dem motorseitigen Arbeitsanschluß (A) Verbindung hat.
- Hydraulische Steuereinrichtung nach Anspruch 5 oder 6, dadurch gekennzeichnet, daß der Druck stromabwärts der Meßdrossel (37) im ersten Proportionaldrosselventil (19) über eine zweite Steuerleitung (32) die Druckwaage (22) gleichsinnig zur Regelfeder (33) beaufschlagt.
- Hydraulische Steuereinrichtung nach einem der Ansprüche 1 bis 7, dadurch gekennzeichnet, daß das Wechselventil (34) über eine dritte Steuerleitung (35) mit der Ablaufleitung (23) in einem Bereich stromaufwärts von der Meßdrossel im zweiten Proportionaldrosselventil (24) Verbindung hat.
- Hydraulische Steuereinrichtung nach einem der Ansprüche 1 bis 8, dadurch gekennzeichnet, daß der Druck in der Zulaufleitung (18) im Bereich zwischen erstem Proportionaldrosselventil (19) und Rückschlagventil (21) von einer fünften Steuerleitung (44) abgegriffen und über ein zweites Wechselventil (45) zu einem Druckmittelversorgungssystem geführt ist, das insbesondere als Konstantpumpe (49) mit einer als Umschaltventil arbeitenden System-Druckwaage (47) ausgebildet ist.
- Hydraulische Steuereinrichtung nach einem der Ansprüche 1 bis 9, dadurch gekennzeichnet, daß beide Proportionaldrosselventile (19, 24) mit ihren Proportionalmagneten von einem elektronischen Steuergerät (27) angesteuert werden.
- Hydraulische Steuereinrichtung nach einem der Ansprüche 1 bis 10, dadurch gekennzeichnet, daß die als Zwei-Wege-Ventil ausgeführte Druckwaage (22) von ihrer Regelfeder (33) in eine offene Ausgangsstellung (42) und von der anliegenden Druckdifferenz in Richtung einer Sperrstellung (43) belastet wird.
Applications Claiming Priority (2)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
DE19632201A DE19632201A1 (de) | 1996-08-09 | 1996-08-09 | Hydraulische Steuereinrichtung |
DE19632201 | 1996-08-09 |
Publications (3)
Publication Number | Publication Date |
---|---|
EP0823559A2 true EP0823559A2 (de) | 1998-02-11 |
EP0823559A3 EP0823559A3 (de) | 1998-07-15 |
EP0823559B1 EP0823559B1 (de) | 2001-10-31 |
Family
ID=7802252
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
EP97112410A Expired - Lifetime EP0823559B1 (de) | 1996-08-09 | 1997-07-19 | Hydraulische Steuereinrichtung |
Country Status (2)
Country | Link |
---|---|
EP (1) | EP0823559B1 (de) |
DE (2) | DE19632201A1 (de) |
Cited By (5)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
EP0965763A1 (de) | 1998-06-17 | 1999-12-22 | HEILMEIER & WEINLEIN Fabrik für Oel-Hydraulik GmbH & Co. KG | Hydraulische Steuervorrichtung |
EP0987444A3 (de) * | 1998-09-18 | 2002-07-31 | HydraForce, Inc. | Proportionales Durchflussregelventil mit Vorrang und Rückflussregelung |
WO2005093164A1 (de) * | 2004-03-17 | 2005-10-06 | Hydac System Gmbh | Vorrichtung zum ansteuern und betätigen einer rüttelmechanik |
CN102979774A (zh) * | 2012-05-24 | 2013-03-20 | 山东弘宇机械有限公司 | 一种拖拉机液压悬挂专用控制阀块 |
CN105035979A (zh) * | 2015-08-05 | 2015-11-11 | 常德中联重科液压有限公司 | 平衡阀组和液压*** |
Families Citing this family (2)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
DE10023583B4 (de) * | 2000-05-13 | 2012-05-24 | Robert Bosch Gmbh | Elektrohydraulischer Senken-Modul |
US6457487B1 (en) * | 2001-05-02 | 2002-10-01 | Husco International, Inc. | Hydraulic system with three electrohydraulic valves for controlling fluid flow to a load |
Citations (2)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
DE3422978A1 (de) | 1984-06-22 | 1986-01-02 | Robert Bosch Gmbh, 7000 Stuttgart | Vorrichtung zur steuerung einer hydraulischen stelleinrichtung |
DE4446145A1 (de) | 1994-12-23 | 1996-06-27 | Bosch Gmbh Robert | Hydraulische Steuerung in Monoblockbauweise zum Heben und Senken einer Last mit mindestens zwei elektromagnetisch betätigbaren Proportionalwegeventilelementen |
Family Cites Families (3)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
DE3844400C2 (de) * | 1988-12-30 | 1993-12-02 | Rexroth Mannesmann Gmbh | Ventilanordnung für ein hydraulisches System |
DE4307872C2 (de) * | 1993-03-12 | 2001-05-17 | Orenstein & Koppel Ag | Lastdruckunabhängige Steuerung der Geschwindigkeit von hydraulischen Stellelementen |
DE9405872U1 (de) * | 1994-04-08 | 1994-05-26 | Heilmeier & Weinlein Fabrik für Oel-Hydraulik GmbH & Co KG, 81673 München | Senkbremsventil und Mengenregel-Vorrichtung für die Hochdruck-Hydraulik |
-
1996
- 1996-08-09 DE DE19632201A patent/DE19632201A1/de not_active Withdrawn
-
1997
- 1997-07-19 DE DE59705151T patent/DE59705151D1/de not_active Expired - Lifetime
- 1997-07-19 EP EP97112410A patent/EP0823559B1/de not_active Expired - Lifetime
Patent Citations (2)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
DE3422978A1 (de) | 1984-06-22 | 1986-01-02 | Robert Bosch Gmbh, 7000 Stuttgart | Vorrichtung zur steuerung einer hydraulischen stelleinrichtung |
DE4446145A1 (de) | 1994-12-23 | 1996-06-27 | Bosch Gmbh Robert | Hydraulische Steuerung in Monoblockbauweise zum Heben und Senken einer Last mit mindestens zwei elektromagnetisch betätigbaren Proportionalwegeventilelementen |
Cited By (7)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
EP0965763A1 (de) | 1998-06-17 | 1999-12-22 | HEILMEIER & WEINLEIN Fabrik für Oel-Hydraulik GmbH & Co. KG | Hydraulische Steuervorrichtung |
US6176261B1 (en) | 1998-06-17 | 2001-01-23 | Heilmeier & Weinlein Fabrik F. Oel-Hydraulik Gmbh & Co. Kg | Hydraulic control device |
EP0987444A3 (de) * | 1998-09-18 | 2002-07-31 | HydraForce, Inc. | Proportionales Durchflussregelventil mit Vorrang und Rückflussregelung |
WO2005093164A1 (de) * | 2004-03-17 | 2005-10-06 | Hydac System Gmbh | Vorrichtung zum ansteuern und betätigen einer rüttelmechanik |
CN102979774A (zh) * | 2012-05-24 | 2013-03-20 | 山东弘宇机械有限公司 | 一种拖拉机液压悬挂专用控制阀块 |
CN102979774B (zh) * | 2012-05-24 | 2015-05-06 | 山东弘宇农机股份有限公司 | 一种拖拉机液压悬挂专用控制阀块 |
CN105035979A (zh) * | 2015-08-05 | 2015-11-11 | 常德中联重科液压有限公司 | 平衡阀组和液压*** |
Also Published As
Publication number | Publication date |
---|---|
EP0823559B1 (de) | 2001-10-31 |
DE59705151D1 (de) | 2001-12-06 |
EP0823559A3 (de) | 1998-07-15 |
DE19632201A1 (de) | 1998-02-12 |
Similar Documents
Publication | Publication Date | Title |
---|---|---|
DE102004050294B3 (de) | Hydraulische Ventilanordnung | |
DE4140409A1 (de) | Elektrohydraulische steuereinrichtung | |
EP0016719B1 (de) | Vorrichtung zum Steuern eines Hydromotors | |
DE102005011395A1 (de) | Hydraulische Steueranordnung | |
DE102012203386A1 (de) | Steueranordnung | |
EP0823559B1 (de) | Hydraulische Steuereinrichtung | |
DE102004025322A1 (de) | Hydraulische Ventilanordnung | |
EP0115590B1 (de) | Hydraulische Steuereinrichtung | |
DE102008064064A1 (de) | Hydraulische Steueranordnung | |
DE102007014550A1 (de) | Ventilanordnung | |
DE19709958B4 (de) | Hydrostatisches Antriebssystem | |
DE19646427B4 (de) | Ventilanordnung | |
EP2157320B1 (de) | Hydrauliksteuerung für einen Hydromotor | |
WO2003087585A1 (de) | Hydraulische steueranordnung in load-sensing technik | |
EP0057355B1 (de) | Hydraulische Hubeinrichtung | |
EP2466154B1 (de) | Elektrohydraulische Steuervorrichtung | |
EP1729014B1 (de) | Steuerblock und Steuerblocksektion | |
EP2157319B1 (de) | Hydrauliksteuerung für einen Hydromotor | |
EP1574720B1 (de) | Elektrohydraulische Steuervorrichtung und Verfahren zu ihrer Abschaltung | |
EP1253327B1 (de) | Hydraulische Steuereinrichtung | |
DE10224740B4 (de) | Hydraulische Steuerventileinrichtung mit einer Stromregeleinrichtung | |
DE10114042B4 (de) | Hydraulikanlage für zwei Konstantpumpen | |
DE4026849C2 (de) | Ventilanordnung zum Erzeugen eines Steuerdrucks in einer hydraulischen Anlage | |
DE10119276B4 (de) | Hydraulischer Steuerkreis | |
DE3938560A1 (de) | Hydraulische steuereinrichtung |
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 |