EP1629156B1 - Hydraulic control arrangement - Google Patents

Hydraulic control arrangement Download PDF

Info

Publication number
EP1629156B1
EP1629156B1 EP04739453A EP04739453A EP1629156B1 EP 1629156 B1 EP1629156 B1 EP 1629156B1 EP 04739453 A EP04739453 A EP 04739453A EP 04739453 A EP04739453 A EP 04739453A EP 1629156 B1 EP1629156 B1 EP 1629156B1
Authority
EP
European Patent Office
Prior art keywords
pressure
control
valve
pressure compensator
pump
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
EP04739453A
Other languages
German (de)
French (fr)
Other versions
EP1629156A1 (en
Inventor
Wolfgang Kauss
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.)
Bosch Rexroth AG
Original Assignee
Bosch Rexroth AG
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 Bosch Rexroth AG filed Critical Bosch Rexroth AG
Publication of EP1629156A1 publication Critical patent/EP1629156A1/en
Application granted granted Critical
Publication of EP1629156B1 publication Critical patent/EP1629156B1/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
    • F15B11/16—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
    • F15B11/163—Servomotor systems without provision for follow-up action; Circuits therefor with two or more servomotors with sensing of servomotor demand or load for sharing the pump output equally amongst users or groups of users, e.g. using anti-saturation, pressure compensation
    • E—FIXED CONSTRUCTIONS
    • E02—HYDRAULIC ENGINEERING; FOUNDATIONS; SOIL SHIFTING
    • E02F—DREDGING; SOIL-SHIFTING
    • E02F9/00—Component parts of dredgers or soil-shifting machines, not restricted to one of the kinds covered by groups E02F3/00 - E02F7/00
    • E02F9/20—Drives; Control devices
    • E02F9/22—Hydraulic or pneumatic drives
    • E02F9/2221—Control of flow rate; Load sensing arrangements
    • E02F9/2225—Control of flow rate; Load sensing arrangements using pressure-compensating valves
    • E—FIXED CONSTRUCTIONS
    • E02—HYDRAULIC ENGINEERING; FOUNDATIONS; SOIL SHIFTING
    • E02F—DREDGING; SOIL-SHIFTING
    • E02F9/00—Component parts of dredgers or soil-shifting machines, not restricted to one of the kinds covered by groups E02F3/00 - E02F7/00
    • E02F9/20—Drives; Control devices
    • E02F9/22—Hydraulic or pneumatic drives
    • E02F9/226—Safety arrangements, e.g. hydraulic driven fans, preventing cavitation, leakage, overheating
    • 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
    • F15B20/00—Safety arrangements for fluid actuator systems; Applications of safety devices in fluid actuator systems; Emergency measures for fluid actuator systems
    • 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
    • F15B2211/30525—Directional control valves, e.g. 4/3-directional control valve
    • F15B2211/3053—In combination with a pressure compensating valve
    • F15B2211/30555—Inlet and outlet of the pressure compensating valve being connected to the 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
    • F15B2211/30—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
    • F15B2211/31541—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 multiple output members
    • 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
    • F15B2211/321—Directional control characterised by the type of actuation mechanically
    • F15B2211/324—Directional control characterised by the type of actuation mechanically manually, e.g. by using a lever or pedal
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/30—Directional control
    • F15B2211/32—Directional control characterised by the type of actuation
    • F15B2211/329—Directional control characterised by the type of actuation actuated by fluid pressure
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/30—Directional control
    • F15B2211/35—Directional control combined with flow control
    • F15B2211/351—Flow control by regulating means in 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
    • F15B2211/40—Flow control
    • F15B2211/415—Flow control characterised by the connections of the flow control means in the circuit
    • F15B2211/41563—Flow control characterised by the connections of the flow control means in the circuit being connected to a pressure source and a return line
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/40—Flow control
    • F15B2211/45—Control of bleed-off flow, e.g. control of bypass flow to the return line

Definitions

  • the invention relates to a hydraulic control arrangement for load-independent control of a consumer according to the preamble of patent claim 1.
  • Mobile implements such as mini excavators and compact excavators are increasingly equipped with hydraulic control arrangements, which distribute the pressure medium volume flow of a single pump load-independent on the connected consumers.
  • the control of these consumers is carried out, for example, via a LUDV control block, which has a plurality of each one of the consumer associated valve discs.
  • a continuously adjustable directional control valve is accommodated, to which a pressure-compensating LUDV pressure compensator is assigned.
  • the pressure medium flowing to the consumer first flows through a metering orifice formed by the continuously adjustable directional control valve and then through the pressure compensator.
  • the control piston of this pressure compensator is acted upon at its front by the pressure prevailing between the metering orifice and the pressure compensator.
  • This pressure is reduced compared to the pump pressure by the largely load pressure and pump pressure-independent pressure drop across the metering orifice.
  • In the closing direction of the control piston of the pressure compensator is acted upon by the highest load pressure of all simultaneously operated hydraulic consumers. This means that there is also the highest load pressure between the metering orifice and the pressure compensator, and that the pressure medium partial quantities flowing to all hydraulic actuators operated simultaneously are independent of the individual load pressures Consumers are reduced in the same ratio, if at an increase in the opening cross-sections of the metering orifice, the maximum flow of the associated pump is achieved.
  • the invention has for its object to provide a hydraulic control arrangement in which the locking of the mechanically actuated load is simplified.
  • the LUDV pressure compensators associated with the mechanically operated directional control valves are acted on by a spring acting in the closing direction.
  • the load pressure signaling line common to all consumers is connected to the tank via a current regulator, so that a small amount of control oil always flows to the tank.
  • a safety valve is arranged, via which the connection of the load pressure signaling line to the current regulator can be shut off.
  • An area upstream of the switching valve is connected via a nozzle to a portion of the pressure medium flow path between the pump and the LUDV pressure compensator.
  • the connection of the load pressure signaling line is shut off to the tank and the tapped through the nozzle pressure in a connected to the load pressure signaling line rear control chamber effective, so that the LUDV pressure compensator is brought into its closed position.
  • the load pressure sensing line is connected downstream of the flow regulator to a pump control. After shutting off the load pressure signaling line, the control pressure at the pump control then drops towards the tank so that the pump can only generate the standby pressure.
  • the solution according to the invention is characterized by a very simple structure and a good response.
  • the upstream of the safety valve disposed nozzle is either integrated into the pressure balance, which is reported via this nozzle the voltage applied to the pressure compensator input pressure in the rear control chamber, so that the pressure compensator piston is pressure balanced and is closed by the force of the additional spring ,
  • this nozzle is provided in a branch line which extends from an area upstream of the directional control valve to an area upstream of the safety valve.
  • the pump pressure applied upstream of the directional control valve is reported to the rear pressure chamber.
  • the consumer supplying pump is designed as a fixed displacement pump, which is associated with a differential pressure regulator, which is controlled in response to the load pressure in the load pressure signaling line.
  • the hydraulically operated consumers are each driven by means of a pilot control device, which is assigned its own control oil supply.
  • a shut-off valve is provided, via which the control oil supply of the pilot control device is interrupted to shut off the hydraulically actuated consumers, so that their Valve spool are moved back to the spring-biased home position. According to the invention then takes place via the switching of this shut-off valve and an actuation of the safety valve.
  • valve discs 2, 4 consumers of the mobile implement, such as a wheeled excavator can be controlled.
  • a consumer such as a hydraulic motor 6 of a traction drive mechanically via a lever
  • the function of another consumer for example, a hydraulic cylinder actuating the boom 8 is actuated hydraulically.
  • the pressure medium supply of the control block 1 takes place in the illustrated embodiment via a constant displacement pump 10 whose flow is controlled by a differential pressure regulator 12 in response to the highest load pressure of the actuated consumers.
  • This load pressure is via an LS line 14 to a in Closing direction effective control surface of the differential pressure regulator 12 out, while acting in the opening direction control surface is acted upon by the pump pressure.
  • Each of the valve disks 2, 4 has a continuously adjustable directional control valve 16, which in each case has directional parts 20, 22 and a speed part 18.
  • the direction parts 20, 22 control the pressure medium flow to and from the consumer and the speed part 18 determines the pressure medium volume flow, which is adjustable by controlling a metering orifice. Downstream of this metering orifice, in each case a LUDV pressure compensator 24 is provided which, as described at the outset, keeps the pressure drop across the metering orifice constant regardless of the load.
  • Each pressure compensator 24 is acted upon in the control position in the opening direction of the individual load pressure of the associated load and in the closing direction of the highest load pressure, which is tapped via the LS line 14.
  • the directional control valve 16 of the valve disc 2 is mechanically operated, for example via a lever, while the directional valve 16 of the valve disc 4 is actuated via a pilot valve 26, which consists in principle of pressure reducing valves, at the input of a control oil supply 28 is applied pressure applied and at whose output in response to the adjustment of the pilot control device 26, a control pressure is generated, which is applied to actuate the directional control valve 16 to control chambers 31, 33 of the directional control valve 16 of the valve disk 4.
  • an electrically operated shut-off valve 30 is provided, via which the control oil supply 28 with a tank T is connectable. In the operating position, this shut-off valve 30 is switched so that the pilot control device 26 is supplied with control oil.
  • the area downstream of the shut-off valve 30 is connected via a control line 32 to a control chamber of a safety valve 34, which is designed as a 2/2 way valve.
  • the safety valve 34 is biased by a spring into a switching position in which the LS line 14 is shut off.
  • the control oil supply pressure provided by the control oil supply 28 acts in the control space of the safety valve 34, so that it is brought into a passage position against the force of the spring.
  • a current regulator 36 is arranged, via which the LS line 14 is connected to the tank T. That through the LS line flows in the open position of the safety valve 34 from a constant control oil volume flow to the tank T from down, the size of which depends on the setting of the flow control valve 36.
  • the pressure in the LS line 14 is limited by a pressure limiting valve 37, which is arranged between the flow control valve 36 and the safety valve 34.
  • valve disc 2 A structure of the valve disc 2 will be explained below with reference to the enlarged view in FIG.
  • Each of the above-described valve discs 2,4 has a pressure port P to which the pump pressure is applied, a tank port S connected to the tank, an LS port LS connected to the LS port 14, and two with the consumer, in the present case the hydraulic motor 6 connected working ports A, B.
  • a valve spool 38 of the directional valve 16 of the valve disc 2 is biased via a centering spring assembly 40 in its illustrated basic position.
  • valve spool 38 is guided in a valve bore 44, which in the radial direction to a pressure chamber 46, an inlet chamber 48, two approximately symmetrically to the pressure chamber 20 disposed drain chambers 50, 52, two on both sides thereof arranged working chambers 54, 56 and two adjacent thereto tank chambers 58, 60 is extended.
  • the valve spool 16 has a central measuring diaphragm collar 62 which, together with the remaining annular web between the pressure chamber 46 and the inlet chamber 48, determines a measuring diaphragm forming the speed part 18.
  • a measuring diaphragm collar 62 On both sides of this measuring diaphragm collar 62, two control collars 64, 66 and two tank collars 68, 70 of the directional part 20, 22 are arranged on the valve slide 38.
  • the pressure chamber 46 is connected to the pressure port P and the two tank chambers 58, 60 are connected to the tank port S.
  • the inlet chamber 48 is connected via an inlet channel 72 to the inlet of the pressure compensator 24. Their output is connected via two drainage channels 74, 76 with the discharge chamber 50, 52 and the two working chambers 54, 56 via working channels 78, 80 to the working port A and B respectively.
  • the pressure compensator 24 is shown in its closed position. It has a pressure compensator piston 84, which is guided axially displaceably in a pressure balance bore 82.
  • the pressure balance piston 84 is designed as a stepped piston, wherein the smaller piston surface is supported in the closed position on a shoulder 86 of the inlet channel 72.
  • the shoulder surface 86 of the pressure compensator piston 84 facing this shoulder 86 is in the control position with the pressure in the drainage channels 74, 76, i. applied to the load pressure on the associated consumer.
  • the larger diameter (top of Figure 2) of the pressure compensator piston 84 immersed in a rear control chamber 88 which is connected via an LS channel 90 to the LS port.
  • the pressure compensator piston 84 has an axial bore 92 which opens out in the stepped-back end face and opens out via a load-indicating nozzle 94 in a transverse bore 96 passing through the pressure compensator piston 84 in the transverse direction.
  • the latter is shut off in the closing and control position of the pressure compensator piston 84 by the peripheral walls of the pressure compensator bore 86 and is only opened when the pressure compensator 24 is fully open.
  • the control oil then flows from the input of the pressure compensator via the load indicator in the control chamber 88 and thus in the LS line 14, so that substantially the load pressure of the consumer as the highest load pressure in the LS line 14 is applied.
  • an additional nozzle 98 is provided in extension of the axial bore 92 beyond the transverse bore 96 through which the axial bore 92 is always connected to the control chamber 88.
  • the pressure compensator piston 84 is further biased by a spring 100 against the shoulder 62 in its closed position in which the outer peripheral edge 102 of the gradation of the pressure compensator piston 84, the connection between the inlet channel 72 and the drainage channels 74, 76 has been controlled.
  • the spring 100 is supported on a screwed into the pressure balance bore 82 screw plug 104.
  • the valve disk 4 assigned to the hydraulic function has, in principle, the same structure, although the pressure compensator piston 106 is not formed with a nozzle 98 and thus there is no permanent connection between the axial bore 108 and the control chamber 110. Furthermore, the pressure compensator piston 106 is not biased by a spring into its closed position.
  • the valve slide 16 When the hydraulic motor 6 is actuated, the valve slide 16 is moved by hand via the adjusting lever into an open position, so that the measuring diaphragm of the speed part 18 is opened.
  • the pump pressure which acts against the effective in the closing direction of the load pressure.
  • the pump pressure increases until the pressure compensator piston 84 opens the connection to the drainage channels 74, 76.
  • the pressure medium can then flow via the direction parts 20, 22 to the hydraulic motor 6 and from this back to the tank. If only the hydraulic motor 6 is actuated, the pressure compensator 24 is brought by the load pressure on the hydraulic motor 6 in the fully open position, so that this load pressure is reported in the LS line.
  • shut-off valve 30 the control oil supply of the pilot control device 26 is shut off, so that the directional control valve 16 of the valve disk 4 is moved back to its basic position and correspondingly no activation of the hydraulic cylinder 8 takes place.
  • the shut-off valve 30 is in the control line 32 also the tank pressure, so that the opened safety valve 34 is brought into its closed position.
  • the spring chamber of the differential pressure regulator 12 is relieved via the flow regulator 36 to the tank T out, so that the differential pressure regulator 12 can only generate the standby pressure.
  • control oil volume flow is interrupted by the safety valve 34 of the pressure compensator 24 of the valve disc 2 via the axial bore 82, the transverse bore 96, the nozzle 98 and the LS line 14 and thus no pressure drop across the pressure compensator 24 more arises due to this control oil flow is the pressure compensator piston 84 pressure balanced and by the force of the spring 100 in its closed position pushed back and thus shut off the connection to the hydraulic motor 6.
  • shut-off valve 30 all mechanically operated functions are thus locked by actuation of the shut-off valve 30.
  • the dimensioning of the spring 100 and the cross section of the nozzle 98 is selected so that on the one hand a secure locking of the mechanically actuated valve discs 2 is possible, but on the other hand, the above-described LUDV function is only slightly affected.
  • FIG. 1 shows a variant of the invention, according to which the nozzle 98 'is not arranged in the pressure compensator piston 84 but in a branch line 112, via which the pressure medium flow path downstream of the pump 10 and upstream of the metering orifice with a portion of the LS line 14 upstream of Safety valve 34 is connected.
  • a control oil volume flow constantly flows via the flow regulator 36 to the tank T via this nozzle 98 '.
  • the safety valve 34 acts on the nozzle 98 ', the pressure at the output of the pump in the load-sensing line 14 and thus in the control chamber 88, so that the pressure compensator 24 is also returned to its closed position.
  • a hydraulic control arrangement for controlling a consumer, with at least one mechanically actuated, continuously adjustable directional control valve, which is followed by a LUDV pressure compensator.
  • the control arrangement is designed with a spring acting on the pressure compensator piston in a closed position.
  • a highest load pressure of all consumers leading LS line is connected via a current regulator to a tank, with the current regulator and a pump control in the sense of reducing the delivery volume is relieved.
  • the LUDV pressure compensator is pressure compensated via a nozzle via which a connection between the LS line and a portion of the Druckstoffströmungspfades downstream of the pump and upstream of the output of the pressure compensator is made.
  • this nozzle is integrated into the pressure compensator piston.

Landscapes

  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Fluid Mechanics (AREA)
  • Mechanical Engineering (AREA)
  • Mining & Mineral Resources (AREA)
  • Civil Engineering (AREA)
  • Structural Engineering (AREA)
  • Chemical & Material Sciences (AREA)
  • Analytical Chemistry (AREA)
  • Fluid-Pressure Circuits (AREA)
  • Operation Control Of Excavators (AREA)

Abstract

A hydraulic control arrangement is disclosed for the control of a consumer, comprising at least one mechanically operated continuously adjustable distribution valve with a subsequent LUDV pressure compensator down the line. In order to lock the consumer the control arrangement is provided with a spring holding the pressure compensator piston in a closed position. Furthermore, the LS line carrying the highest load pressure of all consumers is connected to a reservoir by means of a flow regulator, wherein the pump control may also be relieved by the flow regulator in the sense of a reduction of the pumped volume. According to the invention, the LUDV pressure compensator is pressure-compensated by means of a nozzle through which a connection between the LS line and a portion of the pressure medium flow path downstream of the pump and upstream of the outlet of the pressure compensator is generated. Said nozzle is preferably integrated in the pressure compensator piston.

Description

Die Erfindung betrifft eine hydraulische Steueranordnung zur lastunabhängigen Ansteuerung eines Verbrauchers gemäß dem Oberbegriff des Patentanspruchs 1.The invention relates to a hydraulic control arrangement for load-independent control of a consumer according to the preamble of patent claim 1.

Mobile Arbeitsgeräte, beispielsweise Minibagger und Kompaktbagger werden zunehmend mit hydraulischen Steueranordnungen ausgestattet, welche den Druckmittelvolumenstrom einer einzigen Pumpe lastunabhängig auf die angeschlossenen Verbraucher verteilen. Die Ansteuerung dieser Verbraucher erfolgt dabei beispielsweise über einen LUDV-Steuerblock, der eine Vielzahl von jeweils einem der Verbraucher zugeordneten Ventilscheiben hat. In jeder Ventilscheibe ist ein stetig verstellbares Wegeventil aufgenommen, dem eine druckkompensierende LUDV-Druckwaage zugeordnet ist. Das zum Verbraucher strömende Druckmittel fließt zunächst durch eine durch das stetig verstellbare Wegeventil gebildete Zumessblende und dann durch die Druckwaage. Der Regelkolben dieser Druckwaage wird an seiner Vorderseite von dem zwischen der Zumessblende und der Druckwaage herrschenden Druck beaufschlagt. Dieser Druck ist gegenüber dem Pumpendruck um den weitgehend lastdruck-und pumpendruckunabhängigen Druckabfall über der Zumessblende reduziert. In Schließrichtung wird der Regelkolben der Druckwaage vom höchsten Lastdruck aller gleichzeitig betätigten hydraulischen Verbraucher beaufschlagt. Das bedeutet, dass auch zwischen der Zumessblende und der Druckwaage der höchste Lastdruck herrscht und dass die zu allen gleichzeitig betätigten hydraulischen Verbraucher strömenden Druckmittelteilmengen unabhängig von den einzelnen Lastdrücken der Verbraucher im gleichen Verhältnis verringert werden, wenn bei einer Vergrößerung der Öffnungsquerschnitte der Zumessblende die maximale Fördermenge der zugeordneten Pumpe erreicht wird.Mobile implements, such as mini excavators and compact excavators are increasingly equipped with hydraulic control arrangements, which distribute the pressure medium volume flow of a single pump load-independent on the connected consumers. The control of these consumers is carried out, for example, via a LUDV control block, which has a plurality of each one of the consumer associated valve discs. In each valve disc, a continuously adjustable directional control valve is accommodated, to which a pressure-compensating LUDV pressure compensator is assigned. The pressure medium flowing to the consumer first flows through a metering orifice formed by the continuously adjustable directional control valve and then through the pressure compensator. The control piston of this pressure compensator is acted upon at its front by the pressure prevailing between the metering orifice and the pressure compensator. This pressure is reduced compared to the pump pressure by the largely load pressure and pump pressure-independent pressure drop across the metering orifice. In the closing direction of the control piston of the pressure compensator is acted upon by the highest load pressure of all simultaneously operated hydraulic consumers. This means that there is also the highest load pressure between the metering orifice and the pressure compensator, and that the pressure medium partial quantities flowing to all hydraulic actuators operated simultaneously are independent of the individual load pressures Consumers are reduced in the same ratio, if at an increase in the opening cross-sections of the metering orifice, the maximum flow of the associated pump is achieved.

Bei Minibaggern und Kompaktbaggern werden häufig die Arbeitsfunktionen Ausleger, Löffel, Stiel und Drehen über hydraulische Vorsteuergeräte betätigt, während die Funktionen Fahren, Knicken, Planierschild und Hammer meist aus Kostengründen mechanisch betätigt werden. Gesetzlich sind Sicherheitseinrichtungen vorgeschrieben, welche der Fahrer beim Verlassen des Fahrerplatzes aktivieren muss, um die mechanisch und hydraulisch betätigten Funktionen abzuschalten. Das Abschalten der hydraulisch betätigten Funktionen ist relativ einfach, da lediglich die Steuerölversorgung des Vorsteuergerätes unterbrochen werden muss. Schwieriger ist die Verriegelung der mechanisch betätigten Funktionen. Es ist bekannt, mechanische form- oder kraftschlüssige Verriegelungen zu verwenden, die jedoch vergleichsweise aufwendig zu realisieren sind.In mini excavators and compact excavators often the work functions boom, spoon, handle and turn are operated by hydraulic pilot units, while the functions driving, buckling, dozer blade and hammer are mechanically operated mostly for cost reasons. By law, safety devices are prescribed which the driver must activate when leaving the driver's seat in order to switch off the mechanically and hydraulically actuated functions. Switching off the hydraulically operated functions is relatively simple, since only the pilot oil supply of the pilot control unit must be interrupted. More difficult is the locking of the mechanically operated functions. It is known to use mechanical positive or non-positive locking, but they are relatively complex to implement.

In der US 6,526,747 B2 ist eine Lösung offenbart, bei der die hydraulisch und mechanisch betätigten Funktionen dadurch verriegelt werden, dass die LUDV-Druckwaagen in Schließrichtung mit dem Pumpendruck beaufschlagt werden und somit die Druckmittelzufuhr zum Verbraucher absperren. Dieser Pumpendruck wirkt bei Betätigung der Sicherheitseinrichtung über ein Wegeventil in der allen Verbrauchern gemeinsamen Lastdruckleitung des Steuerblocks, das über ein Abschaltventil betätigt wird, wobei der Druck in der Steuerölversorgung zum Umschalten des Wegeventils genutzt wird. Eine derartige Lösung erfordert einen erheblichen schaltungstechnischen Aufwand.In US 6,526,747 B2, a solution is disclosed in which the hydraulically and mechanically operated functions are locked by the fact that the LUDV pressure compensators are acted upon in the closing direction with the pump pressure and thus shut off the pressure medium supply to the consumer. This pump pressure acts upon actuation of the safety device via a directional control valve in the common load pressure line of the control block, which is actuated via a shut-off valve, wherein the pressure in the control oil supply is used to switch the directional control valve. Such a solution requires a considerable circuit complexity.

Demgegenüber liegt der Erfindung die Aufgabe zugrunde, eine hydraulische Steueranordnung zu schaffen, bei der das Verriegeln der mechanisch betätigten Verbraucher vereinfacht ist.In contrast, the invention has for its object to provide a hydraulic control arrangement in which the locking of the mechanically actuated load is simplified.

Diese Aufgabe wird durch eine hydraulische Steueranordnung mit den Merkmalen des Patentanspruches 1 gelöst.This object is achieved by a hydraulic control arrangement with the features of claim 1.

Erfindungsgemäß sind die den mechanisch betätigten Wegeventilen zugeordneten LUDV-Druckwaagen mit einer in Schließrichtung wirksamen Feder beaufschlagt. Des weiteren ist die allen Verbrauchern gemeinsame Lastdruckmeldeleitung über einen Stromregler mit dem Tank verbunden, so dass stets eine geringe Steuerölmenge zum Tank hin abströmt. In dieser Lastdruckleitung ist ein Sicherheitsventil angeordnet, über das die Verbindung der Lastdruckmeldeleitung zum Stromregler absperrbar ist. Ein Bereich stromaufwärts des Schaltventils ist über eine Düse mit einem Abschnitt des Druckmittelströmungspfades zwischen der Pumpe und der LUDV-Druckwaage verbunden.In accordance with the invention, the LUDV pressure compensators associated with the mechanically operated directional control valves are acted on by a spring acting in the closing direction. Furthermore, the load pressure signaling line common to all consumers is connected to the tank via a current regulator, so that a small amount of control oil always flows to the tank. In this load pressure line, a safety valve is arranged, via which the connection of the load pressure signaling line to the current regulator can be shut off. An area upstream of the switching valve is connected via a nozzle to a portion of the pressure medium flow path between the pump and the LUDV pressure compensator.

Beim Umschalten des Sicherheitsventils in eine Sperrstellung wird die Verbindung der Lastdruckmeldeleitung zum Tank abgesperrt und der über die Düse abgegriffene Druck in einem an die Lastdruckmeldeleitung angeschlossenen rückwärtigen Steuerraum wirksam, so dass die LUDV-Druckwaage in ihre Schließstellung gebracht wird. Die Lastdruckmeldeleitung ist stromabwärts des Stromreglers an eine Pumpenregelung angeschlossen. Nach dem Absperren der Lastdruckmeldeleitung fällt dann auch der Steuerdruck an der Pumpenregelung zum Tank hin ab, so dass die Pumpe nur noch den Standby-Druck erzeugen kann.When switching the safety valve in a blocking position, the connection of the load pressure signaling line is shut off to the tank and the tapped through the nozzle pressure in a connected to the load pressure signaling line rear control chamber effective, so that the LUDV pressure compensator is brought into its closed position. The load pressure sensing line is connected downstream of the flow regulator to a pump control. After shutting off the load pressure signaling line, the control pressure at the pump control then drops towards the tank so that the pump can only generate the standby pressure.

Die erfindungsgemäße Lösung zeichnet sich durch einen sehr einfachen Aufbau und ein gutes Ansprechverhalten aus.The solution according to the invention is characterized by a very simple structure and a good response.

Bei zwei bevorzugten Ausführungsbeispielen der Erfindung ist die stromaufwärts des Sicherheitsventils angeordnete Düse entweder in die Druckwaage integriert, wobei über diese Düse der am Druckwaageneingang anliegende Druck in den rückwärtigen Steuerraum gemeldet wird, so dass der Druckwaagenkolben druckausgeglichen ist und durch die Kraft der zusätzlichen Feder geschlossen wird.In two preferred embodiments of the invention, the upstream of the safety valve disposed nozzle is either integrated into the pressure balance, which is reported via this nozzle the voltage applied to the pressure compensator input pressure in the rear control chamber, so that the pressure compensator piston is pressure balanced and is closed by the force of the additional spring ,

Bei der alternativen Lösung ist diese Düse in einer Zweigleitung vorgesehen, die sich von einem Bereich stromaufwärts des Wegeventils hin zu einem Bereich stromaufwärts des Sicherheitsventils erstreckt. In diesem Fall wird der stromaufwärts des Wegeventils anliegende Pumpendruck in den rückwärtigen Druckraum gemeldet.In the alternative solution, this nozzle is provided in a branch line which extends from an area upstream of the directional control valve to an area upstream of the safety valve. In this case, the pump pressure applied upstream of the directional control valve is reported to the rear pressure chamber.

Bei einem Ausführungsbeispiel der Erfindung ist die die Verbraucher versorgende Pumpe als Konstantpumpe ausgeführt, der ein Differenzdruckregler zugeordnet ist, der in Abhängigkeit vom Lastdruck in der Lastdruckmeldeleitung angesteuert wird.In one embodiment of the invention, the consumer supplying pump is designed as a fixed displacement pump, which is associated with a differential pressure regulator, which is controlled in response to the load pressure in the load pressure signaling line.

Bei einem besonders bevorzugten Ausführungsbeispiel der Erfindung werden die hydraulisch betätigten Verbraucher jeweils mittels eines Vorsteuergerätes angesteuert, dem eine eigene Steuerölversorgung zugeordnet ist.In a particularly preferred embodiment of the invention, the hydraulically operated consumers are each driven by means of a pilot control device, which is assigned its own control oil supply.

In dieser Steuerölversorgung ist ein Abschaltventil vorgesehen, über das zum Absperren der hydraulisch betätigten Verbraucher die Steuerölversorgung des Vorsteuergerätes unterbrochen wird, so dass deren Ventilschieber in die federvorgespannte Grundposition zurückgefahren werden. Erfindungsgemäß erfolgt dann über die Umschaltung dieses Abschaltventils auch eine Betätigung des Sicherheitsventils.In this control oil supply a shut-off valve is provided, via which the control oil supply of the pilot control device is interrupted to shut off the hydraulically actuated consumers, so that their Valve spool are moved back to the spring-biased home position. According to the invention then takes place via the switching of this shut-off valve and an actuation of the safety valve.

Sonstige vorteilhafte Weiterbildungen der Erfindung sind Gegenstand weiterer Unteransprüche.Other advantageous developments of the invention are the subject of further subclaims.

Im folgenden werden bevorzugte Ausführungsbeispiele der Erfindung anhand schematischer Zeichnungen näher erläutert. Es zeigen:

  • Figur 1 ein Schaltschema eines Steuerblocks für ein mobiles Arbeitsgerät mit zumindest einem mechanisch ansteuerbaren Verbraucher und
  • Figur 2 eine vergrößerte Darstellung einer Ventilscheibe des Steuerblocks aus Figur 1.
In the following preferred embodiments of the invention will be explained in more detail with reference to schematic drawings. Show it:
  • Figure 1 is a circuit diagram of a control block for a mobile implement with at least one mechanically controllable loads and
  • FIG. 2 shows an enlarged illustration of a valve disk of the control block from FIG. 1.

In Figur 1 ist eine Steueranordnung eines mobilen Arbeitsgerätes dargestellt, wobei über einen Steuerblock 1 mit Ventilscheiben 2, 4 Verbraucher des mobilen Arbeitsgerätes, beispielsweise eines Mobilbaggers ansteuerbar sind. Bei dem dargestellten Ausführungsbeispiel wird die Funktion eines Verbrauchers, beispielsweise eines Hydromotors 6 eines Fahrantriebs mechanisch über einen Stellhebel und die Funktion eines weiteren Verbrauchers, beispielsweise eines den Ausleger betätigenden Hydrozylinders 8 hydraulisch betätigt.1 shows a control arrangement of a mobile working device is shown, wherein via a control block 1 with valve discs 2, 4 consumers of the mobile implement, such as a wheeled excavator can be controlled. In the illustrated embodiment, the function of a consumer, such as a hydraulic motor 6 of a traction drive mechanically via a lever and the function of another consumer, for example, a hydraulic cylinder actuating the boom 8 is actuated hydraulically.

Die Druckmittelversorgung des Steuerblocks 1 erfolgt beim dargestellten Ausführungsbeispiel über eine Konstantpumpe 10, deren Förderstrom über einen Differenzdruckregler 12 in Abhängigkeit vom höchsten Lastdruck der betätigten Verbraucher gesteuert wird. Dieser Lastdruck wird über eine LS-Leitung 14 zu einer in Schließrichtung wirksamen Steuerfläche des Differenzdruckreglers 12 geführt, während dessen in Öffnungsrichtung wirksame Steuerfläche vom Pumpendruck beaufschlagt ist.The pressure medium supply of the control block 1 takes place in the illustrated embodiment via a constant displacement pump 10 whose flow is controlled by a differential pressure regulator 12 in response to the highest load pressure of the actuated consumers. This load pressure is via an LS line 14 to a in Closing direction effective control surface of the differential pressure regulator 12 out, while acting in the opening direction control surface is acted upon by the pump pressure.

Jede der Ventilscheiben 2, 4 hat ein stetig verstellbares Wegeventil 16, das jeweils Richtungsteile 20, 22 und ein Geschwindigkeitsteil 18 aufweist. Die Richtungsteile 20, 22 steuern die Druckmittelströmung zum bzw. vom Verbraucher und der Geschwindigkeitsteil 18 bestimmt den Druckmittelvolumenstrom, der durch Aufsteuern einer Zumessblende einstellbar ist. Stromabwärts dieser Zumessblende ist jeweils eine LUDV-Druckwaage 24 vorgesehen, die - wie eingangs beschrieben - den Druckabfall über der Zumessblende lastunabhängig konstant hält. Jede Druckwaage 24 ist in der Regelstellung in Öffnungsrichtung von dem individuellen Lastdruck des zugeordneten Verbrauchers und in Schließrichtung von dem höchsten Lastdruck beaufschlagt, der über die LS-Leitung 14 abgegriffen wird.Each of the valve disks 2, 4 has a continuously adjustable directional control valve 16, which in each case has directional parts 20, 22 and a speed part 18. The direction parts 20, 22 control the pressure medium flow to and from the consumer and the speed part 18 determines the pressure medium volume flow, which is adjustable by controlling a metering orifice. Downstream of this metering orifice, in each case a LUDV pressure compensator 24 is provided which, as described at the outset, keeps the pressure drop across the metering orifice constant regardless of the load. Each pressure compensator 24 is acted upon in the control position in the opening direction of the individual load pressure of the associated load and in the closing direction of the highest load pressure, which is tapped via the LS line 14.

Bei der in Figur 1 dargestellten Schaltung ist das Wegeventil 16 der Ventilscheibe 2 mechanisch, beispielsweise über einen Stellhebel betätigt, während das Wegeventil 16 der ventilscheibe 4 über ein Vorsteuergerät 26 betätigt wird, das im Prinzip aus Druckreduzierventilen besteht, an deren Eingang ein von einer Steuerölversorgung 28 bereit gestellter Druck anliegt und an deren Ausgang in Abhängigkeit von der Verstellung des Vorsteuergerätes 26 ein Steuerdruck erzeugt wird, der zur Betätigung des Wegeventils 16 an Steuerräume 31, 33 des Wegeventils 16 der Ventilscheibe 4 angelegt wird. Im Bereich zwischen der Steuerölversorgung 28 und dem Vorsteuergerät 26 ist ein elektrisch betätigtes Abschaltventil 30 vorgesehen, über das die Steuerölversorgung 28 mit einem Tank T verbindbar ist. In der Betriebsposition ist dieses Abschaltventil 30 umgeschaltet, so dass das Vorsteuergerät 26 mit Steueröl versorgt wird.In the circuit shown in Figure 1, the directional control valve 16 of the valve disc 2 is mechanically operated, for example via a lever, while the directional valve 16 of the valve disc 4 is actuated via a pilot valve 26, which consists in principle of pressure reducing valves, at the input of a control oil supply 28 is applied pressure applied and at whose output in response to the adjustment of the pilot control device 26, a control pressure is generated, which is applied to actuate the directional control valve 16 to control chambers 31, 33 of the directional control valve 16 of the valve disk 4. In the area between the control oil supply 28 and the pilot control device 26, an electrically operated shut-off valve 30 is provided, via which the control oil supply 28 with a tank T is connectable. In the operating position, this shut-off valve 30 is switched so that the pilot control device 26 is supplied with control oil.

Der Bereich stromabwärts des Abschaltventils 30 ist über eine Steuerleitung 32 mit einem Steuerraum eines Sicherheitsventils 34 verbunden, das als 2/2 Wegeventil ausgeführt ist. Das Sicherheitsventil 34 ist durch eine Feder in eine Schaltstellung vorgespannt, in der die LS-Leitung 14 abgesperrt ist. Durch Umschalten des Abschaltventils 30 in seine Durchgangsstellung wirkt der von der Steuerölversorgung 28 zur Verfügung gestellte Steuerölversorgungsdruck in dem Steuerraum des Sicherheitsventils 34, so dass dieses gegen die Kraft der Feder in eine Durchgangsstellung gebracht wird.The area downstream of the shut-off valve 30 is connected via a control line 32 to a control chamber of a safety valve 34, which is designed as a 2/2 way valve. The safety valve 34 is biased by a spring into a switching position in which the LS line 14 is shut off. By switching the shut-off valve 30 to its passage position, the control oil supply pressure provided by the control oil supply 28 acts in the control space of the safety valve 34, so that it is brought into a passage position against the force of the spring.

Im Bereich zwischen dem Sicherheitsventil 34 und dem Differenzdruckregler 12 ist ein Stromregler 36 angeordnet, über den die LS-Leitung 14 mit dem Tank T verbunden ist. D.h. durch die LS-Leitung fließt in der Öffnungsstellung des Sicherheitsventils 34 ein konstanter Steuerölvolumenstrom zum Tank T hin ab, dessen Größe von der Einstellung des Stromregelventils 36 abhängt. Der Druck in der LS-Leitung 14 ist über ein Druckbegrenzungsventil 37 begrenzt, das zwischen dem Stromregelventil 36 und dem Sicherheitsventil 34 angeordnet ist.In the area between the safety valve 34 and the differential pressure regulator 12, a current regulator 36 is arranged, via which the LS line 14 is connected to the tank T. That through the LS line flows in the open position of the safety valve 34 from a constant control oil volume flow to the tank T from down, the size of which depends on the setting of the flow control valve 36. The pressure in the LS line 14 is limited by a pressure limiting valve 37, which is arranged between the flow control valve 36 and the safety valve 34.

Ein Aufbau der Ventilscheibe 2 wird im folgenden anhand der vergrößerten Darstellung in Figur 2 erläutert.A structure of the valve disc 2 will be explained below with reference to the enlarged view in FIG.

Jede der vorbeschriebenen Ventilscheiben 2,4 hat einen Druckanschluß P, an dem der Pumpendruck anliegt, einen mit dem Tank verbundenen Tankanschluss S, einen mit der LS-Leitung 14 verbundenen LS-Anschluss LS sowie zwei mit dem Verbraucher, im vorliegenden Fall dem Hydromotor 6 verbundene Arbeitsanschlüsse A, B.Each of the above-described valve discs 2,4 has a pressure port P to which the pump pressure is applied, a tank port S connected to the tank, an LS port LS connected to the LS port 14, and two with the consumer, in the present case the hydraulic motor 6 connected working ports A, B.

Ein Ventilschieber 38 des Wegeventils 16 der Ventilscheibe 2 ist über eine Zentrierfederanordnung 40 in seine dargestellte Grundposition vorgespannt. Die Betätigung des Ventilschiebers 38 erfolgt über einen seitlich aus der Ventilscheibe 2 hervorstehenden Betätigungsabschnitt 42, an den ein Stellhebel oder dergleichen angelenkt sein kann.A valve spool 38 of the directional valve 16 of the valve disc 2 is biased via a centering spring assembly 40 in its illustrated basic position. The actuation of the valve slide 38 via a laterally protruding from the valve disc 2 actuating portion 42 to which a lever or the like may be hinged.

Der Ventilschieber 38 ist in einer Ventilbohrung 44 geführt, die in Radialrichtung zu einer Druckkammer 46, einer Zulaufkammer 48, zwei etwa symmetrisch zur Druckkammer 20 angeordneten Ablaufkammern 50, 52, zwei beidseitig davon angeordneten Arbeitskammern 54, 56 sowie zu zwei dazu benachbarten Tankkammern 58, 60 erweitert ist.The valve spool 38 is guided in a valve bore 44, which in the radial direction to a pressure chamber 46, an inlet chamber 48, two approximately symmetrically to the pressure chamber 20 disposed drain chambers 50, 52, two on both sides thereof arranged working chambers 54, 56 and two adjacent thereto tank chambers 58, 60 is extended.

Der Ventilschieber 16 hat einen mittigen Messblendenbund 62, der gemeinsam mit dem verbleibenden Ringsteg zwischen der Druckkammer 46 und der Zulaufkammer 48 eine den Geschwindigkeitsteil 18 ausbildende Messblende bestimmt. Beidseitig dieses Messblendenbundes 62 sind zwei Steuerbünde 64, 66 und zwei Tankbünde 68, 70 des Richtungsteils 20, 22 am Ventilschieber 38 angeordnet.The valve spool 16 has a central measuring diaphragm collar 62 which, together with the remaining annular web between the pressure chamber 46 and the inlet chamber 48, determines a measuring diaphragm forming the speed part 18. On both sides of this measuring diaphragm collar 62, two control collars 64, 66 and two tank collars 68, 70 of the directional part 20, 22 are arranged on the valve slide 38.

Die Druckkammer 46 ist an den Druckanschluss P und die beiden Tankkammern 58, 60 sind an den Tankanschluss S angeschlossen. Die Zulaufkammer 48 ist über einen Zulaufkanal 72 mit dem Eingang der Druckwaage 24 verbunden. Deren Ausgang ist über zwei Ablaufkanäle 74, 76 mit der Ablaufkammer 50, 52 und die beiden Arbeitskammern 54, 56 über Arbeitskanäle 78, 80 mit dem Arbeitsanschluss A bzw. B verbunden.The pressure chamber 46 is connected to the pressure port P and the two tank chambers 58, 60 are connected to the tank port S. The inlet chamber 48 is connected via an inlet channel 72 to the inlet of the pressure compensator 24. Their output is connected via two drainage channels 74, 76 with the discharge chamber 50, 52 and the two working chambers 54, 56 via working channels 78, 80 to the working port A and B respectively.

In Figur 2 ist die Druckwaage 24 in ihrer Schließposition dargestellt. Sie hat einen Druckwaagenkolben 84, der axial verschiebbar in einer Druckwaagenbohrung 82 geführt ist. Der Druckwaagenkolben 84 ist als Stufenkolben ausgeführt, wobei die kleinere Kolbenfläche in der Schließstellung an einer Schulter 86 des Zulaufkanals 72 abgestützt ist. Die dieser Schulter 86 zugewandte Stirnfläche des Druckwaagenkolbens 84 ist in der Regelposition mit dem Druck in den Ablaufkanälen 74, 76, d.h. dem Lastdruck am zugeordneten Verbraucher beaufschlagt. Der größere Durchmesser (oben in Figur 2) des Druckwaagenkolbens 84 taucht in einen rückwärtigen Steuerraum 88 ein, der über einen LS-Kanal 90 mit dem LS-Anschluss verbunden ist.In Figure 2, the pressure compensator 24 is shown in its closed position. It has a pressure compensator piston 84, which is guided axially displaceably in a pressure balance bore 82. The pressure balance piston 84 is designed as a stepped piston, wherein the smaller piston surface is supported in the closed position on a shoulder 86 of the inlet channel 72. The shoulder surface 86 of the pressure compensator piston 84 facing this shoulder 86 is in the control position with the pressure in the drainage channels 74, 76, i. applied to the load pressure on the associated consumer. The larger diameter (top of Figure 2) of the pressure compensator piston 84 immersed in a rear control chamber 88 which is connected via an LS channel 90 to the LS port.

Wie insbesondere der Detaildarstellung in Figur 2 entnehmbar ist, hat der Druckwaagenkolben 84 eine in der zurückgestuften Stirnfläche mündende Axialbohrung 92, die über eine Lastmeldedüse 94 in einer den Druckwaagenkolben 84 in Querrichtung durchsetzenden Querbohrung 96 mündet. Letztere ist in der Schließ- und Regelposition des Druckwaagenkolbens 84 durch die Umfangswandungen der Druckwaagenbohrung 86 abgesperrt und wird erst geöffnet, wenn die Druckwaage 24 vollständig geöffnet ist. Das Steueröl fließt dann vom Eingang der Druckwaage über die Lastmeldedüse in den Steuerraum 88 und damit in die LS-Leitung 14, so dass im wesentlichen der Lastdruck des Verbrauchers als höchster Lastdruck in der LS-Leitung 14 anliegt.2, the pressure compensator piston 84 has an axial bore 92 which opens out in the stepped-back end face and opens out via a load-indicating nozzle 94 in a transverse bore 96 passing through the pressure compensator piston 84 in the transverse direction. The latter is shut off in the closing and control position of the pressure compensator piston 84 by the peripheral walls of the pressure compensator bore 86 and is only opened when the pressure compensator 24 is fully open. The control oil then flows from the input of the pressure compensator via the load indicator in the control chamber 88 and thus in the LS line 14, so that substantially the load pressure of the consumer as the highest load pressure in the LS line 14 is applied.

Bei dem in Figur 2 dargestellten Ausführungsbeispiel ist in Verlängerung der Axialbohrung 92 jenseits der Querbohrung 96 eine weitere Düse 98 vorgesehen, über die die Axialbohrung 92 stets mit dem Steuerraum 88 verbunden ist.In the embodiment shown in Figure 2, an additional nozzle 98 is provided in extension of the axial bore 92 beyond the transverse bore 96 through which the axial bore 92 is always connected to the control chamber 88.

Der Druckwaagenkolben 84 ist des weiteren über eine Feder 100 gegen die Schulter 62 in seine Schließposition vorgespannt, in der die Außenumfangskante 102 der Abstufung des Druckwaagenkolbens 84 die Verbindung zwischen dem Zulaufkanal 72 und den Ablaufkanälen 74, 76 zugesteuert hat. Die Feder 100 ist an einer in die Druckwaagenbohrung 82 eingeschraubten Verschlussschraube 104 abgestützt.The pressure compensator piston 84 is further biased by a spring 100 against the shoulder 62 in its closed position in which the outer peripheral edge 102 of the gradation of the pressure compensator piston 84, the connection between the inlet channel 72 and the drainage channels 74, 76 has been controlled. The spring 100 is supported on a screwed into the pressure balance bore 82 screw plug 104.

Die der hydraulischen Funktion zugeordnete Ventilscheibe 4 hat im Prinzip den gleichen Aufbau, wobei allerdings der Druckwaagenkolben 106 nicht mit einer Düse 98 ausgebildet ist und somit keine ständige Verbindung zwischen der Axialbohrung 108 und dem Steuerraum 110 vorliegt. Des weiteren ist der Druckwaagenkolben 106 nicht durch eine Feder in seine Schließposition vorgespannt.The valve disk 4 assigned to the hydraulic function has, in principle, the same structure, although the pressure compensator piston 106 is not formed with a nozzle 98 and thus there is no permanent connection between the axial bore 108 and the control chamber 110. Furthermore, the pressure compensator piston 106 is not biased by a spring into its closed position.

Bei der Ansteuerung des Hydromotors 6 wird der Ventilschieber 16 von Hand über den Stellhebel in eine Öffnungsstellung verschoben, so dass die Messblende des Geschwindigkeitsteils 18 aufgesteuert wird. Zu Beginn dieser Ansteuerung liegt am Eingang der Druckwaage 24 der Pumpendruck an, der gegen den in Schließrichtung wirksamen Lastdruck wirkt. Der Pumpendruck steigt an bis der Druckwaagenkolben 84 die Verbindung zu den Ablaufkanälen 74, 76 aufsteuert. Das Druckmittel kann dann über die Richtungsteile 20, 22 zum Hydromotor 6 und von diesem zurück zum Tank strömen. Falls nur der Hydromotor 6 betätigt wird, wird die Druckwaage 24 durch den Lastdruck am Hydromotor 6 in die vollständig geöffnete Position gebracht, so dass dieser Lastdruck in die LS-Leitung gemeldet wird. Bei Zuschalten des Auslegers (Hydrozylinder 8) wird der Ventilschieber 16 der Ventilscheibe 4 über das Vorsteuergerät 26 angesteuert. Falls der Lastdruck am Hydrozylinder 8 größer als am Hydromotor 6 ist, wird dieser höhere Lastdruck in der vorbeschriebenen Weise in den Steuerraum 110 der Ventilscheibe 4 gemeldet, so dass dieser höhere Steuerdruck auf die Rückseite der Druckwaage 24 der Ventilscheibe 2 wirkt. Der Druckwaagenkolben 84 wird dann in eine Regelposition verschoben, in der der Druckabfall über der Messblende der Ventilscheibe 2 lastunabhängig konstant gehalten wird.When the hydraulic motor 6 is actuated, the valve slide 16 is moved by hand via the adjusting lever into an open position, so that the measuring diaphragm of the speed part 18 is opened. At the beginning of this control is at the entrance of the pressure compensator 24, the pump pressure, which acts against the effective in the closing direction of the load pressure. The pump pressure increases until the pressure compensator piston 84 opens the connection to the drainage channels 74, 76. The pressure medium can then flow via the direction parts 20, 22 to the hydraulic motor 6 and from this back to the tank. If only the hydraulic motor 6 is actuated, the pressure compensator 24 is brought by the load pressure on the hydraulic motor 6 in the fully open position, so that this load pressure is reported in the LS line. When switching on the boom (hydraulic cylinder 8), the valve spool 16 of the valve disc 4 via the pilot control device 26th driven. If the load pressure at the hydraulic cylinder 8 is greater than at the hydraulic motor 6, this higher load pressure is reported in the above-described manner in the control chamber 110 of the valve disk 4, so that this higher control pressure acts on the back of the pressure compensator 24 of the valve disk 2. The pressure compensator piston 84 is then moved to a control position in which the pressure drop across the metering orifice of the valve disc 2 is kept constant independent of the load.

Will nun der Fahrer seinen Fahrerplatz verlassen, so muss er zunächst das Abschaltventil 30 betätigen. Dies erfolgt beispielsweise über einen Schalter oder dergleichen. Dadurch wird die Steuerölversorgung des Vorsteuergeräts 26 abgesperrt, so dass das Wegeventil 16 der Ventilscheibe 4 in seine Grundposition zurückgefahren wird und entsprechend keine Ansteuerung des Hydrozylinders 8 mehr erfolgt. Durch das Umschalten des Abschaltventils 30 liegt in der Steuerleitung 32 ebenfalls der Tankdruck an, so dass das geöffnete Sicherheitsventil 34 in seine Schließstellung gebracht wird. Dadurch wird die Verbindung zwischen dem Differenzdruckregler 12 und den einzelnen Ventilfunktionen unterbrochen. Der Federraum des Differenzdruckreglers 12 wird über dem Stromregler 36 zum Tank T hin entlastet, so dass der Differenzdruckregler 12 nur noch den Standby-Druck erzeugen kann.Now, if the driver wants to leave his driver's seat, he must first actuate the shut-off valve 30. This is done for example via a switch or the like. As a result, the control oil supply of the pilot control device 26 is shut off, so that the directional control valve 16 of the valve disk 4 is moved back to its basic position and correspondingly no activation of the hydraulic cylinder 8 takes place. By switching the shut-off valve 30 is in the control line 32 also the tank pressure, so that the opened safety valve 34 is brought into its closed position. As a result, the connection between the differential pressure regulator 12 and the individual valve functions is interrupted. The spring chamber of the differential pressure regulator 12 is relieved via the flow regulator 36 to the tank T out, so that the differential pressure regulator 12 can only generate the standby pressure.

Da durch das Sicherheitsventil 34 der Steuerölvolumenstrom von der Druckwaage 24 der Ventilscheibe 2 über die Axialbohrung 82, die Querbohrung 96, die Düse 98 und über die LS-Leitung 14 unterbrochen ist und somit kein Druckabfall über der Druckwaage 24 aufgrund dieser Steuerölströmung mehr entsteht, wird der Druckwaagenkolben 84 druckausgeglichen und durch die Kraft der Feder 100 in seine Schließposition zurückgeschoben und somit die Verbindung zum Hydromotor 6 abgesperrt.Since the control oil volume flow is interrupted by the safety valve 34 of the pressure compensator 24 of the valve disc 2 via the axial bore 82, the transverse bore 96, the nozzle 98 and the LS line 14 and thus no pressure drop across the pressure compensator 24 more arises due to this control oil flow is the pressure compensator piston 84 pressure balanced and by the force of the spring 100 in its closed position pushed back and thus shut off the connection to the hydraulic motor 6.

Bei dem vorbeschriebenen Ausführungsbeispiel werden somit durch Betätigung des Abschaltventils 30 auch sämtliche mechanisch betätigten Funktionen verriegelt. Selbstverständlich ist es auch möglich, das Abschaltventil 30 mechanisch oder elektrisch zu betätigen.In the above-described embodiment, all mechanically operated functions are thus locked by actuation of the shut-off valve 30. Of course, it is also possible to operate the shut-off valve 30 mechanically or electrically.

Die Dimensionierung der Feder 100 und des Querschnitts der Düse 98 ist so gewählt, dass einerseits eine sichere Verriegelung der mechanisch betätigten Ventilscheiben 2 ermöglicht ist, andererseits aber die vorbeschriebene LUDV-Funktion nur wenig beeinflusst wird.The dimensioning of the spring 100 and the cross section of the nozzle 98 is selected so that on the one hand a secure locking of the mechanically actuated valve discs 2 is possible, but on the other hand, the above-described LUDV function is only slightly affected.

In Figur 1 ist eine Variante der Erfindung dargestellt, gemäß der die Düse 98' nicht im Druckwaagenkolben 84 sondern in einer Zweigleitung 112 angeordnet ist, über die der Druckmittelströmungspfad stromabwärts der Pumpe 10 und stromaufwärts der Messblende mit einem Abschnitt der LS-Leitung 14 stromaufwärts des Sicherheitsventils 34 verbunden ist. Im normalen Betriebszustand, d.h. bei geöffnetem Sicherheitsventil 34 fließt über diese Düse 98' ständig ein Steuerölvolumenstrom über den Stromregler 36 zum Tank T hin ab. Beim Umschalten des Sicherheitsventils 34 wirkt über die Düse 98' der Druck am Ausgang der Pumpe in der Lastmeldeleitung 14 und damit im Steuerraum 88, so dass die Druckwaage 24 ebenfalls in ihre Schließstellung zurückgefahren wird.1 shows a variant of the invention, according to which the nozzle 98 'is not arranged in the pressure compensator piston 84 but in a branch line 112, via which the pressure medium flow path downstream of the pump 10 and upstream of the metering orifice with a portion of the LS line 14 upstream of Safety valve 34 is connected. In the normal operating condition, i. when the safety valve 34 is open, a control oil volume flow constantly flows via the flow regulator 36 to the tank T via this nozzle 98 '. When switching the safety valve 34 acts on the nozzle 98 ', the pressure at the output of the pump in the load-sensing line 14 and thus in the control chamber 88, so that the pressure compensator 24 is also returned to its closed position.

Offenbart ist eine hydraulische Steueranordnung zur Ansteuerung eines Verbrauchers, mit zumindest einem mechanisch betätigten, stetig verstellbaren Wegeventil, dem eine LUDV-Druckwaage nachgeschaltet ist. Zum Verriegeln des Verbrauchers ist die Steueranordnung mit einer den Druckwaagenkolben in eine Schließposition beaufschlagenden Feder ausgeführt. Des weiteren ist eine den höchsten Lastdruck sämtlicher Verbraucher führende LS-Leitung über einen Stromregler an einen Tank angeschlossen, wobei über dem Stromregler auch eine Pumpenreglung im Sinne einer Verkleinerung des Fördervolumens entlastbar ist. Erfindungsgemäß wird die LUDV-Druckwaage über eine Düse druckausgeglichen, über die eine Verbindung zwischen der LS-Leitung und einem Abschnitt des Druckmittelströmungspfades stromabwärts der Pumpe und stromaufwärts der Ausgangs der Druckwaage hergestellt ist. Vorzugsweise wird diese Düse in den Druckwaagenkolben integriert.Disclosed is a hydraulic control arrangement for controlling a consumer, with at least one mechanically actuated, continuously adjustable directional control valve, which is followed by a LUDV pressure compensator. To the Locking the consumer, the control arrangement is designed with a spring acting on the pressure compensator piston in a closed position. Furthermore, a highest load pressure of all consumers leading LS line is connected via a current regulator to a tank, with the current regulator and a pump control in the sense of reducing the delivery volume is relieved. According to the invention, the LUDV pressure compensator is pressure compensated via a nozzle via which a connection between the LS line and a portion of the Druckmittelströmungspfades downstream of the pump and upstream of the output of the pressure compensator is made. Preferably, this nozzle is integrated into the pressure compensator piston.

Bezugszeichenliste:LIST OF REFERENCE NUMBERS

11
Steuerblockcontrol block
22
Ventilscheibevalve disc
44
Ventilscheibevalve disc
66
Hydromotorhydraulic motor
88th
Hydrozylinderhydraulic cylinders
1010
Pumpepump
1212
DifferenzdruckreglerDifferential pressure regulator
1414
LS-LeitungLS line
1616
Wegeventilway valve
1818
Geschwindigkeitsteilspeed part
2020
Richtungsteildirection part
2222
Richtungsteildirection part
2424
LUDV-DruckwaageLUDV pressure
2626
Vorsteuergerätpilot control unit
2828
SteuerölversorgungControl oil supply
3030
Abschaltventilshut-off valve
3131
Steuerraumcontrol room
3232
Steuerleitungcontrol line
3333
Steuerraumcontrol room
3434
Sicherheitsventilsafety valve
3636
StromregelventilFlow control valve
3737
DruckbegrenzungsventilPressure relief valve
3838
Ventilschiebervalve slide
4040
Zentrierfederanordnungcentering
4242
Betätigungsabschnittactuating section
4444
Ventilbohrungvalve bore
4646
Druckkammerpressure chamber
4848
Zulaufkammerinlet chamber
5050
Ablaufkammerdrain chamber
5252
Ablaufkammerdrain chamber
5454
Arbeitskammerworking chamber
5656
Arbeitskammerworking chamber
5858
Tankkammertank chamber
6060
Tankkammertank chamber
6262
MessblendenbundMeasuring orifice collar
6464
Steuerbundcontrol collar
6666
Steuerbundcontrol collar
6868
Tankbundtank Bund
7070
Tankbundtank Bund
7272
Zulaufkanalinlet channel
7474
Ablaufkanaldrain channel
7676
Ablaufkanaldrain channel
7878
Arbeitskanalworking channel
8080
Arbeitskanalworking channel
8282
DruckwaagenbohrungPressure compensator bore
8484
DruckwaagenkolbenPressure regulator piston
8686
Schultershoulder
8888
rückwärtiger Steuerraumrearward control room
9090
LS-KanalLS-channel
9292
Axialbohrungaxial bore
9494
LastmeldedüseLastmeldedüse
9696
Querbohrungcross hole
9898
Düsejet
100100
Federfeather
102102
AußenumfangskanteOuter peripheral edge
104104
VerschlussschraubeScrew
106106
Druckwaagenkolben (4)Pressure balance piston (4)
108108
Axialbohrung (4)Axial bore (4)
110110
Steuerraum (4)Control room (4)
112112
Zweigleitungbranch line

Claims (7)

  1. A hydraulic control arrangement for the control of a consumer (6, 8), comprising at least one mechanically operated continuously adjustable distribution valve (16) with a subsequent pressure compensator (24) down the line to which the load pressure of the corresponding consumer (6) can be applied in the opening direction and the highest load pressure of all controlled consumers prevailing in a rear control chamber (88) can be applied in the closing direction, wherein said load pressure can be carried via an LS line (14) to a pump regulator (12) of a pump (30), and comprising a safety valve (34) upon operation of which the pressure compensator can be brought into a closing position for closing the connection to the consumer (6), characterized in that a pressure compensator piston (84) can be held in its closed position by a spring (100), the LS line (14) is connected to the reservoir by means of a flow control valve (36), the safety valve (34) is arranged in the LS line (14) between the flow regulator (12) and the pressure compensator (24), and a pressure effective upon change-over of the switch valve in the control chamber (88) is tapped off by means of a nozzle (98) from a pressure medium flow portion downstream of the pump (10) and upstream of an outlet (74, 76) of the pressure compensator (24).
  2. A control arrangement according to claim 1, wherein the nozzle (98) is integrated in the pressure compensator piston (84) and connects the rear control chamber (88) to the inlet of the pressure compensator.
  3. A control arrangement according to claim 1, wherein the nozzle (98') is arranged in a branch line (112) extending between the outlet of the pump (10) and a portion of the LS line (14) upstream of the safety valve (34).
  4. A control arrangement according to any one of the preceding claims, wherein the pump regulator is a differential pressure regulator (12) and the pump is a fixed displacement pump.
  5. A control arrangement according to any one of the preceding claims, wherein the function of a further consumer (8) is hydraulically controlled by means of a pilot device (26) connected to a control oil supply (28) which can be disconnected from the pilot device (26) by means of an interrupting valve (30), wherein the safety valve (34) can be brought into its locked position by means of the interrupting valve (30).
  6. A control arrangement according to claim 2, wherein the pressure compensator piston (84) has an axial bore opening (92) via a load detecting nozzle (94) into a transverse bore (96) which is controlled to be opened when the pressure compensator (24) is completely opened, wherein the nozzle (98) connects the transverse bore (96) to the rear control chamber (88).
  7. A control arrangement according to any one of the preceding claims, wherein the nozzle (98, 98') has a smaller cross-section than a load detecting nozzle (96) of the pressure compensator piston (84).
EP04739453A 2003-06-04 2004-05-28 Hydraulic control arrangement Expired - Lifetime EP1629156B1 (en)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE10325295A DE10325295A1 (en) 2003-06-04 2003-06-04 Hydraulic control arrangement
PCT/EP2004/005835 WO2004109019A1 (en) 2003-06-04 2004-05-28 Hydraulic control arrangement

Publications (2)

Publication Number Publication Date
EP1629156A1 EP1629156A1 (en) 2006-03-01
EP1629156B1 true EP1629156B1 (en) 2006-10-25

Family

ID=33482509

Family Applications (1)

Application Number Title Priority Date Filing Date
EP04739453A Expired - Lifetime EP1629156B1 (en) 2003-06-04 2004-05-28 Hydraulic control arrangement

Country Status (6)

Country Link
US (1) US7395662B2 (en)
EP (1) EP1629156B1 (en)
JP (1) JP5081447B2 (en)
AT (1) ATE343687T1 (en)
DE (2) DE10325295A1 (en)
WO (1) WO2004109019A1 (en)

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102013224655A1 (en) * 2013-12-02 2015-06-03 Robert Bosch Gmbh Control arrangement and control valve for such a control arrangement

Families Citing this family (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE10325296A1 (en) * 2003-06-04 2004-12-23 Bosch Rexroth Ag Hydraulic control arrangement
DE102007028864A1 (en) * 2007-03-27 2008-10-02 Robert Bosch Gmbh Hydraulic control arrangement
WO2011096001A1 (en) * 2010-02-02 2011-08-11 Bucher Hydraulics S.P.A. Hydraulic section for load sensing applications and multiple hydraulic distributor
DE102010009704A1 (en) * 2010-03-01 2011-09-01 Robert Bosch Gmbh Hydraulic drive and method for controlling such a drive
DE102011119945A1 (en) * 2011-12-01 2013-06-06 Liebherr-Hydraulikbagger Gmbh hydraulic system
EP2918853B1 (en) 2014-03-11 2016-03-09 Bucher Hydraulics S.p.A. Hydraulic section for load sensing applications and multiple hydraulic distributor
EP2980416B1 (en) 2014-07-31 2019-06-05 Bucher Hydraulics S.p.A. Hydraulic section for load sensing applications and multiple hydraulic distributor
KR102388136B1 (en) * 2016-05-18 2022-04-19 현대두산인프라코어(주) Safety system for construction machinery

Family Cites Families (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS5831486B2 (en) 1979-07-18 1983-07-06 株式会社ナブコ compound valve
DE9111569U1 (en) * 1991-09-17 1991-11-14 Heilmeier & Weinlein Fabrik für Oel-Hydraulik GmbH & Co KG, 81673 München Control device for at least one hydraulic motor
US5699665A (en) 1996-04-10 1997-12-23 Commercial Intertech Corp. Control system with induced load isolation and relief
DE19703997A1 (en) 1997-02-04 1998-08-06 Mannesmann Rexroth Ag Hydraulic control circuit for a priority and for a subordinate hydraulic consumer
WO2001055603A1 (en) * 2000-01-25 2001-08-02 Hitachi Construction Machinery Co., Ltd. Hydraulic driving device
JP2002206508A (en) 2001-01-05 2002-07-26 Hitachi Constr Mach Co Ltd Hydraulic driving device
DE10224730B4 (en) * 2001-06-29 2012-09-27 Linde Material Handling Gmbh Hydraulic control device

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102013224655A1 (en) * 2013-12-02 2015-06-03 Robert Bosch Gmbh Control arrangement and control valve for such a control arrangement

Also Published As

Publication number Publication date
US7395662B2 (en) 2008-07-08
JP2006526744A (en) 2006-11-24
ATE343687T1 (en) 2006-11-15
JP5081447B2 (en) 2012-11-28
EP1629156A1 (en) 2006-03-01
DE10325295A1 (en) 2004-12-23
WO2004109019A1 (en) 2004-12-16
US20060218914A1 (en) 2006-10-05
DE502004001862D1 (en) 2006-12-07

Similar Documents

Publication Publication Date Title
EP1092095B2 (en) Hydraulic circuit
EP1781952B1 (en) Hydraulic control arrangement
DE102006003414B3 (en) Hydraulic circuit arrangement
EP1135613B1 (en) Method and control device for controlling a hydraulic consumer
EP2092200B1 (en) Hydraulic two-circuit system and interconnecting valve arrangement
EP0935713B1 (en) Valve system and manufacture of same
DE102012220863A1 (en) Control arrangement for driving e.g. hydraulic cylinder for e.g. hydraulic excavators, has control surface of pilot or primary stage of directly or servo-controlled lowering brake valve device acted upon by return control pressure
DE19831595B4 (en) Hydraulic circuit
EP2636908A2 (en) Control assembly
WO2007087962A1 (en) Hydraulic control system with regeneration
EP2142808B1 (en) Hydraulic control arrangement
EP1629156B1 (en) Hydraulic control arrangement
WO2005015030A1 (en) Hydraulic control system for building machinery, particularly excavators
EP1643138B1 (en) Hydraulic control device
EP1629209B1 (en) Hydraulic control arrangement
EP1629207B1 (en) Hydraulic control arrangement
DE4433633C1 (en) Hydraulic switching unit for operation of exchangeable additional device on hydraulic excavators
EP1279870B1 (en) Valve arrangement
EP0823559B1 (en) Hydraulic control device
DE10216119A1 (en) Hydraulic control with load-sensing involves reporting line sectors for pressures and signalling servo-valve to progressively reduce sector pressure per consumer for safety.
EP1170510A2 (en) Hydraulic control arrangement for supplying pressurised fluid preferably to several hydraulic loads
DE102008064138A1 (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
EP1452744B1 (en) Hydraulic control device
DE102012218427A1 (en) Hydraulic control arrangement for use in hydraulic drive of mini excavator, has outlet flow path formed from first working port to pressure medium sink and located above control throttle, and pressure unit placed above hydro pump
DE10355329A1 (en) Hydraulic control arrangement

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

17P Request for examination filed

Effective date: 20051115

AK Designated contracting states

Kind code of ref document: A1

Designated state(s): AT BE BG CH CY CZ DE DK EE ES FI FR GB GR HU IE IT LI LU MC NL PL PT RO SE SI SK TR

GRAP Despatch of communication of intention to grant a patent

Free format text: ORIGINAL CODE: EPIDOSNIGR1

DAX Request for extension of the european patent (deleted)
GRAS Grant fee paid

Free format text: ORIGINAL CODE: EPIDOSNIGR3

GRAA (expected) grant

Free format text: ORIGINAL CODE: 0009210

AK Designated contracting states

Kind code of ref document: B1

Designated state(s): AT BE BG CH CY CZ DE DK EE ES FI FR GB GR HU IE IT LI LU MC NL PL PT RO SE SI SK TR

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

Ref country code: SI

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20061025

Ref country code: SK

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20061025

Ref country code: FI

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20061025

Ref country code: IE

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20061025

Ref country code: PL

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20061025

Ref country code: CZ

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20061025

Ref country code: NL

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20061025

Ref country code: RO

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20061025

REG Reference to a national code

Ref country code: GB

Ref legal event code: FG4D

Free format text: NOT ENGLISH

REG Reference to a national code

Ref country code: CH

Ref legal event code: EP

REG Reference to a national code

Ref country code: IE

Ref legal event code: FG4D

Free format text: LANGUAGE OF EP DOCUMENT: GERMAN

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

Effective date: 20061115

REF Corresponds to:

Ref document number: 502004001862

Country of ref document: DE

Date of ref document: 20061207

Kind code of ref document: P

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

Ref country code: SE

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20070125

Ref country code: BG

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20070125

Ref country code: DK

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20070125

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

Ref country code: ES

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20070205

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

Ref country code: PT

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20070326

NLV1 Nl: lapsed or annulled due to failure to fulfill the requirements of art. 29p and 29m of the patents act
ET Fr: translation filed
REG Reference to a national code

Ref country code: IE

Ref legal event code: FD4D

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

Effective date: 20070726

BERE Be: lapsed

Owner name: BOSCH REXROTH A.G.

Effective date: 20070531

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

Ref country code: MC

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

Effective date: 20070531

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

Ref country code: BE

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

Effective date: 20070531

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

Ref country code: GR

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20070126

REG Reference to a national code

Ref country code: CH

Ref legal event code: PL

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

Ref country code: EE

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20061025

Ref country code: LI

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

Effective date: 20080531

Ref country code: CH

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

Effective date: 20080531

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

Ref country code: CY

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20061025

Ref country code: LU

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

Effective date: 20070528

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

Ref country code: TR

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20061025

Ref country code: HU

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20070426

REG Reference to a national code

Ref country code: FR

Ref legal event code: PLFP

Year of fee payment: 12

REG Reference to a national code

Ref country code: FR

Ref legal event code: PLFP

Year of fee payment: 13

REG Reference to a national code

Ref country code: FR

Ref legal event code: PLFP

Year of fee payment: 14

REG Reference to a national code

Ref country code: FR

Ref legal event code: PLFP

Year of fee payment: 15

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

Ref country code: FR

Payment date: 20180523

Year of fee payment: 15

Ref country code: AT

Payment date: 20180517

Year of fee payment: 15

Ref country code: IT

Payment date: 20180518

Year of fee payment: 15

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

Ref country code: GB

Payment date: 20180523

Year of fee payment: 15

Ref country code: DE

Payment date: 20180725

Year of fee payment: 15

REG Reference to a national code

Ref country code: DE

Ref legal event code: R119

Ref document number: 502004001862

Country of ref document: DE

REG Reference to a national code

Ref country code: AT

Ref legal event code: MM01

Ref document number: 343687

Country of ref document: AT

Kind code of ref document: T

Effective date: 20190528

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

Effective date: 20190528

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

Ref country code: AT

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

Effective date: 20190528

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: 20190528

Ref country code: DE

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

Effective date: 20191203

Ref country code: GB

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

Effective date: 20190528

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: 20190531