EP2620656A2 - Composant de soupape à détection de charge avec commande à pression - Google Patents

Composant de soupape à détection de charge avec commande à pression Download PDF

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Publication number
EP2620656A2
EP2620656A2 EP13150235.3A EP13150235A EP2620656A2 EP 2620656 A2 EP2620656 A2 EP 2620656A2 EP 13150235 A EP13150235 A EP 13150235A EP 2620656 A2 EP2620656 A2 EP 2620656A2
Authority
EP
European Patent Office
Prior art keywords
pressure
valve
consumer
pump
port
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
Application number
EP13150235.3A
Other languages
German (de)
English (en)
Other versions
EP2620656B1 (fr
EP2620656A3 (fr
Inventor
Christian Duerr
Robert Rueppel
Kjeld Madsen
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Robert Bosch GmbH
Original Assignee
Robert Bosch GmbH
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Robert Bosch GmbH filed Critical Robert Bosch GmbH
Publication of EP2620656A2 publication Critical patent/EP2620656A2/fr
Publication of EP2620656A3 publication Critical patent/EP2620656A3/fr
Application granted granted Critical
Publication of EP2620656B1 publication Critical patent/EP2620656B1/fr
Not-in-force legal-status Critical Current
Anticipated expiration legal-status Critical

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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
    • F15B11/02—Systems essentially incorporating special features for controlling the speed or actuating force of an output member
    • F15B11/04—Systems essentially incorporating special features for controlling the speed or actuating force of an output member for controlling the speed
    • F15B11/05—Systems essentially incorporating special features for controlling the speed or actuating force of an output member for controlling the speed specially adapted to maintain constant speed, e.g. pressure-compensated, load-responsive
    • F15B11/055—Systems essentially incorporating special features for controlling the speed or actuating force of an output member for controlling the speed specially adapted to maintain constant speed, e.g. pressure-compensated, load-responsive by adjusting the pump output or bypass
    • 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
    • F15B2211/20546—Type of pump variable 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
    • F15B2211/20—Fluid pressure source, e.g. accumulator or variable axial piston pump
    • F15B2211/25—Pressure control functions
    • F15B2211/253—Pressure margin control, e.g. pump pressure in relation to 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
    • F15B2211/30—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
    • F15B2211/30535—In combination with a pressure compensating valve the pressure compensating valve is arranged between pressure source and 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
    • F15B2211/50—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
    • F15B2211/50518—Pressure control characterised by the type of pressure control means the pressure control means controlling a pressure upstream of the pressure control means 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
    • F15B2211/50—Pressure control
    • F15B2211/515—Pressure control characterised by the connections of the pressure control means in the circuit
    • F15B2211/5159—Pressure control characterised by the connections of the pressure control means in the circuit being connected to an output member 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
    • F15B2211/60—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
    • 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
    • F15B2211/65—Methods of control of the load sensing pressure
    • F15B2211/654—Methods of control of the load sensing pressure the load sensing pressure being lower than the load pressure

Definitions

  • the invention relates to a valve assembly according to the preamble of claim 1.
  • valve assembly is known.
  • This valve assembly is composed of several consumer assemblies that can be assembled as a whole, which due to their geometric shape are also referred to as valve disks.
  • Each consumer assembly has a first and a second consumer port for connecting an associated hydraulic consumer, which may be, for example, a cylinder or a hydraulic motor.
  • the consumer assembly has a pump port for connecting a pump, wherein the pump port is connected to a pump line, which passes through all consumer assemblies.
  • a tank connection is provided for connecting a tank, which is connected to a tank line, which also penetrates all consumer assemblies.
  • Each consumer assembly has a proportional directional control valve that has at least one continuously variable metering orifice that can control fluid flow from the pumping line to one of the associated consumer ports.
  • Each metering restrictor is preceded by a pressure compensator, that is connected in series on the pump side, so that a first pressure results between the pressure compensator and the metering restrictor.
  • each consumer assembly is associated with a shuttle valve to which a load pressure of the associated consumer assembly is connected.
  • the shuttle valves are interconnected in a cascade that ends at the LS port, so that there is the highest load pressure of all consumer assemblies.
  • the LS connection is in turn connected to a pump regulator which controls the Adjusting the pump delivery pressure to a pressure which is a predetermined third pressure difference above the highest load pressure.
  • the pump can be a pump with a constant displacement volume, the pressure regulator being a parallel-connected pressure compensator which directs part of the pump delivery flow back into the tank. But it can also be provided with a variable displacement displacement pump, wherein the pump controller adjusts the displacement so that there is the desired delivery pressure. The latter embodiment is significantly more energy efficient.
  • first pressure relief valves which are also referred to as LS-pressure relief valves.
  • LS-pressure relief valves As the load pressure rises above the trigger pressure of the first relief valve, they vent so much hydraulic fluid into the tank until the load pressure falls below the trigger pressure. As little as possible hydraulic fluid should be discharged into the tank, because this is associated with high energy losses. Therefore, a damping throttle is provided, which is connected to the metering throttle tank side in series, wherein the damping throttle, the first pressure relief valve is connected in series on the tank side. Between the metering throttle and the damping throttle results in a second pressure, which is connected to the metering throttle associated with the consumer port.
  • the third pressure is the already mentioned load pressure, which is connected to the shuttle valve.
  • Such a valve assembly can be used for example in a tree harvester.
  • the consumer is a cylinder that presses the delimbing knife against a tree trunk to remove the branches on a tree trunk.
  • the release force set on the first pressure relief valve corresponds to the force with which the delimbing knives mentioned are pressed on average against the tree trunk. This force must be adapted to the hardness of the wood present so that the tree trunk is not damaged.
  • the release force of the first pressure relief valve is therefore electrically adjustable so that it can be adjusted by the user to the control of the tree harvester.
  • the object of the invention is to reduce the mentioned pressure peaks of the second pressure.
  • damage to the tree trunk should be avoided when using the valve assembly in a tree harvester. In this case, excessive energy loss should be avoided.
  • this object is achieved in that the second pressure is connected to a second pressure relief valve, the release pressure is adjustable.
  • the second pressure relief valve By the second pressure relief valve, the second pressure is limited upward, so that the pressure peaks of the second pressure are limited upwards.
  • the trigger pressure must therefore be adjusted so that the second pressure relief valve responds as rarely as possible, but all harmful pressure peaks are avoided. Therefore, the release pressure of the second pressure relief valve is adjustable. It can be thought that the trigger pressure of the second pressure relief valve is electrically adjustable so that it can be set by the control of the tree harvester to the desired value.
  • the release pressure of the second pressure relief valve may be hydraulically adjustable by means of the third pressure so that it is above the third pressure by a predetermined second pressure difference.
  • the already mentioned electrical control has the disadvantage that it is very expensive, especially if the release force to be set with high accuracy.
  • the proposed second pressure relief valve is very simple and is also already manufactured as standard.
  • the proposed solution requires much less space than said electrical control of the trigger pressure.
  • the proposed hydraulic control of the trigger pressure is much more reliable than an electrical control.
  • the user of the tree harvester has to set only a single parameter, namely the contact pressure or the trigger pressure of the first pressure relief valve.
  • the pressure balance may have a load holding position in which it is locked, wherein the load holding position is set when the pressure at the pump connection falls below the second pressure. This is to ensure that the consumer stands still when the pump pressure is no longer sufficient to move it. This increases the security of the entire system. However, precisely this measure increases the already mentioned pressure peaks of the second pressure, so that the invention is particularly advantageous in this embodiment of the valve assembly.
  • the second pressure relief valve a check valve may be connected in parallel, which is installed so that the second pressure can not fall below the ambient pressure.
  • the consumer can use the non-return valve to suck in hydraulic fluid from the tank. This excludes the possibility of creating a free space in the pressure chambers of the consumer which is not filled with hydraulic fluid. Such clearance could result in uncontrolled consumer movements that are very dangerous.
  • the check valve and the second pressure relief valve may be designed in the form of an assembly that can be assembled as a whole. This results in a particularly compact valve assembly, which is also easy to install.
  • the assembly mentioned above can also be produced in series and therefore cost, since it can also be used for many other applications.
  • the trigger pressure of the first pressure relief valve can be both manually and electrically adjustable. Via the electrical adjustment, the triggering pressure of the first pressure relief valve can be set by the control of a higher-level machine. By means of the manual adjustment, it can be ensured that the release pressure does not fall below a predetermined value. As a result, the reliability of the parent machine is increased.
  • the metering throttle may be part of a proportional directional valve, with which the direction of movement of the associated consumer can be adjusted.
  • the proportional directional control valve has at least two continuously variable metering throttles, one throttle being connected to the first consumer port and the second throttle being connected to the second consumer port.
  • the throttle cross-sections of the two metering throttles can be adjusted by a common valve slide, so that there is the desired adjustability of the direction of movement.
  • the first and the second consumer connection can be provided on a first consumer assembly which can be mounted as a whole, wherein at least one further consumer assembly which can be mounted as a whole is provided, to which an assigned consumer can be connected, a pump line to the pump connection and a tank line to the tank connection are connected, wherein the pump and the tank line respectively enforce all consumer assemblies, each consumer assembly having a shuttle valve which are interconnected in a cascade that terminates at the LS port, wherein the third pressure is connected to the shuttle valve of the first consumer board.
  • the present invention is primarily for a Valve assembly thought to which several consumers are connected, which are supplied via a common pump with hydraulic fluid.
  • the first and / or the second pressure relief valve may be configured as a whole mountable assemblies that are grown from the outside to the first consumer assembly. This is to achieve that the present invention can be used with the valve assembly already produced in series.
  • the existing consumer modules must be provided only with vain additional holes.
  • Fig. 1 shows a circuit diagram of a hydraulic drive unit with a single load 11 and a valve assembly according to the invention 10.
  • the consumer 11 in the form of a double-acting cylinder is connected via a first and a second consumer port A; B connected to the valve assembly 10.
  • a pump 13 is provided with a constant displacement volume, which hydraulic fluid from a tank 12 can promote to the pump port P of the valve assembly 10.
  • a delivery pressure regulator 14 is provided, which is designed in the form of a pressure balance, which is connected in parallel to the pump 13.
  • the delivery pressure regulator 14 is pressed by a spring 15 in the closed position, wherein the LS port of the valve assembly 10 with the spring side and the delivery pressure of the pump 13 are connected to the spring opposite side of the delivery pressure regulator 14.
  • the delivery pressure regulator 14 opens a connection to the tank 12 when the delivery pressure of the pump 13 exceeds the pressure at the LS connection by the pressure equivalent of the spring 15.
  • the valve assembly 10 includes a continuously variable metering orifice 20, which can control the flow of fluid from the pump 13 to the first consumer port A.
  • the metering orifice 20 is connected in series with a pressure compensator 22, which is pressed by a spring 23 into the open position. Between the pressure compensator 22 and the metering throttle 20 results in a first pressure 41, which is connected to the spring 23 opposite side of the pressure compensator 22.
  • the metering throttle 20 is connected in series with a damping throttle 21, so that a second pressure 42 results between the metering throttle 20 and the damping throttle 21, which pressure is connected to the first consumer port A.
  • the second consumer port B is connected to the tank port T, which in turn is connected to the tank 12.
  • a first pressure relief valve 31 is connected in series, which in turn is connected to the tank port T. Between the damping throttle 21 and the first pressure relief valve 31 results in a third pressure 43 which is connected to the spring side of the pressure compensator 22.
  • the pressure compensator 22 therefore regulates the pressure difference between the first and third pressures 41; 43 to the pressure equivalent of the spring 23 a.
  • the trigger pressure of the first pressure relief valve 31 can be adjusted both manually and electrically. The electrical adjustment is provided for connection to the control of a parent machine, such as a tree harvester.
  • a second pressure limiting valve 32 which connects the first consumer port A to the tank port T.
  • the second pressure limiting valve 32 is pressed by a spring 33 in the closed position, wherein the third pressure 43 is additionally connected to the spring side.
  • the pressure at the first consumer port A is connected, so that the second pressure relief valve 32 opens the connection to the tank 12 when the pressure at the first consumer port A exceeds the sum of the third pressure 43 and the pressure equivalent of the spring 33 of the second pressure relief valve 32 ,
  • the first pressure relief valve 31 thus causes an energy-saving load pressure control at the first consumer port A, wherein the second pressure relief valve 32 limits the possible pressure peaks on the first consumer port A. It is not necessary to control the second pressure relief valve 32 separately from the outside.
  • Fig. 2 1 shows a circuit diagram of a first embodiment of a first consumer assembly 50 according to the invention.
  • This consumer assembly 50 is for use in a valve assembly according to the catalog " Mono and disc load-sensing control block - Type M4-12 "from Bosch Rexroth AG (Order No. RD 64276, Edition 08/2010 ) intended.
  • the cited catalog is referred to in its entirety and incorporated into the content of the present application.
  • the consumer assembly 50 is comprised of first, second and third subassemblies 60; 70; 71 assembled, each of which can be pre-assembled as a whole. Subsequently, the second and third subassemblies 70; 71 is externally attached to the first subassembly 60.
  • the first sub-assembly 60 is a valve disc according to the above catalog, compared to the standard state, each with an additional first, second, third and fourth bore 61; 62; 63; 64 was provided.
  • the first subassembly 60 is penetrated by a pump line P, a pilot oil feed line X, a pilot oil discharge line Y, an LS line and a tank line T, which are each arranged to be associated Supplement lines from adjacent consumer modules to a line that passes through the entire valve assembly.
  • the pump line P is analogous to Fig. 1 connected to a pump, the LS line to the delivery pressure regulator of the pump and the tank line T to the tank.
  • the pilot oil feed line X is also connected to the pump or to a separate pilot oil pump with the pilot oil drain line Y connected to the tank.
  • the first subassembly 60 includes a proportional directional control valve 52 having a middle blocking position and a first and a second working position.
  • the pump line P In the first working position, the pump line P is connected to the first consumer port A via a first continuously variable metering throttle and the second consumer port B is connected to the tank line T.
  • the pump line P In the second working position, the pump line P is connected via a second continuously variable metering orifice with the second consumer port B, wherein the first consumer port A is connected to the tank line T.
  • the valve spool of the proportional directional control valve 52 is pressed by two return springs 53 in the middle blocking position, wherein the first and the second working position can be adjusted hydraulically with an associated pilot valve 55.
  • the pilot valves 55 may be electrically controlled by the controller of the parent machine.
  • the already mentioned damping throttle 21 is integrated in the proportional directional control valve 52, so that the third pressure is applied to its LS port 54.
  • the LS port 54 of the proportional directional control valve 52 is connected to a shuttle valve 51, the shuttle valves 51 of adjacent first subassemblies 60 being interconnected into a cascade that terminates in the LS port of the valve assembly.
  • the LS port 54 of the proportional directional control valve 52 is connected via the second bore 62 to the second subassembly 70, which in turn is connected via the first bore 61 to the control oil discharge line Y.
  • a pressure compensator 22 is connected in series, compared to the pressure compensator after Fig. 1 an additional load holding position 24 has.
  • the connection is blocked from the pump line P to the proportional directional control valve 52, wherein the pressure compensator 22 is pressed by its spring 23 in the load holding position 24.
  • a pressure in the pump line causes the valve spool of the pressure compensator 22 is displaced against the spring 23, so that the connection from the pump line P to the proportional directional control valve 52 is fully open.
  • the pressure compensator works after Fig. 2 as the pressure balance according to Fig. 1 ,
  • the second subassembly 70 includes the first pressure relief valve 31, the trigger pressure of which is adjustable both electrically and manually.
  • the third subassembly 71 comprises the second pressure limiting valve 32.
  • the third subassembly 71 is connected to the first and the second consumer connection 65; 66 of the first subassembly 60 grown.
  • the first and the second consumer connection 65; 66 are each directly to the first and the second load port A; B of the consumer assembly 50, which are disposed on the third subassembly 71.
  • the second pressure relief valve 32 is installed, to which a separate check valve 34 is connected in parallel.
  • the return valve 34 is installed so that the consumer can suck hydraulic fluid from the tank, so that no negative pressure can occur in the consumer.
  • the spring side 33 of the second pressure limiting valve 32 is connected via the third bore 63 in the first subassembly 60 to the LS port 54 of the proportional directional control valve 52.
  • Fig. 3 shows a circuit diagram of a second embodiment of a first consumer assembly according to the invention 50. This differs only in terms of the second pressure relief valve 32 of the first consumer assembly after Fig. 2 , so far as the comments on Fig. 2 can be referenced.
  • the check valve 34 has been integrated into the second pressure relief valve 32, so that they can be mounted as a whole Form assembly.
  • Such a pressure relief valve is for example from the catalog " Pressure limiting and feed valve, pilot operated - Type MHDBN "from Bosch Rexroth AG (Order No. RD 64602, Edition 09/2011 ), so that in this regard can be made to the statements there.

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  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Fluid Mechanics (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Fluid-Pressure Circuits (AREA)
  • Safety Valves (AREA)
EP13150235.3A 2012-01-26 2013-01-04 Composant de soupape à détection de charge avec commande à pression Not-in-force EP2620656B1 (fr)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
DE102012001549A DE102012001549A1 (de) 2012-01-26 2012-01-26 Load-Sensing-Ventilbaugruppe mit Drucksteuerung

Publications (3)

Publication Number Publication Date
EP2620656A2 true EP2620656A2 (fr) 2013-07-31
EP2620656A3 EP2620656A3 (fr) 2017-03-29
EP2620656B1 EP2620656B1 (fr) 2018-12-26

Family

ID=47561339

Family Applications (1)

Application Number Title Priority Date Filing Date
EP13150235.3A Not-in-force EP2620656B1 (fr) 2012-01-26 2013-01-04 Composant de soupape à détection de charge avec commande à pression

Country Status (3)

Country Link
EP (1) EP2620656B1 (fr)
BR (1) BR102013001832A2 (fr)
DE (1) DE102012001549A1 (fr)

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN105443475A (zh) * 2015-12-30 2016-03-30 中国铁建重工集团有限公司 负载压力自适应控制液压系统、控制方法及预切槽机
FR3054008A1 (fr) * 2016-07-13 2018-01-19 Bosch Gmbh Robert Installation de distributeur hydraulique equipee d'un absorbeur de chocs de pression

Families Citing this family (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102020210441A1 (de) * 2020-08-17 2022-02-17 Hawe Hydraulik Se Proportional-Schieberventil mit einem Druckbegrenzungsventil, Druckbegrenzungsventil und Hydrauliksystem

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Publication number Priority date Publication date Assignee Title
DE3709504C2 (de) * 1987-03-23 1995-02-02 Rexroth Mannesmann Gmbh Ventileinrichtung
DE4420682A1 (de) * 1994-06-14 1996-01-04 Rexroth Mannesmann Gmbh Hydrauliksteuerung für eine teilende Werkzeugmaschine
DE19715020A1 (de) * 1997-04-11 1998-10-15 Rexroth Mannesmann Gmbh Hydraulische Steueranordnung, insbesondere für ein Fahrzeug zum Transport von Absetzmulden
DE19734020A1 (de) * 1997-08-06 1999-02-11 Mannesmann Rexroth Ag Vorgesteuertes Druckbegrenzungsventil
FI104531B (fi) * 1998-09-15 2000-02-29 Timberjack Oy Karsintalaitteisto ja menetelmä karsintalaitteistossa

Non-Patent Citations (3)

* Cited by examiner, † Cited by third party
Title
"Druckbegrenzungs- und Einspeiseventil, vorgesteuert - Typ MHDBN", September 2011, BOSCH REXROTH AG
"Load-Sensing-Steuerblock in Mono- und Scheibenbauweise - Typ M4-12", August 2010, BOSCH REXROTH AG
"Load-Sensing-Steuerblock in Mono-und Scheibenbauweise - Typ M4-12", August 2010, BOSCH REXROTH AG

Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN105443475A (zh) * 2015-12-30 2016-03-30 中国铁建重工集团有限公司 负载压力自适应控制液压系统、控制方法及预切槽机
CN105443475B (zh) * 2015-12-30 2017-10-27 中国铁建重工集团有限公司 负载压力自适应控制液压系统、控制方法及预切槽机
FR3054008A1 (fr) * 2016-07-13 2018-01-19 Bosch Gmbh Robert Installation de distributeur hydraulique equipee d'un absorbeur de chocs de pression

Also Published As

Publication number Publication date
EP2620656B1 (fr) 2018-12-26
DE102012001549A1 (de) 2013-08-01
BR102013001832A2 (pt) 2016-02-23
EP2620656A3 (fr) 2017-03-29

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