EP0958455B1 - Hydraulischer steuerkreis für einen vorrangigen und für einen nachrangigen hydraulischen verbraucher - Google Patents

Hydraulischer steuerkreis für einen vorrangigen und für einen nachrangigen hydraulischen verbraucher Download PDF

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Publication number
EP0958455B1
EP0958455B1 EP97952950A EP97952950A EP0958455B1 EP 0958455 B1 EP0958455 B1 EP 0958455B1 EP 97952950 A EP97952950 A EP 97952950A EP 97952950 A EP97952950 A EP 97952950A EP 0958455 B1 EP0958455 B1 EP 0958455B1
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EP
European Patent Office
Prior art keywords
pressure
hydraulic
valve
control
load
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
EP97952950A
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German (de)
English (en)
French (fr)
Other versions
EP0958455A1 (de
Inventor
Werner Herfs
Jacques Maffini
Thomas Weickert
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
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Bosch Rexroth AG
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Filing date
Publication date
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Publication of EP0958455A1 publication Critical patent/EP0958455A1/de
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Publication of EP0958455B1 publication Critical patent/EP0958455B1/de
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

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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
    • F15B11/16—Servomotor systems without provision for follow-up action; Circuits therefor with two or more servomotors
    • 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
    • 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
    • F15B11/162—Servomotor systems without provision for follow-up action; Circuits therefor with two or more servomotors with sensing of servomotor demand or load for giving priority to particular servomotors or users
    • 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
    • F15B2211/20553—Type of pump variable capacity with pilot circuit, e.g. for controlling a swash plate
    • 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
    • F15B2211/30—Directional control
    • F15B2211/31—Directional control characterised by the positions of the valve element
    • F15B2211/3105—Neutral or centre positions
    • F15B2211/3111—Neutral or centre positions the pump port being closed in the centre position, e.g. so-called closed centre
    • 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
    • F15B2211/45—Control of bleed-off flow, e.g. control of bypass flow to the return line
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/60—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
    • F15B2211/6058—Load sensing circuits with isolator 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
    • F15B2211/70—Output members, e.g. hydraulic motors or cylinders or control therefor
    • F15B2211/75—Control of speed of the output member

Definitions

  • the invention is based on a hydraulic control circuit which is a primary, first hydraulic consumer and a subordinate, second hydraulic consumer with pressure medium can be supplied and the characteristics from the generic term of claim 1.
  • Such a hydraulic control circuit is known from DE 43 28 283 A1 known.
  • the two hydraulic consumers flow the pressure medium each via a metering orifice, the priority, first hydraulic consumers assigned first Orifice plate upstream of a pressure compensator and the subordinate, second hydraulic consumers assigned, a pressure compensator is connected downstream of the second metering orifice. aid of the pressure compensators are supplied with sufficient quantity of pressure medium regardless of the load pressures of the hydraulic consumers maintain constant pressure differences across the metering orifices, so that the flowing to a hydraulic consumer Pressure medium quantity only from the opening cross section of the respective Metering orifice depends.
  • an adjustable hydraulic pump depending on the highest Load pressure can be controlled such that the pressure in an inlet line by a certain pressure difference above the highest Load pressure is.
  • the downstream of the second metering orifice Pressure compensator is in the opening direction from the pressure after the second Orifice plate and in the closing direction from one to the rear Control room applied control pressure, which is usually the highest load pressure of all from the same hydraulic pump supplied hydraulic consumers.
  • each with pressure medium flows through a metering orifice with an upstream pressure compensator, in the closing direction only from the pressure in front of the orifice and in Opening direction only from the load pressure of the respective hydraulic Consumer and is acted upon by a compression spring receives there is no load-independent flow distribution.
  • DE 43 28 283 A1 is now a priority circuit between an LS consumer and one or more LUDV consumers, in which the LS consumer is primarily supplied with pressure medium.
  • a priority valve is provided, one with a Line section connected upstream of the first metering orifice, first connection and one connected to the load signaling line has second connection and its valve member in the direction Open the connection between the first port and the second Connection of the load pressure of the primary hydraulic consumer, So the LS consumer, and an additional force can be applied is.
  • the priority valve according to the control DE 43 28 283 A1 is towards closing the connection between the first port and the second port of pressure acted on in the second connection. In this way, a priority supply of pressure medium to the LS consumer ensured.
  • the pressure in the supply line is determined in certain Cases unnecessarily high, so that there is a loss of performance. Such a case is e.g.
  • DE 35 07 122 C2 shows a priority control between two LS-consumers. These two hydraulic consumers are flowing So pressure medium amount each via an orifice and this metering orifice upstream pressure compensator in the closing direction is acted upon by the pressure in front of the metering orifice.
  • the Pressure compensator assigned to the primary hydraulic consumer is in the opening direction from the load pressure of this hydraulic Consumer and acted upon by a compression spring.
  • the pressure compensator for the subordinate hydraulic consumer is also in the closing direction by a compression spring and also pressurized between a fixed throttle and a proportional orifice serving as a priority valve is tapped between the fixed choke and one Tank line is switched and from the pressure difference on the metering orifice of the primary hydraulic consumer controlled becomes.
  • undersaturation i.e. inadequately funded
  • the quantity of pressure medium reduces the pressure difference the metering orifice of the hydraulic to be operated primarily with pressure medium Consumer, so the proportional aperture is something opens, the pressure between her and the fixed throttle drops a little and the pressure balance of the subordinate to be operated with pressure medium hydraulic consumer closes so far that for the priority hydraulic consumers again sufficient pressure medium is available.
  • the aim of the invention is to provide a hydraulic control circuit has the features from the preamble of claim 1 with which is an LS consumer versus one or more LUDV consumers should be primarily supplied with pressure medium, so to develop that excessively high power losses in operation be avoided.
  • Control circuit can be found in the subclaims.
  • the pressure difference at the first orifice is from the priority valve sensed. Since in the event of undersaturation the the first metering orifice upstream of the pressure compensator is completely open, can a control room on the valve member of the priority valve according to Claim 4 upstream of the first pressure compensator with the feed line be connected. This can be advantageous in terms of construction Design of the individual components of the control his. In terms of construction, it may also be an advantage if according to claim 5 a control pressure chamber on the valve member of the Priority valve and the first connection of the priority valve on the same side of the first pressure compensator with the inlet to the first Orifice plate are connected.
  • a bypass line around the priority valve provided around that a current point downstream of the first metering orifice connects to the load reporting line and in the one to Check valve opening check valve is arranged.
  • this Load pressure prevails in the load reporting line and if sufficient Pressure medium quantity for all actuated consumers the pressure difference via the first metering orifice from the upstream pressure compensator is determined.
  • the pressure difference is only when there is undersaturation determined by the additional force on the priority valve to which a smaller pressure differential is usually equivalent to the spring force on the first pressure compensator.
  • a variable displacement pump 10 sucks with an adjustment 11 pressure medium from a tank 12 and there is in a system from leads 13.
  • a first is via the supply lines hydraulic consumer 14, which is designed as a synchronous cylinder is, and at least a second hydraulic consumer 15, which is a differential cylinder, supplied with pressure medium.
  • the direction and speed of the synchronous cylinder 14 by a corresponding actuation of a 4/3 proportional directional valve 16 determines whose valve spool is in a central position is spring-centered, in which the four working connections and a control connection 18 of the directional control valve 16 are blocked.
  • the control terminal 18 is downstream of the metering orifice with the flow to the synchronous cylinder 14 connected.
  • a 2-way pressure compensator 20 is inserted, whose control piston in the direction of closing the pressure upstream Metering orifice 17 and in the direction of opening via a control line 61 from the pressure in the control port 18 of the directional control valve 16, that is from Load pressure of the synchronous cylinder 14, and from a control spring 21 is applied.
  • the force of the control spring 21 is designed that you have a pressure difference of e.g. 15 bar via an orifice 17 is equivalent.
  • the one associated with the first hydraulic consumer 14 first pressure compensator 20 upstream of the first orifice 17 is the second hydraulic consumer 15th assigned second pressure compensator 30 to a second metering orifice 31 downstream.
  • a directional control valve 32 is arranged, in comparison for the pressure drop at the metering orifice 31, no significant Pressure drop occurs more when the differential cylinder 15 is actuated becomes.
  • the metering orifice 31 and that for direction control necessary control grooves are in a known manner on the same valve spool trained so that direction and speed control go together without further ado.
  • the Control piston 33 of the pressure compensator 30 is opened towards the front the connection between the metering orifice 31 and the directional control valve 32 from the pressure after the metering orifice and backwards in the direction Closing the connection of one in a control pressure chamber 34 prevailing control pressure and a weak compression spring 35, which is a pressure of e.g. is equivalent to only 0.5 bar.
  • the front of the control piston 33 is in a Control piston extending channel 36 with the control pressure chamber 34 connected, one in the channel 36 to the control pressure chamber opening check valve 37 is arranged.
  • the pressure compensator 30 and the directional control valve 32 for the second hydraulic consumer 15 can additional metering orifices, pressure compensators and directional valves for others hydraulic consumers connected to the system of the feed lines 13 his.
  • the control pressure chambers 34 are all pressure compensators 30 connected to each other, so that in these control pressure rooms the same pressure is applied.
  • the control pistons 33 of the pressure compensators look for themselves when actuating a second hydraulic To bring the consumer into such a position in which to their front one only around that of the force of the compression spring 35 equivalent pressure difference sets higher pressure than in the Control pressure rooms 34.
  • the control pressure chambers 34 are connected to a load signaling line 38, which leads to the adjustment 11 of the pump 10.
  • the load reporting line 38 leads, as can be seen from Figure 4, the load reporting line 38 to a control valve 39 with three connections, one of which one connected to an actuating cylinder 40 of the variable displacement pump 10 is.
  • Another connection of the control valve 39 is with a supply line 13 and the third connection to tank 12.
  • the control piston of the control valve 39 is in the direction of Connection of the first connection with the second connection from Pressure in the supply line 13 and in the direction of a connection of the first connection with the third connection from the pressure in the Load signaling line 38 and acted upon by a control spring 41.
  • Variable pumps and control valves according to the circuit diagram according to the figure 4 are generally known and readily available on the market.
  • the pump control causes that a pressure is established in the feed line 13, which is around a the force of the control spring 41 equivalent pressure difference over the Pressure in the load reporting line 38 is.
  • the pressure difference is e.g. 20 bar, is therefore higher than the force of the control spring 21 of the first pressure compensator 20 equivalent pressure difference of 15 bar.
  • the first hydraulic consumer 14 is to take priority over the second hydraulic consumer 15 supplied with pressure medium become.
  • a priority valve 45 is provided, which as Proportional diaphragm with an input 46 and an output 47 is trained. The latter is connected to the load signaling line 38.
  • the input 46 is upstream of the pressure compensator 20 with a Lead 13 connected.
  • the valve member 48 of the priority valve will close towards the connection between the entrance and the output of one in one connected to a feed line 13 first control pressure chamber 49 prevailing pressure and in Direction of opening the connection from one in a second control pressure chamber prevailing pressure and a control spring 51 applied.
  • the second control pressure chamber 50 is activated of the directional control valve 16 via the control line 61 with one point connected downstream of an orifice 17.
  • the control spring 51 is e.g. designed so that the valve member 48 of the priority valve 45 there is a balance of forces when the pressure in the first control pressure chamber 49 by 13 bar higher than the pressure in second control pressure chamber 50. This pressure difference is lower than that of the force of the control spring 21 of the pressure compensator 20 equivalent Pressure difference.
  • the first hydraulic consumer 14, primarily with pressure medium is to be operated without the priority valve 45 would have to come into operation, always with sufficient pressure medium supplied when the sum of its load pressure plus the control ⁇ p the adjustment 11 on the variable displacement pump 10 is smaller than the highest load pressure of all simultaneously operated second hydraulic consumer 15. Because pressure medium always flows to the hydraulic consumer with the lowest load pressure.
  • the load pressure of the first hydraulic Consumer 14 higher than the highest load pressure of all simultaneously actuated second hydraulic consumer 15 is. It is e.g. 80 bar, while the highest load pressure is the LUDV consumer is 60 bar.
  • the directional valve is actuated 16 are then in the control pressure chamber 50 of the priority valve 45 to 80 bar.
  • 93 bar act in Proportional valve 45 opens in the direction of the control piston Valve then a balance of forces if there are 49 93 bar in the first control pressure chamber.
  • connection 47 of the priority valve 45 there is also between the second connection 47 of the priority valve 45 and the load signaling line 38 a check valve 64 arranged. This blocks to connection 47.
  • the control spring 51 determines the Priority valve 45 the pressure drop at an orifice 17 even if the amount of pressure medium delivered is sufficient, if the load pressure of the hydraulic consumer to be operated as a priority 14 minus the difference between that of the force of the control spring 41 of the control valve 39 equivalent pressure and that of Force of the control spring 51 of the priority valve 45 equivalent Pressure is greater than the highest load pressure of all actuated LUDV consumer 15. Because then 38 in the load reporting line Via the priority valve 45, a pressure is regulated, which is around the Difference between the equivalent pressure of the control spring 41 and the Equivalent pressure of the control spring 51 below the load pressure of the priority hydraulic user 14 is located, e.g. e.g. at a load pressure of 80 bar, an equivalent pressure the control spring 41 of 20 bar and an equivalent pressure of the control spring 51 in the amount of 13 bar is 73 bar. In case of undersaturation the pressure in the load signaling line 38 rises above it Value.
  • the funding is sufficient Pressure medium quantity and load-bearing priority hydraulic Consumer 14 the load pressure of this hydraulic consumer passed via the check valve 63 into the load signaling line 38.
  • the pressure in the system of the feed lines 13 is thus around Equivalent pressure of the control spring 41, that is, the control ⁇ p of the variable displacement pump 10 above the load pressure of the hydraulic consumer 14, i.e. at a load pressure of e.g. 80 bar and one Control ⁇ p of e.g. 20 bar 100 bar.
  • the pressure drop over a metering orifice 17 then becomes as in the case of a load-carrying second Consumer 15 of the force of the control spring 21 of the pressure compensator 20 determined.
  • Priority valve 45 equivalent pressure e.g. to 80 bar plus 13 bar has dropped to 93 bar
  • the pressure drop is via a metering orifice 17 of the directional control valve 16 is 13 bar determined by the force of the control spring 51.
  • Another downsizing the pressure drop across an orifice 17 does not occur because the pressure in the Load reporting line 38 increased via the priority valve 45 and thereby the pressure compensators 30 of the LUDV consumers in the closing direction be adjusted.
  • the check valve 64 prevents a pressure medium flow from the hydraulic Consumer 14 via the check valve 63 in that System of supply lines 13, if e.g. at the start of an operation the pressure in the supply lines is not yet above the load pressure lies.

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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)
  • Jib Cranes (AREA)
EP97952950A 1997-02-04 1997-12-16 Hydraulischer steuerkreis für einen vorrangigen und für einen nachrangigen hydraulischen verbraucher Expired - Lifetime EP0958455B1 (de)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
DE19703997 1997-02-04
DE19703997A DE19703997A1 (de) 1997-02-04 1997-02-04 Hydraulischer Steuerkreis für einen vorrangigen und für einen nachrangigen hydraulischen Verbraucher
PCT/EP1997/007072 WO1998034031A1 (de) 1997-02-04 1997-12-16 Hydraulischer steuerkreis für einen vorrangigen und für einen nachrangigen hydraulischen verbraucher

Publications (2)

Publication Number Publication Date
EP0958455A1 EP0958455A1 (de) 1999-11-24
EP0958455B1 true EP0958455B1 (de) 2003-04-23

Family

ID=7819166

Family Applications (1)

Application Number Title Priority Date Filing Date
EP97952950A Expired - Lifetime EP0958455B1 (de) 1997-02-04 1997-12-16 Hydraulischer steuerkreis für einen vorrangigen und für einen nachrangigen hydraulischen verbraucher

Country Status (7)

Country Link
US (1) US6289675B1 (ko)
EP (1) EP0958455B1 (ko)
JP (1) JP4156037B2 (ko)
KR (1) KR100528031B1 (ko)
AT (1) ATE238497T1 (ko)
DE (2) DE19703997A1 (ko)
WO (1) WO1998034031A1 (ko)

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DE19828963A1 (de) * 1998-06-29 1999-12-30 Mannesmann Rexroth Ag Hydraulische Schaltung
CN1316038A (zh) * 1999-04-26 2001-10-03 日立建机株式会社 液压回路装置
DE19937224A1 (de) 1999-08-06 2001-02-08 Mannesmann Rexroth Ag Hydraulische Steueranordnung zur bedarfstromgeregelten (load-sensing-geregelten) Druckmittelversorgung von vorzugsweise mehreren hydraulischen Verbrauchern
DE19957027B4 (de) * 1999-11-26 2009-11-26 Linde Material Handling Gmbh Hydrostatisches Antriebssystem
DE10034431A1 (de) * 2000-07-14 2002-07-25 Juergen Schenk Hydrauliksystem für ein Arbeitsgerät mit einem Sonderverbraucher
DE10119276B4 (de) * 2001-04-20 2009-12-10 Bosch Rexroth Aktiengesellschaft Hydraulischer Steuerkreis
DE10325295A1 (de) * 2003-06-04 2004-12-23 Bosch Rexroth Ag Hydraulische Steueranordnung
GB2408526B (en) 2003-11-26 2007-10-17 Schlumberger Holdings Steerable drilling system
ATE378517T1 (de) 2004-01-07 2007-11-15 Bosch Rexroth Ag Stromventil und stromteiler mit mehreren stromventilen
JP4446822B2 (ja) * 2004-07-13 2010-04-07 日立建機株式会社 作業車両の油圧駆動装置
DE102005047310A1 (de) 2005-09-30 2007-04-05 Bosch Rexroth Ag Hydraulische Steuervorrichtung
DE102005055309A1 (de) * 2005-11-21 2007-05-24 Bosch Rexroth Ag Hydraulische Steuervorrichtung
DE102007028864A1 (de) 2007-03-27 2008-10-02 Robert Bosch Gmbh Hydraulische Steueranordnung
US7748279B2 (en) * 2007-09-28 2010-07-06 Caterpillar Inc Hydraulics management for bounded implements
US7908853B2 (en) * 2007-09-28 2011-03-22 Caterpillar Inc. Hydraulic balancing for steering management
DE102008012301A1 (de) 2008-03-03 2009-09-10 Robert Bosch Gmbh Verfahren zur Steuerung und Regelung der Position eines Arbeitsarmes einer Arbeitsmaschine und Vorrichutng zur Durchführung des Verfahrens
WO2011096001A1 (en) * 2010-02-02 2011-08-11 Bucher Hydraulics S.P.A. Hydraulic section for load sensing applications and multiple hydraulic distributor
JP5948260B2 (ja) * 2013-01-24 2016-07-06 Ｋｙｂ株式会社 流体圧制御装置

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Also Published As

Publication number Publication date
DE19703997A1 (de) 1998-08-06
ATE238497T1 (de) 2003-05-15
US6289675B1 (en) 2001-09-18
DE59709931D1 (de) 2003-05-28
KR100528031B1 (ko) 2005-11-15
WO1998034031A1 (de) 1998-08-06
EP0958455A1 (de) 1999-11-24
KR20000070768A (ko) 2000-11-25
JP4156037B2 (ja) 2008-09-24
JP2001509867A (ja) 2001-07-24

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