WO2003074877A1 - System zur steuerung einer hydraulischen verstellpumpe - Google Patents
System zur steuerung einer hydraulischen verstellpumpe Download PDFInfo
- Publication number
- WO2003074877A1 WO2003074877A1 PCT/EP2003/002138 EP0302138W WO03074877A1 WO 2003074877 A1 WO2003074877 A1 WO 2003074877A1 EP 0302138 W EP0302138 W EP 0302138W WO 03074877 A1 WO03074877 A1 WO 03074877A1
- Authority
- WO
- WIPO (PCT)
- Prior art keywords
- flow
- actuating device
- pressure
- valve
- section
- Prior art date
Links
Classifications
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
- F04C14/00—Control of, monitoring of, or safety arrangements for, machines, pumps or pumping installations
- F04C14/18—Control of, monitoring of, or safety arrangements for, machines, pumps or pumping installations characterised by varying the volume of the working chamber
- F04C14/22—Control of, monitoring of, or safety arrangements for, machines, pumps or pumping installations characterised by varying the volume of the working chamber by changing the eccentricity between cooperating members
- F04C14/223—Control of, monitoring of, or safety arrangements for, machines, pumps or pumping installations characterised by varying the volume of the working chamber by changing the eccentricity between cooperating members using a movable cam
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
- F04C14/00—Control of, monitoring of, or safety arrangements for, machines, pumps or pumping installations
- F04C14/24—Control of, monitoring of, or safety arrangements for, machines, pumps or pumping installations characterised by using valves controlling pressure or flow rate, e.g. discharge valves or unloading valves
- F04C14/26—Control of, monitoring of, or safety arrangements for, machines, pumps or pumping installations characterised by using valves controlling pressure or flow rate, e.g. discharge valves or unloading valves using bypass channels
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16H—GEARING
- F16H61/00—Control functions within control units of change-speed- or reversing-gearings for conveying rotary motion ; Control of exclusively fluid gearing, friction gearing, gearings with endless flexible members or other particular types of gearing
- F16H61/66—Control functions within control units of change-speed- or reversing-gearings for conveying rotary motion ; Control of exclusively fluid gearing, friction gearing, gearings with endless flexible members or other particular types of gearing specially adapted for continuously variable gearings
- F16H61/662—Control functions within control units of change-speed- or reversing-gearings for conveying rotary motion ; Control of exclusively fluid gearing, friction gearing, gearings with endless flexible members or other particular types of gearing specially adapted for continuously variable gearings with endless flexible members
- F16H61/66272—Control functions within control units of change-speed- or reversing-gearings for conveying rotary motion ; Control of exclusively fluid gearing, friction gearing, gearings with endless flexible members or other particular types of gearing specially adapted for continuously variable gearings with endless flexible members characterised by means for controlling the torque transmitting capability of the gearing
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
- F04C2/00—Rotary-piston machines or pumps
- F04C2/30—Rotary-piston machines or pumps having the characteristics covered by two or more groups F04C2/02, F04C2/08, F04C2/22, F04C2/24 or having the characteristics covered by one of these groups together with some other type of movement between co-operating members
- F04C2/34—Rotary-piston machines or pumps having the characteristics covered by two or more groups F04C2/02, F04C2/08, F04C2/22, F04C2/24 or having the characteristics covered by one of these groups together with some other type of movement between co-operating members having the movement defined in groups F04C2/08 or F04C2/22 and relative reciprocation between the co-operating members
- F04C2/344—Rotary-piston machines or pumps having the characteristics covered by two or more groups F04C2/02, F04C2/08, F04C2/22, F04C2/24 or having the characteristics covered by one of these groups together with some other type of movement between co-operating members having the movement defined in groups F04C2/08 or F04C2/22 and relative reciprocation between the co-operating members with vanes reciprocating with respect to the inner member
- F04C2/3441—Rotary-piston machines or pumps having the characteristics covered by two or more groups F04C2/02, F04C2/08, F04C2/22, F04C2/24 or having the characteristics covered by one of these groups together with some other type of movement between co-operating members having the movement defined in groups F04C2/08 or F04C2/22 and relative reciprocation between the co-operating members with vanes reciprocating with respect to the inner member the inner and outer member being in contact along one line or continuous surface substantially parallel to the axis of rotation
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16H—GEARING
- F16H61/00—Control functions within control units of change-speed- or reversing-gearings for conveying rotary motion ; Control of exclusively fluid gearing, friction gearing, gearings with endless flexible members or other particular types of gearing
- F16H61/0021—Generation or control of line pressure
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16H—GEARING
- F16H61/00—Control functions within control units of change-speed- or reversing-gearings for conveying rotary motion ; Control of exclusively fluid gearing, friction gearing, gearings with endless flexible members or other particular types of gearing
- F16H61/0021—Generation or control of line pressure
- F16H61/0025—Supply of control fluid; Pumps therefore
Definitions
- the invention relates to a system for controlling a hydraulic variable displacement pump for consumers according to the preamble of claim 1.
- variable displacement pump which is designed as a vane pump
- the variable displacement pump is loaded in the direction of the adjustment to high delivery rates via an energy store in the form of a spring, and in the opposite direction via a hydraulic adjusting device, the hydraulic adjusting device being in one of the pressure side Inlet branched off to the consumer, discharging excess production quantities and discharging onto a storage container is connected to the return line.
- Such a control is relatively complex and the desired, as suddenly as possible adjustment of the variable displacement pump in the sense of a sudden increase in the delivery volume or the system pressure depends on the fact that the high-pressure connection of the return line is first deactivated by applying a control pressure to the flow control valve and thereby the control pressure on the control valve is reduced in order to open the connection of the hydraulic actuating device against the storage space running through the control valve and thus to achieve a corresponding adjustment of the pump via the energy store designed as a spring, which, in view of the various actuating elements to be controlled, makes a spontaneous adjustment of the Excludes the control pump as well as the lossy design of the discharge path via the control valve.
- the invention has for its object to provide a simplified control system for a system for controlling a hydraulic servo pump, which a practically sudden application speak in the changeover of the variable pump to higher, in particular maximum, volume flows, and thus possibly also a sudden increase in the system working pressure.
- the volume displaced in each case is used to fill up the spaces created by the changeover, for example based on a piston as an actuator, the volume displaced from the cylinder-side pressure chamber to the rear of the piston is routed, such a short-circuit connection generally enabling particularly short conduction paths and large cross-sections.
- the flow valve is preferably actuated as a function of control parameters specified by the consumer, with other information, for example derived from the driving dynamics, being taken into account in a preventive manner, based on the example of the use of the system according to the invention in vehicles can be, so that in the control of the flow valve, the change in the demand behavior of the demand behavior that may already be expected Consumer can be anticipated for the setting of the variable pump.
- the flow control valve can optionally also be made adjustable, in some cases also provided with an additional control, in particular with regard to the expansion of the basic concept according to the invention to further functions.
- an adjustable throttle can be used as the flow valve in the simplest way, so that the adjustment of the pump, or possibly its adjustment to other positions, can be achieved with simple means within the scope of the invention.
- a design with a control piston working as a pressure balance proves to be expedient, which, on the one hand, is spring-loaded on the high-pressure side and in the opposite direction, controlling the passage cross-section from the high-pressure side to the hydraulic actuating device, with the spring load being superimposed by a pressure which is subordinate to it a measuring throttle lying downstream of the flow control valve corresponds to the pressure in the line connection between the flow control valve and the flow valve via the hydraulic adjusting device.
- the variable displacement pump 1 is illustrated in a highly schematic manner as a vane cell pump with a lifting ring 7, which is adjustable relative to a rotor (not shown) with an axis 8 fixed to the housing in order to change the delivery volume of the variable displacement pump 1.
- An energy storage device 9, formed by a spring arrangement, and on the other hand — illustrated by a cylinder-piston arrangement — a hydraulic actuating device 10 are provided as the adjusting device.
- the lifting ring 7 is adjustable via the spring arrangement forming the energy store 9 in the sense of increasing the delivery volume, and when actuated in the opposite direction, that is against the spring force, via the actuating device 10 in the sense of lowering the delivery volume.
- the hydraulic actuating device 10 is located in the return 27 between the flow control valve 12 and the flow valve 13, which can be changed with regard to its free passage cross section and is formed, for example, by an adjustable throttle.
- the flow control valve 12 is complementary to its symbolic Representation in Fig. 1 in Fig. 2 is shown schematically and comprises a pressure compensator in the form of a control slide 14 which, depending on the position, connects the line section 16 of the return line 27 starting from the pressure side (pressure line 6) with the line section 17, which opens on the pressure side (pressure line 6) the hydraulic actuating device 10 runs out and in which a measuring throttle 18 lies.
- the control slide 14 is pressurized on the end face, namely on its end face 19 on the high-pressure side via the branch 20 to the line section 16, and on its opposite end face 21 via a branch 22 extending downstream of the measuring throttle 18 from the line section 17, an additional one against the end face 21 Compensation spring 23 supports.
- the hydraulic actuating device 10 is illustrated as a piston-cylinder unit, when the piston 28 is supported against the cam ring 7 and the line section 17 opens onto the pressure chamber 29 delimited by the piston 28, which merges into the line section 30 of the return line 27 containing the flow valve 13 , wherein, as illustrated in FIG. 2, this line section 30 is dimensioned in cross-section in relation to the maximum flow rate that occurs so that an almost loss-free and thus unthrottled discharge against the suction side or the storage container 24 is possible.
- the flow valve 13, which is designed as an adjustable throttle is fully open in its passage cross section and is adapted to a discharge cross section maximized in this way.
- a branch line 31 to line 30 opens out to the rear chamber 32 to the piston, so that - schematically illustrated - this occurs each time the adjustment of the pump 1 to a higher flow rate via the energy store 9 displaced volume is used for filling cavities created by the changeover.
- a short-circuit connection can also be implemented inside the variable displacement pump, in particular, which is not shown.
- Such a short-circuit connection not only can pressure differences inhibiting the adjustment be avoided, but remaining residual pressures can even be used to adjust the piston - in addition to the actuating force of the energy store 9.
- Such a short-circuit connection also reduces the cross-sectional requirement for the line 30 leading to the reservoir 24.
- the desired abrupt reduction of the pressure in the pressure chamber 29 is achieved by maximizing the discharge cross-sections including the throttle cross-section when the throttle forming the flow valve 13 is fully open, and this with little effort, with the expediently hard design of the energy store with a constantly high actuating force, for example by using a spring with a high preload and preferably also a high spring rate, slight delays can be associated for the adjustment in the opposite direction, but these have no noticeable disadvantageous effects both in terms of energy and in terms of the function of the system.
- the design of the flow control valve 12 has the result that when the pressure in the line section 17 running out to the actuating device 10 drops, the flow cross-section is reduced from the line section 16 to the line section 17 via the control slide 14, so that when the flow cross-section of the flow valve 13 is widened, initially a rapid pressure reduction in relation to the hydraulic actuating device 10 results. A pressure reduction kung in line section 16 from. If the actuating device 10 is thus relieved of pressure, starting from a corresponding actuation of the flow valve 13 by enlarging the discharge cross-section, then the inflow to the actuating device via the line section 17 is also reduced, albeit briefly, up to the flow control valve 12 working as a pressure compensator the volume flow is adjusted again. A corresponding control effect also results in the case of a demand request via the consumer 2 with a pressure drop in the feed line 3 and a corresponding pressure drop in the line section 16 of the return line 27, so that the response behavior of the system is also positively influenced in this way.
Landscapes
- Engineering & Computer Science (AREA)
- General Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- Physics & Mathematics (AREA)
- Fluid Mechanics (AREA)
- Details And Applications Of Rotary Liquid Pumps (AREA)
- Fluid-Pressure Circuits (AREA)
- Rotary Pumps (AREA)
- Control Of Positive-Displacement Pumps (AREA)
Abstract
Description
Claims
Priority Applications (4)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
JP2003573297A JP2005519223A (ja) | 2002-03-06 | 2003-03-03 | 可変液圧ポンプの制御装置 |
DE50301362T DE50301362D1 (de) | 2002-03-06 | 2003-03-03 | System zur steuerung einer hydraulischen verstellpumpe |
EP03711913A EP1485621B1 (de) | 2002-03-06 | 2003-03-03 | System zur steuerung einer hydraulischen verstellpumpe |
US10/911,166 US20050047930A1 (en) | 2002-03-06 | 2004-08-04 | System for controlling a hydraulic variable-displacement pump |
Applications Claiming Priority (2)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
DE10209880A DE10209880A1 (de) | 2002-03-06 | 2002-03-06 | System zur Steuerung einer hydraulischen Verstellpumpe |
DE10209880.8 | 2002-03-06 |
Related Child Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
US10/911,166 Continuation US20050047930A1 (en) | 2002-03-06 | 2004-08-04 | System for controlling a hydraulic variable-displacement pump |
Publications (1)
Publication Number | Publication Date |
---|---|
WO2003074877A1 true WO2003074877A1 (de) | 2003-09-12 |
Family
ID=27762743
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
PCT/EP2003/002138 WO2003074877A1 (de) | 2002-03-06 | 2003-03-03 | System zur steuerung einer hydraulischen verstellpumpe |
Country Status (6)
Country | Link |
---|---|
US (1) | US20050047930A1 (de) |
EP (1) | EP1485621B1 (de) |
JP (1) | JP2005519223A (de) |
DE (2) | DE10209880A1 (de) |
ES (1) | ES2251680T3 (de) |
WO (1) | WO2003074877A1 (de) |
Cited By (4)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
WO2006018272A1 (de) * | 2004-08-17 | 2006-02-23 | Daimlerchrysler Ag | Einstellvorrichtung, insbesondere für ein kraftfahrzeug |
WO2007036189A1 (de) * | 2005-09-28 | 2007-04-05 | Ixetic Bad Homburg Gmbh | Pumpe |
NL1032577C2 (nl) * | 2006-09-26 | 2008-03-27 | Bosch Gmbh Robert | Continu variabele transmissie met een hydraulisch regelsysteem en werkwijze voor het regelen daarvan. |
WO2009095011A2 (de) * | 2008-01-31 | 2009-08-06 | Dieter Voigt | Druckumschaltung für ölpumpen |
Families Citing this family (30)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
DE60308833T2 (de) * | 2003-05-30 | 2007-03-01 | Robert Bosch Gmbh | Hydraulische Anordnung für Fahrzeuggetriebe |
CA2581120C (en) * | 2004-09-20 | 2013-10-15 | Magna Powertrain Inc. | Speed-related control mechanism for a pump and control method |
DE102005033293A1 (de) | 2005-07-16 | 2007-01-25 | Zf Lenksysteme Gmbh | Verdrängerpumpe mit variablem Fördervolumen |
DE102006058691A1 (de) * | 2006-12-13 | 2008-06-19 | Schaeffler Kg | Einrichtung zur hydraulischen Ansteuerung von Gaswechselventilen einer Hubkolbenbrennkraftmaschine |
US8037678B2 (en) | 2009-09-11 | 2011-10-18 | Sustainx, Inc. | Energy storage and generation systems and methods using coupled cylinder assemblies |
US7958731B2 (en) | 2009-01-20 | 2011-06-14 | Sustainx, Inc. | Systems and methods for combined thermal and compressed gas energy conversion systems |
US20100307156A1 (en) | 2009-06-04 | 2010-12-09 | Bollinger Benjamin R | Systems and Methods for Improving Drivetrain Efficiency for Compressed Gas Energy Storage and Recovery Systems |
US8677744B2 (en) | 2008-04-09 | 2014-03-25 | SustaioX, Inc. | Fluid circulation in energy storage and recovery systems |
WO2009126784A2 (en) | 2008-04-09 | 2009-10-15 | Sustainx, Inc. | Systems and methods for energy storage and recovery using compressed gas |
US8225606B2 (en) | 2008-04-09 | 2012-07-24 | Sustainx, Inc. | Systems and methods for energy storage and recovery using rapid isothermal gas expansion and compression |
US7802426B2 (en) | 2008-06-09 | 2010-09-28 | Sustainx, Inc. | System and method for rapid isothermal gas expansion and compression for energy storage |
US8448433B2 (en) | 2008-04-09 | 2013-05-28 | Sustainx, Inc. | Systems and methods for energy storage and recovery using gas expansion and compression |
US8240140B2 (en) | 2008-04-09 | 2012-08-14 | Sustainx, Inc. | High-efficiency energy-conversion based on fluid expansion and compression |
US8359856B2 (en) | 2008-04-09 | 2013-01-29 | Sustainx Inc. | Systems and methods for efficient pumping of high-pressure fluids for energy storage and recovery |
US8479505B2 (en) | 2008-04-09 | 2013-07-09 | Sustainx, Inc. | Systems and methods for reducing dead volume in compressed-gas energy storage systems |
US8474255B2 (en) | 2008-04-09 | 2013-07-02 | Sustainx, Inc. | Forming liquid sprays in compressed-gas energy storage systems for effective heat exchange |
US8250863B2 (en) | 2008-04-09 | 2012-08-28 | Sustainx, Inc. | Heat exchange with compressed gas in energy-storage systems |
DE102008026308B4 (de) * | 2008-05-31 | 2023-04-20 | Dr. Ing. H.C. F. Porsche Aktiengesellschaft | Schmierstoff-Versorgungssystem |
WO2010105155A2 (en) * | 2009-03-12 | 2010-09-16 | Sustainx, Inc. | Systems and methods for improving drivetrain efficiency for compressed gas energy storage |
US8104274B2 (en) | 2009-06-04 | 2012-01-31 | Sustainx, Inc. | Increased power in compressed-gas energy storage and recovery |
WO2011056855A1 (en) | 2009-11-03 | 2011-05-12 | Sustainx, Inc. | Systems and methods for compressed-gas energy storage using coupled cylinder assemblies |
US8191362B2 (en) | 2010-04-08 | 2012-06-05 | Sustainx, Inc. | Systems and methods for reducing dead volume in compressed-gas energy storage systems |
US8171728B2 (en) | 2010-04-08 | 2012-05-08 | Sustainx, Inc. | High-efficiency liquid heat exchange in compressed-gas energy storage systems |
US8234863B2 (en) | 2010-05-14 | 2012-08-07 | Sustainx, Inc. | Forming liquid sprays in compressed-gas energy storage systems for effective heat exchange |
US8495872B2 (en) | 2010-08-20 | 2013-07-30 | Sustainx, Inc. | Energy storage and recovery utilizing low-pressure thermal conditioning for heat exchange with high-pressure gas |
US8578708B2 (en) | 2010-11-30 | 2013-11-12 | Sustainx, Inc. | Fluid-flow control in energy storage and recovery systems |
WO2012158781A2 (en) | 2011-05-17 | 2012-11-22 | Sustainx, Inc. | Systems and methods for efficient two-phase heat transfer in compressed-air energy storage systems |
US20130091836A1 (en) | 2011-10-14 | 2013-04-18 | Sustainx, Inc. | Dead-volume management in compressed-gas energy storage and recovery systems |
DE112014005946A5 (de) * | 2013-12-18 | 2016-10-06 | Schaeffler Technologies AG & Co. KG | Verstellpumpe |
CN114278530B (zh) * | 2021-12-24 | 2024-03-15 | 浙江利欧环境科技有限公司 | 一种二次供水设备的水泵节能控制方法 |
Citations (3)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
GB913197A (en) * | 1960-05-17 | 1962-12-19 | Thompson Grinder Co | Improvements in hydraulic systems |
DE3214212A1 (de) * | 1982-04-17 | 1983-10-20 | Alfred Teves Gmbh, 6000 Frankfurt | Druckregelvorrichtung fuer pumpen, insbesondere fluegelzellenpumpen |
US4678412A (en) * | 1982-12-23 | 1987-07-07 | Mannesmann Rexroth G.M.B.H. | Adjusting apparatus for a vane pump or radial piston pump |
Family Cites Families (3)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US3856436A (en) * | 1972-12-18 | 1974-12-24 | Sperry Rand Corp | Power transmission |
DE4334167A1 (de) * | 1993-10-07 | 1995-04-13 | Rexroth Mannesmann Gmbh | Hydraulisches System zur Beaufschlagung eines hydraulischen Verbrauchers mit einem geregelten Verbraucherdruck und Drosselventil, insbesondere zur Verwendung in einem solchen hydraulischen System |
DE19722495B4 (de) * | 1996-06-07 | 2005-09-29 | Volkswagen Ag | Pumpe mit verstellbarem Fördervolumen |
-
2002
- 2002-03-06 DE DE10209880A patent/DE10209880A1/de not_active Withdrawn
-
2003
- 2003-03-03 DE DE50301362T patent/DE50301362D1/de not_active Expired - Lifetime
- 2003-03-03 ES ES03711913T patent/ES2251680T3/es not_active Expired - Lifetime
- 2003-03-03 WO PCT/EP2003/002138 patent/WO2003074877A1/de active IP Right Grant
- 2003-03-03 JP JP2003573297A patent/JP2005519223A/ja not_active Withdrawn
- 2003-03-03 EP EP03711913A patent/EP1485621B1/de not_active Expired - Fee Related
-
2004
- 2004-08-04 US US10/911,166 patent/US20050047930A1/en not_active Abandoned
Patent Citations (3)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
GB913197A (en) * | 1960-05-17 | 1962-12-19 | Thompson Grinder Co | Improvements in hydraulic systems |
DE3214212A1 (de) * | 1982-04-17 | 1983-10-20 | Alfred Teves Gmbh, 6000 Frankfurt | Druckregelvorrichtung fuer pumpen, insbesondere fluegelzellenpumpen |
US4678412A (en) * | 1982-12-23 | 1987-07-07 | Mannesmann Rexroth G.M.B.H. | Adjusting apparatus for a vane pump or radial piston pump |
Cited By (7)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
WO2006018272A1 (de) * | 2004-08-17 | 2006-02-23 | Daimlerchrysler Ag | Einstellvorrichtung, insbesondere für ein kraftfahrzeug |
US7444978B2 (en) | 2004-08-17 | 2008-11-04 | Daimler Ag | Adjusting device, in particular for a motor vehicle |
WO2007036189A1 (de) * | 2005-09-28 | 2007-04-05 | Ixetic Bad Homburg Gmbh | Pumpe |
NL1032577C2 (nl) * | 2006-09-26 | 2008-03-27 | Bosch Gmbh Robert | Continu variabele transmissie met een hydraulisch regelsysteem en werkwijze voor het regelen daarvan. |
WO2008037665A1 (en) * | 2006-09-26 | 2008-04-03 | Robert Bosch Gmbh | Continuously variable transmission with a hydraulic control system and method for controlling said transmission |
WO2009095011A2 (de) * | 2008-01-31 | 2009-08-06 | Dieter Voigt | Druckumschaltung für ölpumpen |
WO2009095011A3 (de) * | 2008-01-31 | 2009-12-10 | Dieter Voigt | Druckumschaltung für ölpumpen |
Also Published As
Publication number | Publication date |
---|---|
EP1485621A1 (de) | 2004-12-15 |
ES2251680T3 (es) | 2006-05-01 |
US20050047930A1 (en) | 2005-03-03 |
EP1485621B1 (de) | 2005-10-12 |
DE50301362D1 (de) | 2006-02-23 |
DE10209880A1 (de) | 2003-09-18 |
JP2005519223A (ja) | 2005-06-30 |
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