EP1283366A2 - Pompe à pistons radiaux et méthode de contròle - Google Patents

Pompe à pistons radiaux et méthode de contròle Download PDF

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Publication number
EP1283366A2
EP1283366A2 EP02015316A EP02015316A EP1283366A2 EP 1283366 A2 EP1283366 A2 EP 1283366A2 EP 02015316 A EP02015316 A EP 02015316A EP 02015316 A EP02015316 A EP 02015316A EP 1283366 A2 EP1283366 A2 EP 1283366A2
Authority
EP
European Patent Office
Prior art keywords
drive shaft
adjusting
ring
piston pump
radial piston
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
EP02015316A
Other languages
German (de)
English (en)
Other versions
EP1283366B1 (fr
EP1283366A3 (fr
Inventor
Hans-Peter Stiefel
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 EP1283366A2 publication Critical patent/EP1283366A2/fr
Publication of EP1283366A3 publication Critical patent/EP1283366A3/fr
Application granted granted Critical
Publication of EP1283366B1 publication Critical patent/EP1283366B1/fr
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B1/00—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders
    • F04B1/04—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders having cylinders in star- or fan-arrangement
    • F04B1/0404—Details or component parts
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B49/00—Control, e.g. of pump delivery, or pump pressure of, or safety measures for, machines, pumps, or pumping installations, not otherwise provided for, or of interest apart from, groups F04B1/00 - F04B47/00
    • F04B49/12—Control, e.g. of pump delivery, or pump pressure of, or safety measures for, machines, pumps, or pumping installations, not otherwise provided for, or of interest apart from, groups F04B1/00 - F04B47/00 by varying the length of stroke of the working members
    • F04B49/123—Control, e.g. of pump delivery, or pump pressure of, or safety measures for, machines, pumps, or pumping installations, not otherwise provided for, or of interest apart from, groups F04B1/00 - F04B47/00 by varying the length of stroke of the working members by changing the eccentricity of one element relative to another element
    • F04B49/125—Control, e.g. of pump delivery, or pump pressure of, or safety measures for, machines, pumps, or pumping installations, not otherwise provided for, or of interest apart from, groups F04B1/00 - F04B47/00 by varying the length of stroke of the working members by changing the eccentricity of one element relative to another element by changing the eccentricity of the actuation means, e.g. cams or cranks, relative to the driving means, e.g. driving shafts
    • F04B49/126—Control, e.g. of pump delivery, or pump pressure of, or safety measures for, machines, pumps, or pumping installations, not otherwise provided for, or of interest apart from, groups F04B1/00 - F04B47/00 by varying the length of stroke of the working members by changing the eccentricity of one element relative to another element by changing the eccentricity of the actuation means, e.g. cams or cranks, relative to the driving means, e.g. driving shafts with a double eccenter mechanism
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B1/00—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders
    • F04B1/04—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders having cylinders in star- or fan-arrangement
    • F04B1/06—Control
    • F04B1/07—Control by varying the relative eccentricity between two members, e.g. a cam and a drive shaft

Definitions

  • the invention first relates to a radial piston pump for High-pressure fuel generation in fuel systems from Internal combustion engines, especially in a common rail injection system, with a housing with at least one Cylinder, with a drive shaft in the housing is stored and at least one eccentric section has, with a cam ring, which around the Eccentric section is arranged around and with at least a piston which is received in the cylinder and is supported on the cam ring.
  • Such a radial piston pump is known from DE 198 58 862 A1 known. With her, three cylinders are star-shaped around one Eccentric section of a centrally arranged drive shaft arranged. There is a cam ring on the eccentric section placed with the radially inner ends of the in the Cylinder piston is connected. The cam ring itself does not rotate, but moves in its Level along a circular path. This way, in the Cylinders picked up pistons alternately in a back and forth Moved here.
  • Such a radial piston pump is called a high pressure fuel pump used in a fuel system. you fuel is fed from a pre-feed pump and it feeds the fuel further into a fuel manifold, commonly referred to as "rail". Of there the fuel reaches the combustion chambers via injectors the internal combustion engine.
  • the present invention has the task of a Radial piston pump of the type mentioned educate that the fuel system in which they is used, manufactured easier and cheaper can be.
  • This task is the beginning of a radial piston pump mentioned kind in that between Eccentric section and cam ring arranged an adjusting ring is, the inner opening opposite the outer contour is eccentric and which is about the central axis of the Opposite inner opening in a desired angular position the eccentric section can be rotated.
  • Radial piston pump is that for controlling it the amount of fuel delivered no pressure and / or Volume control valves are required more. Instead the quantity is controlled by adjusting the stroke the piston or pistons of the radial piston pump.
  • the radial piston pump according to the invention is therefore simpler to build.
  • the amount of fuel delivered by the radial piston pump can be set very precisely, can be done on the Fuel line existing pressure relief valve and the corresponding return line turn out smaller, or it can possibly even completely on such a pressure relief valve to be dispensed with. Also for example to the fuel tank returning leakage line is when using the Radial piston pump according to the invention no longer required. By the radial piston pump according to the invention thus become costs when building a fuel system saved and the fuel system builds overall easier, because it has fewer components.
  • the Radial piston pump according to the invention includes an adjustment shaft, which has a Gearing works together with the adjusting ring.
  • a such adjustment shaft is space-saving in the To accommodate radial piston pump and enables a reliable and precise adjustment of the adjustment ring.
  • the adjusting shaft arranged coaxially to the axis of rotation of the drive shaft and on an end face of the eccentric section of the drive shaft, eccentric to the axis of rotation of the drive shaft a gear is stored, which on the one hand with external teeth on the adjusting shaft and on the other hand with a Internal toothing on the adjusting ring works together.
  • An adjusting device for the adjusting ring becomes created, which on the one hand builds small and on the other hand due to the between the adjusting shaft and the Adjustment ring arranged gear a cheap Translation, possibly also a self-locking between Adjustment ring and adjustment shaft enables.
  • Adjustment ring there is a stop, which is a such angular position of the adjusting ring relative to the Drive shaft defined in which the cam ring at least is approximately coaxial with the axis of rotation of the drive shaft.
  • the radial piston pump works with Zero discharge.
  • the stop becomes this operating point the radial piston pump defined in a simple manner.
  • the stop can be formed by the Internal teeth on the adjusting ring in the circumferential direction in one Range of approximately 185 ° to 195 °, preferably over one Range of approximately 190 °, and the Internal toothing opposite an axis, which is in the plane of the adjustment ring lies through the center of the Inner opening of the adjustment ring goes and orthogonal to Axis of symmetry of the adjusting ring is symmetrical.
  • the So stop is only through the arrangement and training the internal toothing formed on the adjusting ring, so that on an additional stop element can be dispensed with.
  • An electrical adjustment device is preferred provided, which works on the adjusting shaft.
  • a such a device can be easily controlled.
  • the electrical adjustment device can be an electric motor, preferably a stepper motor.
  • the corresponding supply lines are possible to save space.
  • a electrical adjustment device, in particular a Stepper motor also work very precisely and build relatively small. In principle, it is also conceivable the use of an electromagnetic or a hydraulic actuator.
  • the stator of the Electric motor with the drive shaft and the rotor of the Electric motor rotatably connected to the adjusting shaft are.
  • the drive shaft, the adjusting shaft rotate and correspondingly the stator and the rotor of the electric motor synchronous. Only if the adjustment ring is adjusted can be required by the arrangement according to the invention in a simple way a speed difference between the drive shaft and the adjusting shaft are generated, which leads to the adjustment of the adjustment ring.
  • the invention also relates to a method for operating an internal combustion engine in which the fuel is at least is also promoted by a radial piston pump, with a Housing with at least one cylinder, one drive shaft, which is stored in the housing and at least one Has eccentric section, with a cam ring, which around the eccentric section is arranged around and with at least one piston which is in the cylinder is recorded and is supported on the cam ring.
  • Radial piston pump delivered fuel amount very much quickly to a changed operating state of the Internal combustion engine to be adjusted. This will essentially allows only that amount of fuel is promoted to the fuel rail, which of the Injectors finally passed into the combustion chambers becomes. Excess the usual return Fuel from the fuel rail can thus omitted or the components required for this can at least turn out smaller.
  • the amount of fuel to be delivered is the desired torque and the instantaneous speed of the internal combustion engine. This is the case with that further development of the invention Process taken into account in which a desired Torque and a speed of the internal combustion engine Parameter is determined which for setting a such eccentricity of the cam ring with respect to the axis of rotation the drive shaft is required, in which the Radial piston pump that the torque request and the speed appropriate amount of fuel promotes.
  • the invention further relates to a computer program which is suitable for performing the above method if it is running on a computer. It becomes special preferred if the computer program is on a memory, is stored in particular on a flash memory.
  • the present invention also relates to a control and / or Control device for control and / or regulation at least one function of an internal combustion engine. at such a control and / or regulating device suggested that it work with a computer program above type is provided.
  • a fuel system has the reference number 10 in FIG. 1.
  • a fuel tank 12 from which one electric fuel pump 14 via a filter 16 Fuel promotes. Via a low pressure fuel line 18 is the electric fuel pump 14 with a High pressure fuel pump 20 connected. Between electric fuel pump 14 and high pressure pump 20 branches off from the low pressure fuel line 18 Branch line 22 in which a pressure control valve 24 is arranged.
  • the high pressure fuel pump 20 pumps the fuel in a fuel manifold 26. In this is the Fuel stored under very high pressure. To the Fuel rail 26 is a plurality of injectors 28 connected, the fuel directly into combustion chambers 30 inject.
  • the High-pressure fuel pump 20 for the fuel rail 26 delivered fuel quantity can be changed.
  • the high pressure fuel pump 20 includes an electric motor 32, which of a control and / or regulating device 34th is controlled. This is on the input side with a Sensor 36, which taps the speed of the internal combustion engine and a sensor 38, which is a target torque Internal combustion engine delivers corresponding signals, connected.
  • the High-pressure fuel pump 20 is a Radial piston pump with three arranged in a star shape Cylinders 40a, 40b and 40c ( Figure 3). Cylinder heads 42a, 42b and 42c close the cylinders 40a, 40b and 40c radially outside. In the cylinder heads 42a, 42b and 42c contain bushings 44a, 44b and 44c in which Pistons 46a, 46b and 46c are slidably received.
  • the cylinders 40a, 40b and 40c are part of a housing 48.
  • a drive shaft 50 In the center between the cylinders 40a, 40b and 40c is in Housing 48 received a drive shaft 50. Over a Coupling 52 is this with a camshaft (not shown) connected to the internal combustion engine. That in figure 2 left end of the drive shaft 50 is opposite the housing 48 supported by a ball bearing 53.
  • the drive shaft 50 has in the region of the cylinders 40a, 40b and 40c an eccentric section 54. This is with respect to the axis of rotation 56 of the drive shaft 50 by one Eccentricity 58 replaced ( Figure 5). Radial outside is open the eccentric portion 54 of the drive shaft 50 Adjustment ring 60 put on. Radially outside is on the Adjustment ring 60 in turn a lifting ring 62 placed. The The cam ring 62 bears one around its cam ring bore 63 radially inner extending circumferential collar 65th By this is the cam ring 62 between the adjusting ring 60 and a shaft collar 67 present on the drive shaft 50 held axially.
  • the outer lateral surface of the cam ring 62 has three 120 ° offset flattened areas 64a, 64b and 64c on.
  • a sliding shoe 66a, 66b or 66c is against this by a spring 68a, 68b or 68c, which is located on the Bushing 44a, 44b and 44c supported, pressed.
  • the Slide shoe 66a, 66b and 66c is with the radially inner End of the piston 46a, 46b and 46c connected.
  • the drive shaft 50 is in its right in Figure 2 Hollow area. In this recess is one Adjustment shaft 70 introduced. On her left in Figure 2 At the end, the adjusting shaft 70 has circumferential teeth 72nd
  • the central axis 81 of the inner opening 80 is opposite that circular outer contour of the adjusting ring 60 by a Eccentricity 82 arranged offset ( Figure 5).
  • On one Area of the inner lateral surface of the inner opening 80 of the Adjustment ring 60 has an internal toothing 84.
  • the Gear 76 is also with this internal toothing 84 in Intervention.
  • the internal toothing 84 on the adjusting ring 60 extends in the circumferential direction over a range of about 190 °.
  • the internal toothing 84 is opposite an axis 86 which is in the plane of the adjusting ring 60 lies through the center 81 of the inner opening of the Adjustment ring goes and orthogonal to the axis of symmetry 88 des Adjustment ring 60 is symmetrical ( Figure 5). How to continue set out below, formed the ends of the Internal toothing stops, one of which is shown in FIGS. 4 and 5 bears reference number 89.
  • a shaft journal 90 to the right in FIG. 2 a bearing bush 92 is pressed on.
  • the associated one Bearing ring 94 is pressed with the housing 48.
  • the Bearing bush 92 and the bearing ring 94 together form one Slide bearing, over which the right end in Figure 2 supports the drive shaft 50 relative to the housing 48.
  • the adjusting shaft 70 is also the axis of the Electric motor 32. To this extent, a rotor 102 of the Electric motor 32 at the right end in FIG Adjustment shaft 70 fixed in rotation. A stator 104 of the Electric motor 32 surrounds rotor 102. Stator 104 is via a disk-shaped holding plate 106 rotatably with the Bearing bush 92 connected. The disc-shaped holding plate 106 can be injection molded onto the bearing bush 92, for example. On in this way, the stator 104 is rotationally fixed to the Drive shaft 50 connected. The stator 104 is one of Cover hood 108, the edge of which in the housing 48th is crimped pressure-tight. In the cover 108 are Plug contacts 110 inserted, which via sliding contacts Power the stator 104 (without reference numerals) can.
  • the fuel system 10 with the radial piston pump 20 works as follows: Before starting the Internal combustion engine, for example when the ignition is actuated the electric motor 32 from the control and / or regulating device 34 so controlled that the gear 76 against the stop 89 of the Internal toothing 84 on the adjusting ring 60 runs.
  • the adjustment ring 60 is adjusted by a relative rotation of the rotor 102 with respect to the stator 104. This also rotates the adjusting shaft 70 and that Gear 76. This in turn leads to a relative rotation of the Adjustment ring 60 with respect to the eccentric section 54 Drive shaft 50.
  • every angular position of the adjusting ring 60 with respect to the eccentric section 54 of the drive shaft 50 a very specific delivery rate of the high pressure fuel pump 20 corresponds. These are angular positions with the associated delivery rates in the control unit 34 saved.
  • the ones that correspond to the user's request Performance of the internal combustion engine, in particular torque and speed, are from the control unit 34 in the required fuel quantity and the corresponding Angular position of the adjusting ring 60 relative to that Eccentric section 54 of the drive shaft 50 converted and the electric motor 32 is controlled accordingly.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Reciprocating Pumps (AREA)
  • Fuel-Injection Apparatus (AREA)
  • Electrical Control Of Air Or Fuel Supplied To Internal-Combustion Engine (AREA)
EP02015316A 2001-08-10 2002-07-10 Pompe à pistons radiaux et méthode de contròle Expired - Lifetime EP1283366B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE10139519 2001-08-10
DE10139519A DE10139519A1 (de) 2001-08-10 2001-08-10 Radialkolbenpumpe zur Kraftstoffhochdruckerzeugung, sowie Verfahren zum Betreiben einer Brennkraftmaschine, Computerprogramm und Steuer- und/oder Regelgerät

Publications (3)

Publication Number Publication Date
EP1283366A2 true EP1283366A2 (fr) 2003-02-12
EP1283366A3 EP1283366A3 (fr) 2004-05-12
EP1283366B1 EP1283366B1 (fr) 2005-11-09

Family

ID=7695149

Family Applications (1)

Application Number Title Priority Date Filing Date
EP02015316A Expired - Lifetime EP1283366B1 (fr) 2001-08-10 2002-07-10 Pompe à pistons radiaux et méthode de contròle

Country Status (4)

Country Link
US (1) US6872056B2 (fr)
EP (1) EP1283366B1 (fr)
JP (1) JP2003097383A (fr)
DE (2) DE10139519A1 (fr)

Cited By (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102006000832A1 (de) * 2006-01-05 2007-07-12 Siemens Ag Radialkolbenpumpe mit Fördermengenregelung
EP2093421A1 (fr) * 2008-02-22 2009-08-26 Robert Bosch GmbH Pompe haute pression pour fournir du carburant à un système d'injection de carburant
WO2010094367A1 (fr) * 2009-02-18 2010-08-26 Robert Bosch Gmbh Pompe d'alimentation haute pression pour moteur à combustion interne
CN105179218A (zh) * 2015-10-12 2015-12-23 杭州电子科技大学 一种数字式径向柱塞变量泵

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DE10349310B3 (de) * 2003-10-23 2005-05-19 Siemens Ag Radialkolbenpumpe für Common Rail Einspritzsysteme
JP4297859B2 (ja) * 2004-09-28 2009-07-15 三洋電機株式会社 電動車輪用ハブユニット及び該ハブユニットを具えた乗物
DE102005061456B4 (de) * 2005-12-22 2015-09-24 Magna Powertrain Bad Homburg GmbH Zylinderblock einer Hubkolbenmaschine mit durch Spannring gehaltenen Zylinderköpfen
DE102006006823B3 (de) * 2006-02-14 2007-03-15 Siemens Ag Verfahren und Vorrichtung zum Einspritzen von Kraftstoff
JP4624961B2 (ja) * 2006-06-13 2011-02-02 株式会社ニッキ 燃料供給システム
US8122811B2 (en) * 2007-11-12 2012-02-28 Denso Corporation Fuel injection pump and method for assembling the same
EP2464867B1 (fr) * 2009-08-11 2014-09-03 ProMinent GmbH Dispositif d'entrainement pour une machine de refoulement oscillante
DE102009049354A1 (de) * 2009-10-14 2011-04-21 Robert Bosch Gmbh Hydromaschine
US9618129B2 (en) * 2010-10-07 2017-04-11 Vanderbilt University Normally closed microvalve and applications of the same
WO2013010458A1 (fr) * 2011-07-14 2013-01-24 Neo Mechanics Limited Pompe d'injection de carburant de moteur diesel dont les pistons sont étanchéifiés à l'aide de bagues d'étanchéité entièrement métalliques
DE102015214837A1 (de) * 2015-08-04 2017-02-09 Zf Friedrichshafen Ag Hydraulische Radialkolbenmaschine
JP6305480B2 (ja) * 2016-09-01 2018-04-04 日機装株式会社 無脈動ポンプ
US11624326B2 (en) 2017-05-21 2023-04-11 Bj Energy Solutions, Llc Methods and systems for supplying fuel to gas turbine engines
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Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB608234A (en) * 1944-07-03 1948-09-13 Olaer Marine Improvements in pumps, motors, compressors and analogous machines
US2900839A (en) * 1954-01-26 1959-08-25 Donald D R Mackintosh Variable throw radial pump
US5944493A (en) * 1990-06-29 1999-08-31 Whitemoss, Inc. Radial piston fluid machine and/or adjustable rotor
EP1111234A2 (fr) * 1999-12-20 2001-06-27 Hydraulik-Ring GmbH Pompe à carburant

Family Cites Families (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3682572A (en) * 1970-07-27 1972-08-08 Donald L Yarger Piston type pump
JPH03111673A (ja) * 1989-09-26 1991-05-13 Zexel Corp 固定シリンダ型可変容量ラジアルピストンポンプ
JPH07180650A (ja) * 1993-12-24 1995-07-18 Zexel Corp ラジアルピストンポンプ
DE19523282A1 (de) 1995-06-27 1997-01-02 Bosch Gmbh Robert Kolbenpumpe
DE19705205A1 (de) 1997-02-12 1998-08-13 Bosch Gmbh Robert Kolbenpumpe
US6016791A (en) * 1997-06-04 2000-01-25 Detroit Diesel Corporation Method and system for controlling fuel pressure in a common rail fuel injection system
DE19858862A1 (de) 1998-12-19 2000-03-02 Bosch Gmbh Robert Radialkolbenpumpe
DE19956092A1 (de) * 1999-11-22 2000-10-26 Siemens Ag Kolbenpumpe, insbesondere Hochdruck-Radialkolbenpumpe

Patent Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB608234A (en) * 1944-07-03 1948-09-13 Olaer Marine Improvements in pumps, motors, compressors and analogous machines
US2900839A (en) * 1954-01-26 1959-08-25 Donald D R Mackintosh Variable throw radial pump
US5944493A (en) * 1990-06-29 1999-08-31 Whitemoss, Inc. Radial piston fluid machine and/or adjustable rotor
EP1111234A2 (fr) * 1999-12-20 2001-06-27 Hydraulik-Ring GmbH Pompe à carburant

Cited By (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102006000832A1 (de) * 2006-01-05 2007-07-12 Siemens Ag Radialkolbenpumpe mit Fördermengenregelung
DE102006000832B4 (de) * 2006-01-05 2011-12-01 Continental Automotive Gmbh Radialkolbenpumpe mit Fördermengenregelung
EP2093421A1 (fr) * 2008-02-22 2009-08-26 Robert Bosch GmbH Pompe haute pression pour fournir du carburant à un système d'injection de carburant
WO2010094367A1 (fr) * 2009-02-18 2010-08-26 Robert Bosch Gmbh Pompe d'alimentation haute pression pour moteur à combustion interne
CN102325994A (zh) * 2009-02-18 2012-01-18 罗伯特·博世有限公司 用于内燃机的高压燃料泵
CN102325994B (zh) * 2009-02-18 2015-10-21 罗伯特·博世有限公司 用于内燃机的高压燃料泵
CN105179218A (zh) * 2015-10-12 2015-12-23 杭州电子科技大学 一种数字式径向柱塞变量泵
CN105179218B (zh) * 2015-10-12 2016-11-30 杭州电子科技大学 一种数字式径向柱塞变量泵

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EP1283366B1 (fr) 2005-11-09
DE50204834D1 (de) 2005-12-15
DE10139519A1 (de) 2003-02-27
US20030031568A1 (en) 2003-02-13
US6872056B2 (en) 2005-03-29
JP2003097383A (ja) 2003-04-03
EP1283366A3 (fr) 2004-05-12

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