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WO2003048564A1 - Pompe a piston radiaux a graissage force - Google Patents

Pompe a piston radiaux a graissage force Download PDF

Info

Publication number
WO2003048564A1
WO2003048564A1 PCT/DE2002/002879 DE0202879W WO03048564A1 WO 2003048564 A1 WO2003048564 A1 WO 2003048564A1 DE 0202879 W DE0202879 W DE 0202879W WO 03048564 A1 WO03048564 A1 WO 03048564A1
Authority
WO
WIPO (PCT)
Prior art keywords
radial piston
piston pump
pump according
fuel
slide bearing
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.)
Ceased
Application number
PCT/DE2002/002879
Other languages
German (de)
English (en)
Inventor
Heinz Siegel
Helmut Rembold
Hans-Peter Stiefel
Karl Gmelin
Thomas Fuerst
Thilo Bolz
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
Priority claimed from DE10208574A external-priority patent/DE10208574A1/de
Application filed by Robert Bosch GmbH filed Critical Robert Bosch GmbH
Priority to EP02764536A priority Critical patent/EP1454055B1/fr
Priority to AT02764536T priority patent/ATE308676T1/de
Priority to DE50204804T priority patent/DE50204804D1/de
Publication of WO2003048564A1 publication Critical patent/WO2003048564A1/fr
Anticipated expiration legal-status Critical
Ceased legal-status Critical Current

Links

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
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M59/00—Pumps specially adapted for fuel-injection and not provided for in groups F02M39/00 -F02M57/00, e.g. rotary cylinder-block type of pumps
    • F02M59/02—Pumps specially adapted for fuel-injection and not provided for in groups F02M39/00 -F02M57/00, e.g. rotary cylinder-block type of pumps of reciprocating-piston or reciprocating-cylinder type
    • F02M59/10—Pumps specially adapted for fuel-injection and not provided for in groups F02M39/00 -F02M57/00, e.g. rotary cylinder-block type of pumps of reciprocating-piston or reciprocating-cylinder type characterised by the piston-drive
    • F02M59/102—Mechanical drive, e.g. tappets or cams
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M59/00—Pumps specially adapted for fuel-injection and not provided for in groups F02M39/00 -F02M57/00, e.g. rotary cylinder-block type of pumps
    • F02M59/44—Details, components parts, or accessories not provided for in, or of interest apart from, the apparatus of groups F02M59/02 - F02M59/42; Pumps having transducers, e.g. to measure displacement of pump rack or piston
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M59/00—Pumps specially adapted for fuel-injection and not provided for in groups F02M39/00 -F02M57/00, e.g. rotary cylinder-block type of pumps
    • F02M59/02—Pumps specially adapted for fuel-injection and not provided for in groups F02M39/00 -F02M57/00, e.g. rotary cylinder-block type of pumps of reciprocating-piston or reciprocating-cylinder type
    • F02M59/04—Pumps specially adapted for fuel-injection and not provided for in groups F02M39/00 -F02M57/00, e.g. rotary cylinder-block type of pumps of reciprocating-piston or reciprocating-cylinder type characterised by special arrangement of cylinders with respect to piston-driving shaft, e.g. arranged parallel to that shaft or swash-plate type pumps
    • F02M59/06—Pumps specially adapted for fuel-injection and not provided for in groups F02M39/00 -F02M57/00, e.g. rotary cylinder-block type of pumps of reciprocating-piston or reciprocating-cylinder type characterised by special arrangement of cylinders with respect to piston-driving shaft, e.g. arranged parallel to that shaft or swash-plate type pumps with cylinders arranged radially to driving shaft, e.g. in V or star arrangement
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M63/00—Other fuel-injection apparatus having pertinent characteristics not provided for in groups F02M39/00 - F02M57/00 or F02M67/00; Details, component parts, or accessories of fuel-injection apparatus, not provided for in, or of interest apart from, the apparatus of groups F02M39/00 - F02M61/00 or F02M67/00; Combination of fuel pump with other devices, e.g. lubricating oil pump
    • F02M63/02—Fuel-injection apparatus having several injectors fed by a common pumping element, or having several pumping elements feeding a common injector; Fuel-injection apparatus having provisions for cutting-out pumps, pumping elements, or injectors; Fuel-injection apparatus having provisions for variably interconnecting pumping elements and injectors alternatively
    • F02M63/0225—Fuel-injection apparatus having a common rail feeding several injectors ; Means for varying pressure in common rails; Pumps feeding common rails

Definitions

  • the invention relates to a radial piston pump for generating high fuel pressure for a
  • Fuel injection system of internal combustion engines with a drive shaft, the drive shaft having an eccentric section and a stub shaft supported in a pump housing by a first slide bearing, preferably several with respect to the
  • Such an internally supported radial piston pump is known, for example, from DE 197 05 205 AI.
  • the mounting of the drive shaft in the pump housing and the mounting of the ring on the eccentric section of the drive shaft are subject to greater stress as the delivery volume and delivery head of the pump elements increase.
  • the radial piston pump is to be used to deliver fuels with poor lubrication properties, such as gasoline, the mounting of the stub shaft in the pump housing and the mounting of the ring on the eccentric section of the drive shaft are a limiting factor for the delivery rate and the delivery head - 1
  • the object of the invention is to further develop a known radial piston pump in such a way that it can be used for larger delivery quantities and greater delivery heights without profound changes.
  • a radial piston pump for high-pressure fuel generation for a fuel injection system of internal combustion engines with a drive shaft, the drive shaft having an eccentric section and a stub shaft supported in a pump housing by a first slide bearing, preferably with a plurality of pump elements arranged radially with respect to the drive shaft, with one between the eccentric section and the pump elements arranged ring, and with a fuel connection in the pump housing, solved in that the first sliding bearing is forcibly flowed through by the fuel flowing through the fuel connection.
  • the fuel flowing into the fuel connection of the radial piston pump has a pressure, which is provided by a prefeed pump, of about 4-6 bar. This pressure is independent of the speed and the
  • the first slide bearing is designed as a hydrostatic slide bearing. This creates a lubricating film with great reliability, so that the risk of "eaters" is significantly reduced.
  • the load capacity of the first plain bearing also increases. This measure can be implemented by slight modifications of the first slide bearing on a known radial piston pump, so that the existing production facilities for manufacturing the radial piston pump can be taken over almost unchanged.
  • the ring is supported on the eccentric section by a second slide bearing, and that the fuel flowing through the fuel connection forcibly flows through the second slide bearing, so that the load-bearing capacity of the second slide bearing is simple and effective Way is increased in all operating states and speeds of the high-pressure fuel pump.
  • a particularly economical embodiment of the invention provides that the first slide bearing has at least one lubrication groove running essentially in the direction of the axis of rotation of the drive shaft, so that the fuel flowing out of the fuel connection into the first slide bearing is ' evenly distributed over the entire bearing surface and thus the uniform formation of a lubricating film is favored.
  • the stub shaft has a central bore, that a transverse bore branches off from the central bore, and that the second slide bearing is supplied with fuel by the transverse bore.
  • the fuel for lubrication of the second slide bearing can be introduced into the center of the bearing surface of the second slide bearing and flow from there to the edges of the slide bearing. This favors the formation of a stable lubricating film between the ring and the eccentric section of the drive shaft.
  • the second slide bearing has at least one lubrication groove running essentially in the direction of the axis of rotation of the drive shaft.
  • the eccentric section or the ring has an annular groove, and that the transverse bore opens into the annular groove, so that the fuel is distributed uniformly over the entire circumference of the second slide bearing.
  • an impeller of a micropump can be inserted into the center bore, so that an additional pressure increase takes place depending on the speed of the radial piston pump, thus further increasing the load-bearing capacity of the second slide bearing at high speeds.
  • Alternative embodiments of the invention provide that the fuel connection opens into the interior of the housing or directly into the first slide bearing.
  • the design of the first and second plain bearings according to the invention can be used equally advantageously in different types of radial piston pumps.
  • Further advantageous refinements of the inventions provide that the lubrication groove is arranged on the stub shaft of the drive shaft, that the lubrication groove is arranged on the bushing of the first slide bearing, that the lubrication groove is arranged on the eccentric section of the drive shaft and / or that the lubrication groove on one Bushing of the second plain bearing is arranged so that the load capacity and life of the first and second plain bearings increase further.
  • lubrication groove on the stub shaft and / or the lubrication groove on the eccentric section are arranged offset by approximately 180 ° to the resulting force vector.
  • the formation of a stable lubricating film can be further promoted if the lubricating groove on the shaft end and / or the lubricating groove on the eccentric section are designed to be spiral.
  • Figure 1 is a representation of a first embodiment of an inventive
  • Figure 2 shows a second embodiment of a radial piston pump according to the invention in cross section. Description of the embodiments
  • a first embodiment of a radial piston pump according to the invention is shown in cross section.
  • the radial piston pump consists of a pump housing 1.
  • a drive shaft 3 is rotatably mounted in the pump housing 1.
  • the drive shaft 3 is supported with a stub shaft 5 in a first slide bearing 7 in the pump housing 1. With its end opposite the shaft end 5, the drive shaft 3 is supported in a cover 9 by means of a ball bearing 11.
  • the drive shaft 3 has an eccentric section 13.
  • the eccentric section 13 is surrounded by a ring 15 which, in a view from the front (not shown), has a polygonal outer contour 19.
  • the ring 15 does not rotate when the drive shaft 3 is rotated, but performs a circular movement.
  • a second slide bearing 17 is present, which is pressed with the ring 15. With its polygonal outer contour 19, the ring 15 transmits the circular movement impressed on it by the eccentric section 13 to a piston foot plate 21 of a pump element 23.
  • the pump element 23 has a cylinder bore 25 and a piston 27.
  • the piston 27 is set into an oscillating movement via the piston foot plate 21.
  • fuel is drawn from a fuel connection (not shown) into a working space 29 and then pressurized during the so-called delivery stroke.
  • the fuel which is under high pressure, is fed through a high-pressure outlet (not shown) pushed out of the work space 29.
  • the high-pressure fuel pump is supplied via a fuel connection 31, which opens into the first slide bearing 7.
  • the fuel in the fuel connection 31 is pressed into the first slide bearing 7 by a prefeed pump, not shown, with a delivery pressure of approximately 4-6 bar. This results in a very stable formation of a lubricating film between the pump housing 1 and the shaft end 5, which significantly increases the load-bearing capacity and service life of the first plain bearing 7.
  • a plurality of lubrication grooves 33 are arranged distributed over the circumference of the first slide bearing 7.
  • the lubrication grooves 33 can also be designed helically.
  • the first slide bearing 7 consists of a bush 37 pressed into the housing 1 with a pressed bush
  • the lubrication grooves 33 can be incorporated either in the inner ring 36 or in the stub shaft 5. When the lubrication grooves 33 are machined into the stub shaft 5, the rotary movement of the stub shaft can be used to deliver fuel into the first slide bearing 7. This further increases the load capacity of the first plain bearing 7.
  • Fig. 2 is a second embodiment of an inventive radial piston pump in cross section shown :. Same components will be mine. provided with the same reference number and what has been said regarding FIG. 1 applies accordingly.
  • the ball bearing 11 is inserted into the pump housing 1.
  • the fuel connection 31 opens into the interior 35. From there, the fuel flows via lubrication grooves 33 through the first slide bearing 7 to the end of the stub shaft 5. From the cross-sectional illustration of FIG. 2 it can be seen that a bushing 37 is pressed into the housing 1, in which the lubrication grooves 33 are incorporated. The bush 37 forms, together with the stub shaft 5, the first slide bearing 7.
  • the stub shaft 5 has a central bore 39, which is penetrated by a transverse bore 41.
  • the transverse bore 41 in turn opens into an annular groove 43 which is incorporated in the eccentric section 13 of the drive shaft 3.
  • the annular groove 43 can also be worked into the ring 15. This alternative is not shown in Fig. 2.
  • the fuel passes from the end of the stub shaft 5 to the second slide bearing 17, which is formed by the eccentric section 13 and the ring 15.
  • In the eccentric ring 15 are lubrication grooves
  • the lubrication grooves 45 establish a hydraulic connection between the ring groove 43 and the interior 35 on the side of the ring 15 facing away from the shaft end 5.
  • the lubrication grooves 45 end in the ring 15, so that on this side of the ring 15 only very little fuel passes through the gap (not visible in FIG. 2) between the ring 15 and the eccentric section 13 in FIG Interior 35 occur can. This measure ensures that "fresh" fuel always flows out of the interior 35 through the first slide bearing 7 and that a short-circuit flow cannot occur between the second slide bearing 17 and the first slide bearing 7.
  • An impeller 49 of a micropump is pressed into the center bore 39 at the end of the stub shaft. This impeller rotates with the drive shaft 3 and generates a fuel flow, fuel being sucked in through the first slide bearing 7 and then flowing through the second slide bearing 17 due to the pressure increase of the micropump. The fuel passes through the annular groove 43 into the second slide bearing 17, the pressure increase by the micropump depending on the speed of the
  • a third embodiment of a radial piston pump according to the invention is shown in cross section.
  • the same components are provided with the same reference numerals and what has been said regarding FIGS. 1 and 2 applies accordingly.
  • a coiled lubrication groove 33 is present in the stub shaft 5.
  • fuel is conveyed into the first slide bearing 7 by the rotation of the drive shaft 3, which increases its resilience and service life.
  • a helical lubrication groove 45 is present. The lubrication groove 45 improves the supply of fuel to the second slide bearing 17 and thereby increases its load capacity and service life.
  • Fig. 4 the third embodiment shown in Fig. 3 is shown schematically in a side view.
  • the optimal arrangement of the coiled or straight lubrication grooves 37 and 45 will be explained.
  • three pump elements 23-1, 23-11 and 23-111 which are arranged offset by 120 ° to one another are schematically represented by their longitudinal axes, which are actuated via the eccentric section 13 of the drive shaft.
  • the direction of rotation of the drive shaft is shown by a first arrow 53.
  • the direction of the resulting force vector 55 which acts on the shaft end 5 of the drive shaft and rotates with it, lies within the first angular range designated 57, which is preferably approximately 60 ° and whose central axis is approximately 90 ° to the maximum point of the
  • Eccentric section 13 is offset (axis 23-1). It is therefore advisable to arrange the lubrication groove 33 offset by 180 ° to the first winding area 57.
  • the preferred location for arranging the lubrication groove 33 is identified in FIG. 4 as the second angular range 59. In this way, the load-bearing capacity of the first plain bearing 7 is not impaired by the lubrication groove 33 in the area of its highest stress.
  • the first angular area 57 has 180 ° to the second
  • Angular range 59 is arranged offset, proven to be advantageous.
  • the first and second slide bearings 7 and 17 can also be lubricated with high-pressure fuel from the pump elements 23 (not shown).
  • a throttle (not shown) can be provided for each plain bearing.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Reciprocating Pumps (AREA)
  • Fuel-Injection Apparatus (AREA)
  • Lubrication Of Internal Combustion Engines (AREA)
  • Compressors, Vaccum Pumps And Other Relevant Systems (AREA)

Abstract

L'invention concerne une pompe à pistons radiaux pour un dispositif d'injection de moteurs à combustion interne, dans laquelle un premier palier lisse (7) et un second palier lisse (17) se présentent sous la forme de paliers lisses hydrostatiques. La pression nécessaire est mise à disposition par une pompe de pré-alimentation, qui alimente en carburant la pompe à pistons radiaux par l'intermédiaire d'une arrivée de carburant (31). La limite de charge du premier palier lisse (7) et du second palier lisse (17) est ainsi améliorée. En outre, lesdits paliers (7, 17) sont mieux refroidis. En conséquence, ladite pompe à pistons radiaux de l'invention peut être soumise à des charges plus élevées en ce qui concerne le refoulement et la hauteur de refoulement et présente une durée de vie plus longue que celle des pompes à piston radiaux de la technique antérieure.
PCT/DE2002/002879 2001-12-01 2002-08-06 Pompe a piston radiaux a graissage force Ceased WO2003048564A1 (fr)

Priority Applications (3)

Application Number Priority Date Filing Date Title
EP02764536A EP1454055B1 (fr) 2001-12-01 2002-08-06 Pompe a piston radiaux a graissage force
AT02764536T ATE308676T1 (de) 2001-12-01 2002-08-06 Radialkolbenpumpe mit zwangsschmierung
DE50204804T DE50204804D1 (de) 2001-12-01 2002-08-06 Radialkolbenpumpe mit zwangsschmierung

Applications Claiming Priority (4)

Application Number Priority Date Filing Date Title
DE10159099 2001-12-01
DE10159099.7 2001-12-01
DE10208574.9 2002-02-21
DE10208574A DE10208574A1 (de) 2001-12-01 2002-02-21 Radialkolbenpumpe

Publications (1)

Publication Number Publication Date
WO2003048564A1 true WO2003048564A1 (fr) 2003-06-12

Family

ID=26010700

Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/DE2002/002879 Ceased WO2003048564A1 (fr) 2001-12-01 2002-08-06 Pompe a piston radiaux a graissage force

Country Status (4)

Country Link
EP (1) EP1454055B1 (fr)
AT (1) ATE308676T1 (fr)
DE (1) DE50204804D1 (fr)
WO (1) WO2003048564A1 (fr)

Cited By (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2004040128A1 (fr) * 2002-10-31 2004-05-13 Robert Bosch Gmbh Pompe haute pression d'alimentation en carburant comprenant un clapet a bille dans l'admission basse pression
WO2008046683A1 (fr) * 2006-10-16 2008-04-24 Robert Bosch Gmbh Pompe à piston, notamment pompe de carburant haute pression, avec poussoir à galet
WO2008113623A1 (fr) * 2007-03-16 2008-09-25 Robert Bosch Gmbh Pompe à haute pression pour l'alimentation en carburant, dotée d'une structure améliorée de paliers pour le logement de l'arbre à cames
WO2009068448A1 (fr) * 2007-11-30 2009-06-04 Robert Bosch Gmbh Pompe à haute pression
ITMI20090638A1 (it) * 2009-04-17 2010-10-18 Bosch Gmbh Robert Circuito di lubrificazione di una pompa common rail di alta pressione e pompa common rail di alta pressione
WO2016005089A1 (fr) * 2014-07-09 2016-01-14 Delphi International Operations Luxembourg S.À R.L. Ensemble pompe
WO2024120473A1 (fr) * 2022-12-07 2024-06-13 北京天玛智控科技股份有限公司 Ensemble sabot de piston et pompe à piston radial entraînée par moyeu polygonal

Families Citing this family (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP2660456B1 (fr) * 2012-05-01 2017-12-06 Delphi International Operations Luxembourg S.à r.l. Pompe à carburant

Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE4126640A1 (de) * 1991-08-12 1993-03-04 Rexroth Mannesmann Gmbh Pumpenanordnung mit pumpen-hauptstufe und vorgeschalteter vorfoerderpumpe
DE19705205A1 (de) * 1997-02-12 1998-08-13 Bosch Gmbh Robert Kolbenpumpe
EP1101931A2 (fr) * 1999-11-19 2001-05-23 CRT Common Rail Technologies AG Système d'injection à haute pression avec common rail
DE10012306A1 (de) * 2000-03-14 2001-09-27 Bosch Gmbh Robert Verteilereinspritzpumpe

Patent Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE4126640A1 (de) * 1991-08-12 1993-03-04 Rexroth Mannesmann Gmbh Pumpenanordnung mit pumpen-hauptstufe und vorgeschalteter vorfoerderpumpe
DE19705205A1 (de) * 1997-02-12 1998-08-13 Bosch Gmbh Robert Kolbenpumpe
EP1101931A2 (fr) * 1999-11-19 2001-05-23 CRT Common Rail Technologies AG Système d'injection à haute pression avec common rail
DE10012306A1 (de) * 2000-03-14 2001-09-27 Bosch Gmbh Robert Verteilereinspritzpumpe

Cited By (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2004040128A1 (fr) * 2002-10-31 2004-05-13 Robert Bosch Gmbh Pompe haute pression d'alimentation en carburant comprenant un clapet a bille dans l'admission basse pression
US7273036B2 (en) 2002-10-31 2007-09-25 Robert Bosch Gmbh High-pressure fuel pump with a ball valve in the low-pressure inlet
WO2008046683A1 (fr) * 2006-10-16 2008-04-24 Robert Bosch Gmbh Pompe à piston, notamment pompe de carburant haute pression, avec poussoir à galet
WO2008113623A1 (fr) * 2007-03-16 2008-09-25 Robert Bosch Gmbh Pompe à haute pression pour l'alimentation en carburant, dotée d'une structure améliorée de paliers pour le logement de l'arbre à cames
WO2009068448A1 (fr) * 2007-11-30 2009-06-04 Robert Bosch Gmbh Pompe à haute pression
ITMI20090638A1 (it) * 2009-04-17 2010-10-18 Bosch Gmbh Robert Circuito di lubrificazione di una pompa common rail di alta pressione e pompa common rail di alta pressione
WO2010127899A1 (fr) * 2009-04-17 2010-11-11 Robert Bosch Gmbh Circuit de lubrification d'une pompe de rampe commune haute pression et pompe de rampe commune haute pression
WO2016005089A1 (fr) * 2014-07-09 2016-01-14 Delphi International Operations Luxembourg S.À R.L. Ensemble pompe
WO2024120473A1 (fr) * 2022-12-07 2024-06-13 北京天玛智控科技股份有限公司 Ensemble sabot de piston et pompe à piston radial entraînée par moyeu polygonal

Also Published As

Publication number Publication date
EP1454055B1 (fr) 2005-11-02
ATE308676T1 (de) 2005-11-15
EP1454055A1 (fr) 2004-09-08
DE50204804D1 (de) 2005-12-08

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