WO2009115353A1 - Pompe haute pression - Google Patents

Pompe haute pression Download PDF

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Publication number
WO2009115353A1
WO2009115353A1 PCT/EP2009/050679 EP2009050679W WO2009115353A1 WO 2009115353 A1 WO2009115353 A1 WO 2009115353A1 EP 2009050679 W EP2009050679 W EP 2009050679W WO 2009115353 A1 WO2009115353 A1 WO 2009115353A1
Authority
WO
WIPO (PCT)
Prior art keywords
pump
spring element
drive shaft
pump assembly
piston
Prior art date
Application number
PCT/EP2009/050679
Other languages
German (de)
English (en)
Inventor
Friedrich Boecking
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
Priority to AT09722786T priority Critical patent/ATE523685T1/de
Priority to CN2009801095468A priority patent/CN101978158B/zh
Priority to EP09722786A priority patent/EP2265811B1/fr
Publication of WO2009115353A1 publication Critical patent/WO2009115353A1/fr

Links

Classifications

    • 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
    • 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
    • F02M59/44—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
    • F02M59/48—Assembling; Disassembling; Replacing
    • 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
    • F04B1/0426—Arrangements for pressing the pistons against the actuated cam; Arrangements for connecting the pistons to the actuated cam
    • 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
    • F04B1/0439—Supporting or guiding means for the pistons
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01L—CYCLICALLY OPERATING VALVES FOR MACHINES OR ENGINES
    • F01L2307/00—Preventing the rotation of tappets

Definitions

  • the invention relates to a high-pressure pump, in particular a fuel pump for fuel injection systems. Specifically, the invention relates to the field of high pressure pumps for fuel injection systems of air compressing, auto-ignition internal combustion engines.
  • a high-pressure pump for a fuel injection device of an internal combustion engine has a pump housing, in which a pump element is arranged, which has a driven by a drive shaft in a stroke pump piston, which is guided displaceably in a cylinder bore of a part of the pump housing and limited in this a pump working space.
  • the pump piston is supported on the drive shaft via a hollow-cylindrical ram, wherein the ram is displaceably guided in a bore of a part of the pump housing in the direction of the longitudinal axis of the pump piston.
  • a return spring is provided, which ensures a contact of the pump piston on the plunger, so that the entire composite of pump piston, plunger and support element is acted upon via a roller to the cam of the drive shaft.
  • the high pressure pump according to the invention with the features of claim 1 has the advantage that an optimized design of the high pressure pump, in particular in the region of the pump assembly, is possible. Specifically, a return spring can be saved in the pump assembly, so that constructive freedom are created, for example, allow a more favorable design of the high-pressure pump, whereby the high-pressure pump is suitable for higher pressures and / or may have a higher efficiency.
  • a separate return spring or the like can be omitted in the pump assemblies.
  • the structural design in the region of the first pump assembly can be carried out with greater freedom.
  • a more compact design or a design that is suitable for higher pressures can take place.
  • the spring element is designed as an annular spring element, wherein the annular spring element may surround the drive shaft preferably adjacent to the cam.
  • the opposite arrangement of the pump assemblies is a reliable loading of the respective pistons of the pump assemblies in the direction of the drive shaft with a bias.
  • the first pump assembly has a roller skate that receives a running on the cam of the drive shaft roller and that the skate has a groove-shaped recess in which the spring element is at least partially disposed. It is also advantageous that the spring element has a band-shaped portion and that the band-shaped portion of the spring element is inserted into the groove-shaped recess of the skate. This allows the spring element at the same time prevent the rotation of the skate, so that a reliable alignment of the skate, in particular an orientation of the skate, which allows a coaxial alignment of the roller taken up by the roller with respect to an axis of the drive shaft, is possible.
  • the roller taken up by the roller skate of the pump assembly is oriented at least substantially coaxially with the axis of the drive shaft and that a starting element is attached to the spring element in the region of the roller, which causes a displacement of the roller in the direction of the axis of the drive shaft limited.
  • a further starting element may be provided in the opposite direction in order to limit a displacement of the roller in the direction of the axis of the drive shaft on both sides.
  • the first pump arrangement has a retaining bracket which connects the piston of the first pump arrangement with the spring element.
  • the headband can also be used at least partially in a groove-shaped recess of the skate.
  • a further spring element is provided, which is connected on the one hand by means of the retaining bracket with the piston of the first pump assembly and on the other hand at least indirectly with the piston of the second pump assembly, and that the spring element and the further spring element in the direction of an axis of the drive shaft spaced apart on different sides of the cam of the drive shaft are provided.
  • the further spring element can be developed according to the spring element.
  • the first pump arrangement is closed by a cylinder head, on which a projection projecting into the first pump arrangement is formed, wherein in the projection a cylinder bore is formed and the piston defines a pump working space in the cylinder bore and wherein an outer diameter of the projection is at least substantially is equal to an inner diameter of the bore in a main body of a housing into which the first pump assembly is inserted.
  • the approach in the cylinder bore may have a relatively large wall thickness, so that high pressures in the pump working space can be reached during operation.
  • a high efficiency of the high pressure pump can be achieved because elastic Deformations of the cylinder head, in particular in the region of the neck, in which the cylinder bore is formed, are reduced.
  • the second pump assembly may be further developed according to the first pump assembly. This also results in the corresponding advantages for the second pump assembly.
  • FIG. 1 shows a high-pressure pump in an excerpt, axial sectional view according to a first embodiment of the invention.
  • Fig. 2 is an excerpt section through the high-pressure pump shown in FIG. 1 along the section line designated by Il and
  • Fig. 3 is an excerpt section through the high-pressure pump shown in Fig. 1 according to a second embodiment of the invention.
  • Fig. 1 shows a high-pressure pump 1 in an excerpt, axial sectional view according to a first embodiment of the invention.
  • the high-pressure pump 1 can serve in particular as a fuel pump for fuel injection systems of air-compressing, self-igniting internal combustion engines.
  • a preferred use of the high pressure pump 1 is for a fuel injection system with a fuel rail, a so-called common rail that stores diesel fuel under high pressure.
  • the high-pressure pump 1 according to the invention is also suitable for other applications.
  • the high-pressure pump 1 has a multi-part housing 2. Furthermore, the high-pressure pump 1 has a drive shaft 3 which rotates about its axis 4 during operation.
  • the drive shaft 3 is on the one hand at a bearing point 5 in a base body 6 of the Housing 2 stored. On the other hand, the drive shaft 3 is mounted on a bearing 7 in a connected to the main body 6 flange 8 of the housing 2.
  • the two bearing points 5, 7 are arranged axially spaced from each other with respect to the axis 4.
  • cam 9 which may also be formed as a multiple cam.
  • the term of the cam 9 also includes embodiments of the drive shaft 3, in which, for example, the cam 9 is formed by an eccentric to the axis 4 formed portion on the drive shaft 3.
  • the main body 6 of the housing 2 has a first bore 15 and at least one second bore 16, which are arranged with respect to the axis 4 of the drive shaft 3 in mutually opposite radial directions.
  • a first pump assembly 17 is arranged in the first bore 15 of the base body 6.
  • a second pump assembly 18 is disposed in the second bore 16 of the base body 6.
  • the structure and function of the pump assemblies 17, 18 are described mainly with reference to the first pump assembly 17.
  • the structure of the second pump assembly 18 substantially corresponds to that of the first pump assembly 17.
  • the first bore 15 is closed by a housing part 19 serving as a cylinder head. Furthermore, the second pump assembly 18 is closed by a likewise serving as a cylinder head housing part 20.
  • the housing part 19 has a projection 21, in which a cylinder bore 22 is configured.
  • a piston 23 is arranged, which is displaceably mounted in the cylinder bore 22.
  • the piston 23 defines a pump working space 24 in the cylinder bore 22.
  • the pump working space 24 is connected to a fuel passage 25 in which an inlet valve 26 opening to the pump working space 24 is arranged.
  • the pump working space 24 is connected to a fuel passage 27 in which an exhaust valve 28 is arranged, which mainly has the function of preventing a backflow of fuel from the fuel passage 27 into the pump working space 24.
  • the outlet valve 28 and the fuel channel 27 high-pressure fuel can be conveyed to a fuel distributor strip during operation of the high-pressure pump 1.
  • a plunger body 30th In the bore 15 of the main body 6 of the housing 2 is a plunger body 30th arranged, which is guided in the bore 15.
  • the plunger body 30 is preferably made relatively thin-walled.
  • an outer diameter 31 of the projection 21 can be essentially the same size as an inner diameter 32 of the bore 15.
  • a high pressure in the pump chamber 24 can be generated, wherein an elastic expansion of the housing part 19, in particular in the region of the projection 21, is avoided , This also allows high pressure generation efficiency.
  • the pump assembly 17 has a roller skate 35 which receives a roller 36 running on the cam 9 of the drive shaft 3.
  • the roller 36 is oriented at least substantially coaxially with the axis 4 of the drive shaft 3.
  • the piston 23 is supported by a collar 37 of the piston 23 on the skate 35.
  • the high-pressure pump 1 has a spring element 40 and a further spring element 41.
  • the spring elements 40, 41 are arranged axially spaced relative to each other with respect to the axis 4 of the drive shaft 3. Furthermore, the spring elements 40, 41 are arranged on different sides of the cam 9 of the drive shaft 3. The spring elements 40, 41 thereby surround the drive shaft 3 circumferentially, as is also illustrated with reference to FIG. 3.
  • the piston 23 of the first pump assembly 17 is connected to a piston 23 'of the second pump assembly 18.
  • the spring elements 40, 41 are on the one hand indirectly connected to the piston 23 and on the other hand indirectly connected to the piston 23 '.
  • the connection of the piston 23 with the spring elements 40, 41 is further described in detail below.
  • the connection of the piston 23 'with the spring elements 40, 41 results in a corresponding manner.
  • the first pump assembly 17 has a retaining clip 45, which surrounds the piston 23 above the collar 37, that is to say radially outward viewed from the axis 4.
  • the retaining clip 45 can thereby hold the piston 23 in abutment with the roller skate 35 with respect to rotational forces occurring during operation.
  • the retaining clip 45 is connected to the spring elements 40, 41, which in turn are connected to the piston 23 '.
  • the spring elements 40, 41 are under a certain bias, so that the headband 45 presses the collar 37 of the piston 23 against the skate 35, which is supported on the roller 36 on the cam 9. Thereby, the piston 23, the Roller skate 35, the roller 36 and the cam 9 are held in abutment with each other.
  • the first pump assembly 17 also has start-up elements 46, 47, wherein a pin-shaped projection 46 'of the starting element 46, the spring element 40 connects to the headband 45, while a pin-shaped projection 47' of the starting element 47 connects the headband 45 with the other spring element 41.
  • the start-up elements 46, 47 thereby limit a coaxial displaceability of the roller 36, so that within certain limits a centering of the roller 36 with respect to the running surface of the cam 9 is achieved.
  • a tilting or pivoting that is, a non-coaxial operation, the roller 36 can be avoided relative to the axis 4 or at least limited in extent, so that a reliable operation of the high pressure pump 1 is ensured.
  • the cam 9 serves both to drive the first pump assembly 17 and the second pump assembly 18.
  • the spring elements 40, 41, the respective elements of the pump assemblies 17, 18 are held together, so that a reliable operation of the high-pressure pump 1 is possible, with separate return springs for the pistons 23, 23 'of the pump assemblies 17, 18 can each be saved.
  • This allows, inter alia, the relatively thick-walled design of the projection 21 to the cylinder bore 22 of the first pump assembly 17 and a corresponding configuration in the second pump assembly 18.
  • FIG. 2 shows an excerpted section through the high-pressure pump 1 shown in FIG. 1 along the section line designated by II in accordance with the embodiment of the first exemplary embodiment of the invention.
  • the headband 45 is designed band-shaped and inserted into a groove-shaped recess 48 in the skate 35.
  • the spring elements 40, 41 may be at least partially inserted into the groove-shaped recess 48 of the skate 35.
  • By inserting the retaining clip 45 and optionally the spring elements 40, 41 in the groove-shaped recess 48 is a rotation of the skate 35 with respect to a desired position in which the roller 36 is guided coaxially with the axis 4 of the drive shaft 3, prevented.
  • a coaxial movement of the roller 36 is achieved to the drive shaft 3.
  • a high reliability of the high-pressure pump 1 can be ensured.
  • FIG. 3 shows an excerpted section through a high-pressure pump 1 along the in FIG Fig. 1 with III designated cutting line according to a second embodiment of the invention.
  • the headband 45 is shown cut back at the height of an axis 49 of the piston 23 to allow the view of the spring element 40, the groove-shaped recess 48 and the skate 35.
  • the spring element 40 has a band-shaped portion 49.
  • the band-shaped portion 49 has a circular opening 50, through which the pin-shaped projection 46 'of the starting element 46 extends.
  • the pin-shaped projection 46 'of the starting element 46 also extends through a corresponding opening in the retaining clip 45, so that the spring element 40 is reliably connected at its band-shaped portion 49 to the retaining clip 45.
  • the band-shaped portion 49 of the spring element 40 is partially inserted into the groove-shaped recess 48 of the skate 35, so that a rotation of the skate 35 is prevented from its desired position.
  • the spring element 40 may surround the drive shaft 3 outside the region of the cam 9 or else be arranged within the region of the cam 9, so that the spring element surrounds the cam 9 of the drive shaft 3 in a circumferential manner.
  • the spring element 40 is preferably mounted biased, so that the spring element 40 biases the piston 23 in the direction of the drive shaft 3. This can account for a separate return spring, in particular in the region of the projection 21 of the housing part 19 serving as a cylinder head.
  • the spring element 40 is designed as an annular spring element 40, so that a uniform force transmission between the first pump assembly 17 and the second pump assembly 18 for returning the piston 23, 23 'is possible in dependence on the respective operating position.
  • the pistons 23, 23 ' are connected to one another via at least one spring element 40 so that restoring or return springs in the pump assemblies 17, 18 can be saved.
  • the space saved with respect to a design with return or return springs can be used to reinforce the projection 21 of the cylinder head housing part 19 in the region of the bore 15, which serves as a guide for the plunger body 30, so that an expansion of the as a cylinder head serving housing part 19 is reduced under high pressure.
  • the spring element 40 runs in the region of the roller skate 35 in a groove-shaped recess 48, so that a rotation of the roller skate 35 is prevented.
  • the spring element 40 may additionally in the region of the roller 36 a tarnish protection assume a starting element 46, which is also the connecting piece for the spring element 40 with the headband 45.
  • the high-pressure pump 1 Special advantages of the high-pressure pump 1 are thus a significantly reinforced, given by the housing part 19 cylinder head and the guaranteed rotation.
  • the reinforced cylinder head allows an optionally significant increase in the efficiency of the high pressure pump. 1

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Reciprocating Pumps (AREA)
  • Details Of Reciprocating Pumps (AREA)
  • Fuel-Injection Apparatus (AREA)

Abstract

L'invention concerne une pompe haute pression (1) servant en particulier de pompe à carburant pour des systèmes d'injection de carburant de moteurs à combustion interne à autoallumage par compression. La pompe haute pression (1) comprend un premier module de pompe (17) et un second module de pompe (18) ainsi qu'un arbre d'entraînement (3). Le premier module de pompe (17) est placé au moins approximativement à l'opposé du second module de pompe (18) par rapport à l'arbre d'entraînement (3). L'arbre d'entraînement (3) comporte au moins une came (9) servant à entraîner aussi bien le premier module de pompe (17) que le second module de pompe (18). De plus, des éléments élastiques (40, 41) sont reliés, d'une part, à un piston (23) du premier module de pompe (17) au moyen d'un étrier de retenue (45) et, d'autre part, à un piston (23') du second module de pompe (18). Les éléments élastiques (40, 41) sont montés sous précontrainte, de sorte que les deux pistons (23, 23') sont rappelés sans ressort de rappel séparé lorsque la pompe haute pression (1) est en service.
PCT/EP2009/050679 2008-03-17 2009-01-22 Pompe haute pression WO2009115353A1 (fr)

Priority Applications (3)

Application Number Priority Date Filing Date Title
AT09722786T ATE523685T1 (de) 2008-03-17 2009-01-22 Hochdruckpumpe
CN2009801095468A CN101978158B (zh) 2008-03-17 2009-01-22 高压泵
EP09722786A EP2265811B1 (fr) 2008-03-17 2009-01-22 Pompe haute pression

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102008000710A DE102008000710A1 (de) 2008-03-17 2008-03-17 Hochdruckpumpe
DE102008000710.2 2008-03-17

Publications (1)

Publication Number Publication Date
WO2009115353A1 true WO2009115353A1 (fr) 2009-09-24

Family

ID=40430017

Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/EP2009/050679 WO2009115353A1 (fr) 2008-03-17 2009-01-22 Pompe haute pression

Country Status (5)

Country Link
EP (1) EP2265811B1 (fr)
CN (1) CN101978158B (fr)
AT (1) ATE523685T1 (fr)
DE (1) DE102008000710A1 (fr)
WO (1) WO2009115353A1 (fr)

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2012079831A1 (fr) * 2010-12-17 2012-06-21 Robert Bosch Gmbh Pompe haute pression
CN103726964A (zh) * 2012-10-16 2014-04-16 北京亚新科天纬油泵油嘴股份有限公司 高压共轨泵用的吸油控制装置

Families Citing this family (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102012212579B4 (de) * 2012-07-18 2018-11-22 Continental Automotive Gmbh Rollenstößelanordnung für eine Radialkolbenpumpe mit zwei Sicherungselementen für die Laufrolle des Rollenstößels
FR3016929B1 (fr) * 2014-01-30 2018-02-16 Societe De Motorisations Aeronautiques Dispositif d'injection de carburant pour moteur a pistons a plat
DE102017103483B3 (de) * 2017-02-21 2018-01-04 Schaeffler Technologies AG & Co. KG Rollenstößel
DE102017107100B3 (de) 2017-04-03 2018-06-14 Schaeffler Technologies AG & Co. KG Leichtbau Rollenstößel
DE102017107099B3 (de) * 2017-04-03 2018-06-28 Schaeffler Technologies AG & Co. KG Mehrteiliger Rollenstößel für eine Kraftstoffhochdruckpumpe
IT201800006423A1 (it) * 2018-06-18 2019-12-18 Gruppo di pompaggio per alimentare combustibile, preferibilmente gasolio, ad un motore a combustione interna

Citations (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB533405A (en) 1939-11-03 1941-02-12 Automotive Prod Co Ltd Improvements in or relating to reciprocating pumps
DE4027794A1 (de) 1990-09-01 1992-03-05 Teves Gmbh Alfred Hydraulische radialkolbenpumpe
DE9209366U1 (de) * 1992-07-11 1993-07-29 Wap Reinigungssysteme Gmbh & Co, 89287 Bellenberg Radialkolbenpumpe
DE19650276A1 (de) * 1996-12-04 1998-06-10 Teves Gmbh Alfred Hubkolbenpumpe
DE19816044A1 (de) * 1998-04-09 1999-10-21 Bosch Gmbh Robert Radialkolbenpumpe zur Kraftstoffhochdruckerzeugung
DE19948445A1 (de) 1999-10-08 2001-04-12 Continental Teves Ag & Co Ohg 6-Kolben-Pumpe, insbesondere für geregelte Bremssysteme
DE102005046670A1 (de) 2005-09-29 2007-04-05 Robert Bosch Gmbh Hochdruckpumpe, insbesondere für eine Kraftstoffeinspritzeinrichtung einer Brennkraftmaschine

Family Cites Families (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE10355027A1 (de) * 2003-11-25 2005-06-23 Robert Bosch Gmbh Hochdruckpumpe, insbesondere für eine Kraftstoffeinspritzeinrichtung einer Brennkraftmaschine

Patent Citations (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB533405A (en) 1939-11-03 1941-02-12 Automotive Prod Co Ltd Improvements in or relating to reciprocating pumps
DE4027794A1 (de) 1990-09-01 1992-03-05 Teves Gmbh Alfred Hydraulische radialkolbenpumpe
DE9209366U1 (de) * 1992-07-11 1993-07-29 Wap Reinigungssysteme Gmbh & Co, 89287 Bellenberg Radialkolbenpumpe
DE19650276A1 (de) * 1996-12-04 1998-06-10 Teves Gmbh Alfred Hubkolbenpumpe
WO1998025028A1 (fr) * 1996-12-04 1998-06-11 Itt Manufacturing Enterprises, Inc. Pompe a pistons alternatifs
DE19816044A1 (de) * 1998-04-09 1999-10-21 Bosch Gmbh Robert Radialkolbenpumpe zur Kraftstoffhochdruckerzeugung
DE19948445A1 (de) 1999-10-08 2001-04-12 Continental Teves Ag & Co Ohg 6-Kolben-Pumpe, insbesondere für geregelte Bremssysteme
DE102005046670A1 (de) 2005-09-29 2007-04-05 Robert Bosch Gmbh Hochdruckpumpe, insbesondere für eine Kraftstoffeinspritzeinrichtung einer Brennkraftmaschine

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2012079831A1 (fr) * 2010-12-17 2012-06-21 Robert Bosch Gmbh Pompe haute pression
CN103726964A (zh) * 2012-10-16 2014-04-16 北京亚新科天纬油泵油嘴股份有限公司 高压共轨泵用的吸油控制装置

Also Published As

Publication number Publication date
DE102008000710A1 (de) 2009-09-24
EP2265811B1 (fr) 2011-09-07
CN101978158B (zh) 2013-03-27
ATE523685T1 (de) 2011-09-15
CN101978158A (zh) 2011-02-16
EP2265811A1 (fr) 2010-12-29

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