EP1184572A2 - Joint d'étanchéité haute pression - Google Patents

Joint d'étanchéité haute pression Download PDF

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Publication number
EP1184572A2
EP1184572A2 EP01117578A EP01117578A EP1184572A2 EP 1184572 A2 EP1184572 A2 EP 1184572A2 EP 01117578 A EP01117578 A EP 01117578A EP 01117578 A EP01117578 A EP 01117578A EP 1184572 A2 EP1184572 A2 EP 1184572A2
Authority
EP
European Patent Office
Prior art keywords
pressure seal
seal
sealing device
pressure
high pressure
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
EP01117578A
Other languages
German (de)
English (en)
Other versions
EP1184572A3 (fr
EP1184572B1 (fr
Inventor
Bernhard Arnold
Thorsten Beck
Ralf Goebl
Karl Huber
Hans-Ulrich Leutwein
Uwe Nigrin
Matthias Weidner
Franz Wirzberger
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.)
Continental Automotive GmbH
Original Assignee
Siemens AG
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 Siemens AG filed Critical Siemens AG
Publication of EP1184572A2 publication Critical patent/EP1184572A2/fr
Publication of EP1184572A3 publication Critical patent/EP1184572A3/fr
Application granted granted Critical
Publication of EP1184572B1 publication Critical patent/EP1184572B1/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
    • F04B1/0448—Sealing means, e.g. for shafts or housings
    • 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
    • F04B53/00—Component parts, details or accessories not provided for in, or of interest apart from, groups F04B1/00 - F04B23/00 or F04B39/00 - F04B47/00
    • F04B53/007—Cylinder heads
    • 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
    • F04B53/00—Component parts, details or accessories not provided for in, or of interest apart from, groups F04B1/00 - F04B23/00 or F04B39/00 - F04B47/00
    • F04B53/16—Casings; Cylinders; Cylinder liners or heads; Fluid connections
    • 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
    • F02M2200/00—Details of fuel-injection apparatus, not otherwise provided for
    • F02M2200/16—Sealing of fuel injection apparatus not otherwise provided for
    • 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

Definitions

  • the present invention relates to a sealing device for a transition area on high pressure components and in particular a sealing device for transition areas on pump components of pumps for common rail systems.
  • FIG. 11 there is a known high pressure seal 1 for a common rail system, which on a Transition area 5 between a first component 2 and a second component 3 is used to continue to enable a fluid channel 6.
  • High-pressure seal 1 consists of two elements, namely one Sealing ring 24 and a support ring 25, which in a recess 4 are arranged, which are formed in the first component 2 is.
  • the sealing ring 24 is made of an elastomer.
  • the support ring 25 is on the outer circumference of the sealing ring 24 arranged to the sealing ring 24 against the high pressures in the Support common rail.
  • the support ring has none Sealing function.
  • a valve 26 is arranged first to the second component, which essentially from a valve ball 22, a spring element 27 and a basket-shaped ball cage 28.
  • high pressure seals are disadvantageous that they are not over the entire temperature range seal completely. Especially at low temperatures are the sealing properties of the well-known high pressure seals not sufficient, often causing leakage occurs to the outside. This results in sealing problems in particular when starting a cold engine, especially in winter because the sealing ring withstands the high pressures in the common rail system (up to approx. 1800 bar) does not withstand. Further the known high pressure seals are disadvantageous in that that depends on the operating loads (pressure, forces) there is a gap in the transition region 5. From a certain The gap size or frequency of the gap change is the Elastomeric ring is no longer able to pass this transition area seal. This leads to undesirable leaks during of the company.
  • a sealing device Sealing high pressure components at a transition area provided on a high pressure line, which has a high pressure seal with a substantially annular shape and includes a low pressure seal.
  • the high pressure seal is at a line transition of the high pressure components arranged.
  • the low pressure seal is outside the high pressure seal arranged to prevent any leakage to seal securely to the outside thanks to the high pressure seal. So there is a redundant sealing system, which is an escape of fluid at transition areas of high pressure components can reliably prevent. Therefore can occur in the event of leakage through the high pressure seal retained by the low pressure seal become. Accordingly, the combination of a high pressure seal and a low pressure seal reliably prevents leakage prevent.
  • the present invention can be found in a common rail system at transitions between pump components be used.
  • the high pressure seal is made of metal. Further is the inventive high pressure seal made of metal preloaded when assembled. Thereby can be achieved that the high pressure seal after the Assembly due to their preload with high pressure on their Contact surfaces for sealing.
  • a high-pressure seal according to the invention provides a seal, which over the entire temperature range ensures adequate sealing without leakage, especially in the lower temperature range.
  • the combination of the preload of the seal and of the sealing ring made of metal is a dynamically resilient High pressure seal provided, which in particular Pressure pulsations with a high frequency can follow and thus no leaks due to fluid-induced Has stress pulses.
  • the invention requires High pressure seal also no support ring, because they are adequate due to their manufacture from a metal Resistance to high pressures. moreover is the high pressure seal made of metal against aggressive Media resistant.
  • the high-pressure seal is preferably made of spring plate or made of steel. This can be an inexpensive and easy to manufacture high pressure seal can be obtained. When producing the seal from spring plate, the further also a particularly simple prestressing of the seal be realized.
  • the high-pressure seal made of temperature-resistant Plastic or made of rubber. Particularly preferred an elastomer is used as the plastic.
  • the low pressure seal made of metal or made of plastic or rubber or from one with plastic coated metal.
  • the low pressure seal is preferably a flat seal or designed as a profile seal. Particularly preferred the low pressure seal has a bead.
  • the high pressure seal as a ring with a C-shaped Cross section formed.
  • the open area of the C-shaped ring directed inwards. Due to the C-shaped design of the high pressure seal in particular, that the seal is additionally achieved through the fluid pressure with great force against their contact surfaces is pressed because the fluid pressure in the direction of the contact surface is directed.
  • the existing contact pressure due to the geometric Design of the seal in C-shape reinforced.
  • Can continue the C-ring-shaped high pressure seal also deforms components, which arise due to the high pressures, very good compensate for the fact that due to its C-shape it especially the extensions and the approaches, neighboring Components can follow easily due to the high pressure.
  • the high-pressure seal which is C-shaped in cross section is particularly preferred a symmetrical shape, so that a mix-up is guaranteed.
  • the high-pressure seal advantageously has two sealing surfaces or three sealing surfaces.
  • the seal can thus be arranged such that it has an upper and a lower contact surface for sealing. It is also possible to have a third contact surface through the outward circular section of the C-shaped sealing ring is formed.
  • the high pressure seal as a ring with a angular cross section.
  • This has so-called wedge ring in the unassembled state one leg angle, i.e. an angle between his two legs, from significantly larger than 90 °. For example, this leg angle is approx. 115 ° when not installed.
  • the one leg When assembled the one leg is attached to an area of the one component pressed. The other leg is against the sealing surface of the second component pressed.
  • This is the leg angle the wedge ring when installed is significantly smaller than in the unassembled state and is approx. 90 ° to 95 °.
  • both legs of the wedge ring lie directly on the sealing surfaces of the two components, so that a very secure seal is achieved.
  • the wedge ring is made of metal e.g. a sheet (spring sheet) manufactured.
  • the high-pressure seal preferably has a cross section tapered area.
  • This can, for example a wedge-shaped seal can be provided.
  • the wedge-shaped surface of the seal is on the inside of the seal directed. It is particularly preferred tapered area parabolic or rectilinear in section educated.
  • the high pressure seal has in addition to that tapered area an area with constant internal and outside diameter.
  • one of the Contact surfaces for sealing are relatively large.
  • the high pressure seal has a central connection area on which has at least one through opening having.
  • the middle connection area connects the outer ones Ring areas of the seal with each other. This allows the The stability of the high pressure seal can be increased.
  • the high-pressure seal is advantageously designed in the form of a button.
  • the high pressure seal has a flat circular shape middle connection area so that the high pressure seal e.g. as a cage or stop for a valve body can be used.
  • the high pressure seal e.g. as a cage or stop for a valve body can be used.
  • the high pressure seal with a cage for a valve body combined to retain a valve body. Consequently the high pressure seal has both a sealing function as well as a retention function for a valve body valve located immediately before the seal.
  • the button-shaped high-pressure seal is preferably included four through openings are provided to ensure adequate To ensure fluid flow.
  • the middle connection area at one in cross section C-shaped ring formed at one end in the vertical direction. This enables the advantages of the C-shaped high pressure seal with those of the middle connection area combine.
  • the central connection area preferably serves as a stop for the valve body. This makes it particularly easy Construction of the high pressure seal and one immediately valve adjacent to the seal.
  • the present invention provides a redundant sealing device through a combination of a high pressure seal ready with a low pressure seal.
  • the sealing device has a simple structure and enables over the entire temperature range in which the Combination seal is used, a reliable seal without leakage problems, especially in the low temperature range.
  • This is further combined by a high pressure sealing made of metal and the preload the seal is further reinforced, so that excellent sealing properties can be provided.
  • the sealing device according to the invention an insensitivity to load pulses occurring in the delivery fluid achieved, which with the previously used Elastomer seals were not given.
  • it can sealing system according to the invention also as a cage or stop can be used for a valve body and is durable against aggressive media.
  • Figures 1 and 2 is a high pressure seal 1 for a Sealing device according to a first embodiment of the present invention.
  • the high pressure seal 1 is at a transition area 5 between a first component 2 (e.g. a cylinder) and a second component 3 (e.g. a cylinder head). There is a recess 4 on the first component 2 for receiving the high pressure seal 1 provided (see FIG. 1). At the transition area 5 opens a fluid channel 6 of the first component 2, which is continued in the second component 3. The recess 4 is formed around the mouth of the fluid channel 6. The high-pressure seal 1 must therefore cover the transition area 5 Seal around the fluid channel 6 to prevent fluid leakage to prevent.
  • the high-pressure seal 1 an annular shape. Further, as can be seen from Figure 1 is, the high pressure seal 1 has a C-shaped Cross section on.
  • the high-pressure seal shows 1 a first straight section 7, a curved section 8 and a second straight section 9.
  • the two straight sections 7 and 9 lie with their flat surfaces on the first or second component and thus form annular Sealing areas 10 and 11 in the form of line seals.
  • the curved section 8 is designed such that he is in contact with the side wall of the recess 4 comes and thus an additional third sealing area 30 forms.
  • the C-shaped High-pressure seal is completely curved, i.e. is formed without straight sections or such that he only has two sealing areas, e.g. B. the two sealing areas 10 and 11.
  • the C-shaped high pressure seal 1 has its entire Cross-section has a constant thickness. However, it is also possible that the high pressure seal, especially if made of sheet metal or similar is produced, different in cross section Has thicknesses.
  • the high-pressure seal 1 points in the vertical direction, i.e. in the direction of the central axis 0-0, one at one end Inside diameter D1 and at the other end an inside diameter D2 on.
  • the inside diameter is D1 equal to the inside diameter D2, so the high pressure seal 1 is symmetrical.
  • the high pressure seal 1 of the first embodiment is made of spring steel and the two straight sections 7 and 9 are biased outwards so that they are installed Condition against the wall surfaces of the first and second Component 2 and 3 are pressed. Due to the concave arrangement of the curved area 8 to the fluid channel 6 supported the fluid pressure the pressing of the straight regions 7 and 9 against the respective contact surfaces of the first and second Component.
  • the C-ring-shaped high pressure seal 1 is constructed symmetrically is the same at both ends in the vertical direction Has inner diameter D1 and D2, the pressing forces the same at all points of the high pressure seal 1. Consequently can secure sealing of the transition region 5 is achieved become. Since the preload of the high pressure seal 1 over the entire temperature range is one adequate sealing, especially at low temperatures guaranteed. Furthermore, you can also easily high-frequency pressure pulsations are recorded in the fluid and Component deformations due to the high pressure compensated become. Furthermore, the symmetrical structure of the High pressure seal 1 ensures a mix-up-free installation and the high pressure seal is against aggressive Media resistant.
  • FIG 3 is the sealing device according to the invention with the C-ring-shaped high pressure seal 1 according to the first Embodiment shown.
  • the sealing device comprises the high pressure seal and a low pressure seal 12.
  • the high pressure seal 1 seals a transition area between a cylinder block 2 and a cylinder head 3 a fluid channel 6.
  • the high pressure seal 1 is in a on the cylinder block 2 formed annular recess 4 inserted.
  • Between cylinder head 3 and cylinder block 2 is further the low-pressure seal 12 designed as a flat seal arranged.
  • the low pressure seal 12 is one with a Sheet with an elastomer coating and can also have one Have a bead.
  • the transition area on the fluid channel 6 sealed twice by the sealing device, namely by the high pressure seal 1 and the low pressure seal 12.
  • the two seals are in the assembled state 1 and 12 of the sealing device essentially in one level at the transition area 5.
  • FIG 4 is a sealing device according to a second Embodiment shown.
  • the second embodiment corresponds essentially to that shown in FIG first embodiment.
  • the flat gasket Form seal or profile seal 12 is provided, which in a corresponding recess 13 inserted in the cylinder block 2 becomes.
  • the molded seal 12 is outside the high pressure seal 1 arranged so that a direct connection from the High pressure seal 1 to the low pressure area guaranteed is.
  • FIGS A high-pressure seal 1 is shown in FIGS Use in a sealing device according to the invention according to a third embodiment of the present invention shown. Same or functionally the same parts have the same reference numerals as in the first embodiment designated. Because the third embodiment corresponds essentially to the first exemplary embodiment, are only the differences between the two below Exemplary embodiments described in detail.
  • the high pressure seal 1 is for one Sealing device at a transition area 5 of a fluid channel 6 between a first component 2 and a second Component 3 arranged.
  • the high pressure seal 1 is, as shown in Figures 5 and 6, button-shaped.
  • a C-ring-shaped edge region 16 one of its sides in the vertical direction (i.e. in the direction the center line 0-0) a middle connection area 17 on.
  • a first straight section 7 a curved section 8 and a second straight section 9 formed C-shaped edge area 16 at its second straight section 9 with the middle connection area 17 connected.
  • the second straight section 9 goes in the middle connection area over.
  • the section 7 can also be curved.
  • a valve ball 22 is provided, which on a Valve seat 23 abuts.
  • a valve is formed.
  • the button-shaped high-pressure seal 1 forms the ball cage for the valve ball 22.
  • the in Area of the midline 0-0 lying section of the middle Connection area 17 a greater thickness than the edge area 16 to provide sufficient strength for retention to provide the valve ball 22.
  • the high-pressure seal 1 for a sealing device according to the third embodiment in addition to the Sealing function also a retention function for the Valve ball 22 on.
  • the high pressure seal 1 made of metal e.g. made of spring steel, can be made. It is also possible to choose between the as Cage serving high pressure seal and the valve ball still to arrange a spring element so that a check valve in Fluid channel 6 arranged between the first and the second component is.
  • FIG. 7 and 8 is a high pressure seal 1 for a Sealing device according to a fourth embodiment of the present invention. Same or Functionally identical parts have the same reference symbols as referred to in the previously described embodiments. Since the fourth embodiment essentially corresponds to the previously described exemplary embodiments, are only the differences to the exemplary embodiments described in detail.
  • the high pressure seal 1 is at one Transition area 5 between a first component 2 and arranged a second component 3. It is in one Recess 4 positioned, which is formed in the first component 2 is and seals a transition of a fluid channel 6.
  • the high-pressure seal 1 a first area 14 and a second area 15.
  • the first area 14 has a constant inside and outside diameter and therefore has a rectangular section Shape up. However, the first area 14 can also be different Have inside and outside diameter.
  • the second Area 15 tapers starting from the first area 14 to its outside. As shown in Figure 7, the is tapering region 15 is parabolic in section.
  • This configuration of the high-pressure seal according to the invention 1 arise at the contact surfaces of the seal 1 different areas for the first and second component of sealing areas 10 and 11.
  • the wedge ring-shaped High pressure seal 1 To on both sealing areas to get a surface pressure, the wedge ring-shaped High pressure seal 1 to one side accordingly biased.
  • the high pressure seal is pressed 1 to areas 10 and 11 and towards the center line 0-0 extending area 30 of the recess 4.
  • To a to obtain additional prestressing of the high pressure seal 1, are the sealing areas 10 and 30 of the seal 1 in the unassembled state to each other at an angle of greater arranged as 90 ° - 95 °.
  • the sealing areas are in the assembled state 10 and 30 then at an angle of 90 ° - 95 ° arranged to each other.
  • the high pressure seal 1 according to the fourth Embodiment a sufficient sealing function very high pressures and is insensitive to the fluid occurring high-frequency pressure pulsations and resistant to PME fluids.
  • FIG. 9 and 10 is a high pressure seal 1 for a sealing device according to a fifth embodiment of the present invention. Same or Functionally identical parts have the same reference symbols as referred to in the previously described embodiments. Since the fifth embodiment essentially corresponds to the previously described exemplary embodiments, are only the differences to the exemplary embodiments described in detail.
  • the high pressure seal is 1 for the sealing device as a so-called wedge seal educated.
  • the wedge seal 1 is annular and includes a first leg 31 and a second Leg 32.
  • the two legs 31 and 32 have the same length. You can but also have different lengths.
  • the high-pressure seal 1 is provided in a component 2 Recess 4 arranged.
  • the depth corresponds to the Recess 4 essentially the length of the leg of the leg 32.
  • the high-pressure seal 1 is in an intermediate assembly step shown.
  • the high pressure seal 1 inserted into the recess 4.
  • sealing device according to the invention from any combination of those previously described High pressure seals or low pressure seals can be formed.
  • the present invention relates to a sealing device with a high pressure seal 1 and one Low pressure seal 12 for sealing a transition area 5 on a high-pressure line 6, which in particular is used in common rail systems.
  • the high pressure seal 1 has a substantially annular shape and is arranged at the line transition of the high pressure components 2, 3.
  • the low pressure seal 12 is in one plane with the high-pressure seal 1 arranged around it to a Any leakage that may occur through the high pressure seal 1 to seal to the outside.
  • a reliable, redundant seal are provided which dynamic across the entire operating temperature range resilient high-pressure sealing ring 1 and also for one Use with aggressive media is suitable.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Gasket Seals (AREA)
EP01117578A 2000-08-29 2001-07-20 Joint d'étanchéité haute pression Expired - Lifetime EP1184572B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE2000142305 DE10042305A1 (de) 2000-08-29 2000-08-29 Abdichtungsvorrichtung für einen Übergangsbereich an Hochdruckbauteilen
DE10042305 2000-08-29

Publications (3)

Publication Number Publication Date
EP1184572A2 true EP1184572A2 (fr) 2002-03-06
EP1184572A3 EP1184572A3 (fr) 2003-03-19
EP1184572B1 EP1184572B1 (fr) 2008-06-11

Family

ID=7654110

Family Applications (1)

Application Number Title Priority Date Filing Date
EP01117578A Expired - Lifetime EP1184572B1 (fr) 2000-08-29 2001-07-20 Joint d'étanchéité haute pression

Country Status (2)

Country Link
EP (1) EP1184572B1 (fr)
DE (2) DE10042305A1 (fr)

Cited By (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2004046547A1 (fr) * 2002-11-15 2004-06-03 Robert Bosch Gmbh Pompe a piston radial pourvue d'une garniture d'etancheite plane entre le flasque et le carter
DE10310123A1 (de) * 2003-03-07 2004-09-23 Siemens Ag Radialkolbenpumpe
WO2009071462A1 (fr) * 2007-12-06 2009-06-11 Robert Bosch Gmbh Joint d'étanchéité pour pompe haute pression et pompe haute pression comprenant ledit joint d'étanchéité
WO2009135709A1 (fr) * 2008-05-06 2009-11-12 Robert Bosch Gmbh Pompe à carburant haute pression pour faire fonctioner un moteur à combustion interne
WO2012038198A1 (fr) * 2010-09-22 2012-03-29 Robert Bosch Gmbh Pompe haute pression et procédé pour produire un corps de pompe
WO2017220696A1 (fr) * 2016-06-23 2017-12-28 Delphi International Operations Luxembourg S.À R.L. Joint d'étanchéité d'une plaque avant d'une pompe haute pression

Families Citing this family (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102005023226B4 (de) 2005-05-20 2019-05-16 Audi Ag Maschinenbauteilanordnung mit einer Flachdichtung und Flachdichtung
EP2072818A1 (fr) 2007-12-21 2009-06-24 Reinz-Dichtungs-GmbH & Co. KG Joint plat métallique et son utilisation

Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE19653339A1 (de) * 1996-12-20 1998-06-25 Rexroth Mannesmann Gmbh Pumpenanordnung zur Förderung von Kraftstoff
DE19726572A1 (de) * 1997-06-23 1998-12-24 Mannesmann Rexroth Ag Radialkolbenpumpe
DE19802476A1 (de) * 1998-01-23 1999-07-29 Bosch Gmbh Robert Pumpenanordnung zur Kraftstoffhochdruckversorgung
EP1013921A2 (fr) * 1998-12-25 2000-06-28 Denso Corporation Pompe d'injection de carburant

Patent Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE19653339A1 (de) * 1996-12-20 1998-06-25 Rexroth Mannesmann Gmbh Pumpenanordnung zur Förderung von Kraftstoff
DE19726572A1 (de) * 1997-06-23 1998-12-24 Mannesmann Rexroth Ag Radialkolbenpumpe
DE19802476A1 (de) * 1998-01-23 1999-07-29 Bosch Gmbh Robert Pumpenanordnung zur Kraftstoffhochdruckversorgung
EP1013921A2 (fr) * 1998-12-25 2000-06-28 Denso Corporation Pompe d'injection de carburant

Cited By (10)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2004046547A1 (fr) * 2002-11-15 2004-06-03 Robert Bosch Gmbh Pompe a piston radial pourvue d'une garniture d'etancheite plane entre le flasque et le carter
CN100429398C (zh) * 2002-11-15 2008-10-29 罗伯特·博世有限公司 在法兰盘与壳体之间设有平面密封件的径向柱塞泵
DE10310123A1 (de) * 2003-03-07 2004-09-23 Siemens Ag Radialkolbenpumpe
US7415920B2 (en) 2003-03-07 2008-08-26 Siemens Aktiengesellschaft Radial piston pump
CN1756905B (zh) * 2003-03-07 2011-06-08 欧陆汽车有限责任公司 径向柱塞泵
WO2009071462A1 (fr) * 2007-12-06 2009-06-11 Robert Bosch Gmbh Joint d'étanchéité pour pompe haute pression et pompe haute pression comprenant ledit joint d'étanchéité
US8590442B2 (en) 2007-12-06 2013-11-26 Robert Bosch Gmbh Gasket for high-pressure pump and high-pressure pump comprising said gasket
WO2009135709A1 (fr) * 2008-05-06 2009-11-12 Robert Bosch Gmbh Pompe à carburant haute pression pour faire fonctioner un moteur à combustion interne
WO2012038198A1 (fr) * 2010-09-22 2012-03-29 Robert Bosch Gmbh Pompe haute pression et procédé pour produire un corps de pompe
WO2017220696A1 (fr) * 2016-06-23 2017-12-28 Delphi International Operations Luxembourg S.À R.L. Joint d'étanchéité d'une plaque avant d'une pompe haute pression

Also Published As

Publication number Publication date
EP1184572A3 (fr) 2003-03-19
DE50114019D1 (de) 2008-07-24
DE10042305A1 (de) 2002-03-21
EP1184572B1 (fr) 2008-06-11

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