EP1184572B1 - Joint d'étanchéité haute pression - Google Patents

Joint d'étanchéité haute pression Download PDF

Info

Publication number
EP1184572B1
EP1184572B1 EP01117578A EP01117578A EP1184572B1 EP 1184572 B1 EP1184572 B1 EP 1184572B1 EP 01117578 A EP01117578 A EP 01117578A EP 01117578 A EP01117578 A EP 01117578A EP 1184572 B1 EP1184572 B1 EP 1184572B1
Authority
EP
European Patent Office
Prior art keywords
high pressure
sealing device
pressure seal
seal
transition area
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.)
Expired - Lifetime
Application number
EP01117578A
Other languages
German (de)
English (en)
Other versions
EP1184572A2 (fr
EP1184572A3 (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
Continental Automotive 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 Continental Automotive GmbH filed Critical Continental Automotive GmbH
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

Links

Images

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 region to high-pressure components, and more particularly to a sealing device for transition areas on pump components of pumps for common-rail systems.
  • FIG. 11 a known high-pressure seal 1 shown for a common rail system, which is used at a transition region 5 between a first component 2 and a second component 3, to allow a continuation of a fluid channel 6.
  • high-pressure seal 1 consists of two elements, namely a sealing ring 24 and a support ring 25, which are arranged in a recess 4 which is formed in the first component 2.
  • the sealing ring 24 is made of an elastomer.
  • the support ring 25 is arranged on the outer circumference of the sealing ring 24 in order to support the sealing ring 24 against the high pressures in the common rail.
  • the support ring has no sealing function.
  • a valve 26 is arranged, which consists essentially of a valve ball 22, a spring element 27 and a basket-shaped ball cage 28 formed.
  • Another seal for sealing a transition region on high pressure components is for example from DE 196 53 339 A1 known.
  • the known high-pressure seal consists of at least two components, namely the sealing ring and the support ring, resulting in relatively high manufacturing and assembly costs. Moreover, the known high-pressure seals only to a limited extent against aggressive media, such as plant methyl ester (PME), resistant.
  • aggressive media such as plant methyl ester (PME), resistant.
  • a sealing device for sealing high-pressure components at a transition region on a high-pressure line which comprises a high-pressure seal with a substantially annular shape and a low-pressure seal.
  • the high-pressure seal is arranged on a line transition of the high-pressure components.
  • the low-pressure seal is arranged outside the high-pressure seal in order to securely seal any leakage occurring through the high-pressure seal to the outside.
  • a redundant sealing system is provided which can reliably prevent leakage of fluid at transition areas of high pressure components. Therefore, if leakage occurs through the high pressure seal these are retained by the low pressure seal.
  • the combination of a high pressure seal and a low pressure seal can reliably prevent leakage.
  • the present invention can be used in a common rail system at transitions of pump components.
  • the high pressure seal is made of metal. Furthermore, the high pressure seal made of metal according to the invention is prestressed in the mounted state. It can thereby be achieved that the high-pressure seal rests after assembly due to their bias with high pressure at their contact surfaces for sealing. Thus, a seal is provided by the high pressure seal according to the invention, which ensures a sufficient seal over the entire temperature range, without leaks, especially in the lower temperature range occur. Further, the combination of biasing the gasket and the sealing ring made of metal provides a high pressure dynamic load seal which in particular can follow pressure pulsations at a high frequency and thus have no leakage due to stress pulses caused by the fluid. Furthermore, the high-pressure seal according to the invention also requires no support ring, since it has sufficient strength against the high pressures due to its production from a metal. Moreover, the high pressure seal made of metal is resistant to aggressive media.
  • the high pressure seal is made of spring steel or steel.
  • a low-cost and easy to produce high-pressure seal can be obtained.
  • a particularly simple bias of the seal can be realized.
  • the high-pressure seal is made of heat-resistant plastic or of rubber.
  • an elastomer is used as the plastic.
  • the low pressure seal is made of metal or of plastic or rubber or of a plastic coated metal.
  • the low-pressure seal is preferably designed as a flat gasket or as a profile gasket. Particularly preferably, the low-pressure seal has a bead.
  • the high-pressure seal is designed as a ring with a C-shaped cross-section.
  • the open area of the C-shaped ring is directed inwards.
  • the C-shaped design of the high-pressure seal can be achieved in particular that the seal is additionally pressed by the fluid pressure with great force against their contact surfaces, since the fluid pressure is directed in the direction of the contact surface.
  • the existing due to the bias of the seal contact pressure is reinforced by the geometric design of the seal in C-shape.
  • the C-ring high-pressure seal can also compensate for component deformations, which arise due to the high pressures, since it can easily follow the deformations, in particular the widths and approaches, of adjacent components due to the high pressure due to its C-shape.
  • the cross-section C-shaped high-pressure seal has a symmetrical shape, so that u.a. a mix-proof installation is guaranteed.
  • the high-pressure seal has two sealing surfaces or three sealing surfaces.
  • the seal may be arranged such that it has an upper and a lower abutment surface for sealing. Further, it is also possible that a third contact surface is formed by the outwardly directed circular portion of the C-shaped sealing ring.
  • the high-pressure seal is designed as a ring with an angular cross-section.
  • this so-called wedge ring in the uninstalled state has a leg angle, i. an angle between its two thighs, of significantly greater than 90 °.
  • this leg angle in the uninstalled state is about 115 °.
  • the leg angle of the wedge ring in the installed state is significantly smaller than in the uninstalled state and is about 90 ° to 95 °.
  • the metal wedge ring is e.g. a sheet metal (spring plate) made.
  • the high-pressure seal preferably has a region which tapers in cross-section.
  • a wedge-shaped seal can be provided.
  • the wedge-shaped surface of the seal is directed to the inside of the seal.
  • the tapered region is parabolic or rectilinear in section.
  • the high-pressure seal preferably has a region with a constant inner and outer diameter in addition to the tapered region. As a result, in particular one of the bearing surfaces can be made relatively large for sealing.
  • the high-pressure seal on a central connection region, which has at least one passage opening.
  • the middle connection area connects the outer ring areas of the gasket with each other. This can increase the stability of the high pressure seal.
  • the high pressure seal is button-shaped.
  • the high-pressure seal has a flat circular central connection region, so that the high-pressure seal, e.g. can be used as a cage or stop for a valve body.
  • the high-pressure seal is combined with a cage for a valve body in order to retain a valve body.
  • the high-pressure seal has both a sealing function and a retaining function for a valve body of a valve arranged immediately before the seal.
  • the button-shaped high pressure seal with four through holes is provided to ensure sufficient fluid flow.
  • the middle connection region is formed on a cross-sectionally C-shaped ring at one end in the vertical direction. This allows the advantages of the C-shaped high-pressure seal to be combined with those of the middle connection area.
  • the middle connection area serves as a stop for the valve body.
  • the present invention provides a redundant sealing device by a combination of a high pressure seal ready with a low pressure seal.
  • the sealing device has a simple construction and allows reliable sealing over the entire temperature range in which the combination seal is used without leakage problems, in particular in the low temperature range. This is further enhanced by the further combination of a high pressure seal made of metal and the bias of the seal so that excellent sealing properties can be provided. Furthermore, insensitivity to load pulses occurring in the conveying fluid is achieved by the sealing device according to the invention, which was not given in the elastomer seals used previously.
  • the sealing system according to the invention can also be used as a cage or stop for a valve body and is resistant to aggressive media.
  • the seal assembly according to the invention is used in common rail systems in which a relatively high pressure is present.
  • a high-pressure seal 1 is shown for a sealing device according to a first embodiment of the present invention.
  • the high-pressure seal 1 is arranged at a transition region 5 between a first component 2 (for example a cylinder) and a second component 3 (for example a cylinder head).
  • a recess 4 for receiving the high-pressure seal 1 is provided on the first component 2 (see. FIG. 1 ).
  • the recess 4 is formed around the mouth of the fluid channel 6 around.
  • the high pressure seal 1 must seal the transition region 5 around the fluid passage 6 to prevent leakage of fluid.
  • the high-pressure seal 1 has an annular shape.
  • the high-pressure seal 1 has a C-shaped cross-section.
  • the high-pressure seal 1 has a first straight section 7, a curved section 8 and a second straight section 9.
  • the two straight sections 7 and 9 rest 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 portion 8 is formed so as to come into contact with the side wall of the recess 4, thus forming an additional third seal portion 30.
  • the C-shaped high-pressure seal is formed completely curved, that is formed without straight sections or such that it only two sealing areas, for. B. the two sealing regions 10 and 11, has.
  • the C-shaped high pressure seal 1 has a constant thickness over its entire cross section. However, it is also possible that the high-pressure seal, in particular if they are made of sheet metal or similar. is manufactured, has different thicknesses in cross section.
  • the high-pressure seal 1 in the vertical direction, i. in the direction of the central axis 0-0, at its one end an inner diameter D1 and at its other end an inner diameter D2.
  • the inner diameter D1 is equal to the inner diameter D2, so that the high-pressure seal 1 is formed symmetrically.
  • the high-pressure seal 1 of the first embodiment is made of spring steel and the two straight sections 7 and 9 are biased outwardly so that they are pressed in the installed state against the wall surfaces of the first and second components 2 and 3. Due to the concave arrangement of the curved region 8 to the fluid channel 6, the fluid pressure supports the pressing of the straight portions 7 and 9 against the respective contact surfaces of the first and second component.
  • the C-ring high-pressure seal 1 is constructed symmetrically and has at its two ends in the vertical direction the same inner diameter D1 and D2, the pressure forces at all points of the high-pressure seal 1 are the same. Thus, a secure seal of the transition region 5 can be achieved. Since the bias of the high-pressure seal 1 over the entire temperature range is present, a sufficient seal is ensured even at low temperatures. Furthermore, it is also possible to easily record high-frequency pressure pulsations in the fluid and to compensate for component deformations as a result of the high pressure. Furthermore, the symmetrical construction of the high-pressure seal 1 ensures a mix-proof installation and the high-pressure seal is resistant to aggressive media.
  • FIG. 3 shows the sealing device according to the invention with the C-ring high pressure seal 1 according to the first embodiment shown.
  • the sealing device includes the high pressure seal and a low pressure seal 12.
  • the high-pressure seal 1 seals a transition region between a cylinder block 2 and a cylinder head 3 on a fluid channel 6.
  • the high-pressure seal 1 is inserted into an annular recess 4 formed on the cylinder block 2.
  • the low-pressure seal 12 designed as a flat seal is furthermore arranged.
  • the low-pressure seal 12 is a sheet coated with an elastomer and may additionally have a bead.
  • the transition region at the fluid channel 6 is sealed twice by the sealing device, namely by the high-pressure seal 1 and the low-pressure seal 12.
  • the two seals 1 and 12 of the sealing device lie substantially in one plane at the transition region 5.
  • a gap or slot 29 is formed.
  • possible leakage through the high pressure seal 1 via the gap 29 in the low pressure seal 12 is supplied to the low pressure region of the system. Since the gap 29 is formed at a middle intermediate region of the low-pressure seal 12, it is further ensured that the low-pressure seal 12 completely surrounds the high-pressure seal 1 and thus a redundant seal is present.
  • FIG. 4 a sealing device according to a second embodiment is shown.
  • the second embodiment substantially corresponds to the in FIG. 3 shown first embodiment.
  • a molded seal or profile seal 12 is provided instead of the flat gasket, which is inserted into a corresponding recess 13 on the cylinder block 2.
  • the molded seal 12 is arranged outside the high-pressure seal 1, so that a direct connection is ensured from the high-pressure seal 1 to the low-pressure region.
  • FIGS. 5 and 6 there is shown a high pressure seal 1 for use in a sealing device according to a third embodiment of the present invention.
  • Identical or functionally identical parts are denoted by the same reference numerals as in the first embodiment. Since the third embodiment substantially corresponds to the first embodiment, only the differences between the two embodiments will be described below in detail.
  • the high-pressure seal 1 for a sealing device is arranged at a transition region 5 of a fluid channel 6 between a first component 2 and a second component 3.
  • the high-pressure seal 1 is as in FIGS. 5 and 6 shown, button-shaped design.
  • a C-annular edge region 16 on one of its sides in the vertical direction ie in the direction of the center line 0-0
  • the C-shaped edge portion 16 formed by a first straight portion 7, a curved portion 8 and a second straight portion 9 is connected to the middle connecting portion 17 at its second straight portion 9.
  • the second straight section 9 merges into the middle connection region.
  • the section 7 can also be curved.
  • the middle connecting region 17 four through holes 18, 19, 20 and 21 are formed.
  • the passage openings ensure fluid passage through the button-shaped high-pressure seal 1. It is of course possible to form a different number of through holes.
  • a valve ball 22 is further provided at the transition region of the fluid channel 6, which on a Valve seat 23 is present.
  • a valve is formed by the button-shaped high-pressure seal 1 and the valve ball 22 at the transition region of the fluid channel 6.
  • the button-shaped high-pressure seal 1 forms the ball cage for the valve ball 22.
  • the portion of the center connecting portion 17 located in the region of the center line 0-0 has a greater thickness than the edge region 16 in order to provide sufficient strength for the retention of the valve ball 22.
  • the high-pressure seal 1 for a sealing device also has a retaining function for the valve ball 22.
  • the high pressure seal 1 is made of metal, e.g. made of spring steel, can be made. It is also possible to arrange a spring element between the high-pressure seal serving as a cage and the valve ball, so that a check valve is arranged in the fluid passage 6 between the first and the second component.
  • FIGS. 7 and 8 a high-pressure seal 1 is shown for a sealing device according to a fourth embodiment of the present invention. Identical or functionally identical parts are denoted by the same reference numerals as in the previously described embodiments. Since the fourth embodiment substantially corresponds to the previously described embodiments, only the differences from the embodiments will be described below in detail.
  • the high-pressure seal 1 is arranged at a transition region 5 between a first component 2 and a second component 3. In this case, it is positioned in a recess 4, which is formed in the first component 2 and seals a transition of a fluid channel 6 from.
  • the high-pressure seal 1 has a first region 14 and a second region 15.
  • the first region 14 has a constant inside and outside diameter and accordingly has a rectangular shape in section. However, the first region 14 may also have different inside and outside diameters.
  • the second region 15 tapers from the first region 14 to its outside. As in FIG. 7 shown, the tapered portion 15 is formed parabolic in section.
  • the wedge-shaped high-pressure seal 1 is pretensioned to one side.
  • the prestressing of the wedge-shaped sealing ring 1 made of spring steel takes place in the direction of the second region 15.
  • the high-pressure seal 1 is pressed against the regions 10 and 11 and the region 30 extending in the direction of the center line 0-0 the recess 4.
  • the sealing portions 10 and 30 of the seal 1 in the unmounted state to each other at an angle greater than 90 ° - 95 ° are arranged.
  • the sealing regions 10 and 30 are then arranged at an angle of 90 ° - 95 ° to each other.
  • a pressure is additionally exerted by the fluid on the high-pressure seal 1, in particular in the direction of the sealing regions 10 and 30.
  • a relatively large chamfer 16 is further formed on the outside of the second tapered portion 15 to allow easier assembly.
  • the high-pressure seal 1 also provides a sufficient sealing function at very high pressures and is insensitive to high-frequency pressure pulsations occurring in the fluid and resistant to PME fluids.
  • FIGS. 9 and 10 a high-pressure seal 1 is shown for a sealing device according to a fifth embodiment of the present invention. Identical or functionally identical parts are denoted by the same reference numerals as in the previously described embodiments. Since the fifth embodiment substantially corresponds to the previously described embodiments, only the differences from the embodiments will be described below in detail.
  • the high-pressure seal 1 is designed for the sealing device as a so-called wedge seal.
  • the wedge seal 1 is annular and comprises a first leg 31 and a second leg 32.
  • the two legs 31 and 32 have an equal length. However, they can also have different lengths.
  • the high-pressure seal 1 is arranged in a recess 2 provided in the component 2.
  • the depth of the recess 4 substantially corresponds to the leg length of the leg 32
  • FIG. 9 the high-pressure seal 1 is shown in an intermediate assembly step.
  • the high-pressure seal 1 is inserted into the recess 4.
  • two side surfaces of the seal 1 bear against the walls of the recess 4 and form sealing regions 11 and 30 (cf. FIGS. 9 and 10 ).
  • the first leg 31 forms a further sealing region 10 with the component 3.
  • the angle ⁇ between the first leg 31 and the second leg 32 is significantly greater than 90 °.
  • the angle ⁇ is about 115 °.
  • the second leg 32 is pressed against the surface of the recess 4 in an area denoted by 11, and the first leg in the area 10 is pressed against the component 3.
  • the angle between the two legs reduces to ⁇ 'of about 90 ° - 95 ° (see. FIG. 10 ). If ⁇ 'is exactly 90 °, the one side of the leg 31 is completely against the component 3.
  • the wedge ring 1 exerts a bias in the mounted state on the components 2 and 3, whereby the tightness of the seal 1 is increased.
  • sealing device according to the invention can be formed from any combination of the previously described high-pressure seals or low-pressure seals.
  • the present invention relates to a sealing device with a high-pressure seal 1 and a low-pressure seal 12 for sealing a transition region 5 on a high-pressure line 6, which is used in particular 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 arranged in a plane with the high-pressure seal 1 around it in order to seal any leakage occurring through the high-pressure seal 1 to the outside.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Gasket Seals (AREA)

Claims (21)

  1. Dispositif d'étanchéité pour rendre étanche une région de jonction (5) sur des éléments à haute pression (2, 3) comprenant un joint à haute pression (1) qui présente une conformation sensiblement annulaire et qui peut être disposé au niveau d'une jonction de conduite des éléments à haute pression (2, 3), caractérisé en ce qu'en supplément, est prévu un joint à basse pression (12), le joint à basse pression (12) étant disposé autour du joint à haute pression (1) pour étanchéifier vers l'extérieur une fuite qui se produirait éventuellement à travers le joint à haute pression (1).
  2. Dispositif d'étanchéité pour une région de jonction (5) sur des éléments à haute pression (2, 3) selon la revendication 1, caractérisé en ce que le joint à haute pression (1) est fabriqué en métal et présente une précontrainte à l'état monté.
  3. Dispositif d'étanchéité pour une région de jonction (5) sur des éléments à haute pression (2, 3) selon la revendication 2, caractérisé en ce que le joint à haute pression (1) est fabriqué en tôle ressort ou en acier.
  4. Dispositif d'étanchéité pour une région de jonction (5) sur des éléments à haute pression (2, 3) selon la revendication 1, caractérisé en ce que le joint à haute pression (1) est fabriqué en matière plastique, en particulier en un élastomère ou en caoutchouc.
  5. Dispositif d'étanchéité pour une région de jonction (5) sur des éléments à haute pression (2, 3) selon une des revendications 1 à 4, caractérisé en ce que le joint à basse pression (12) est fabriqué en métal, en matière plastique, en caoutchouc ou en un métal revêtu de matière plastique.
  6. Dispositif d'étanchéité pour une région de jonction (5) sur des éléments à haute pression (2, 3) selon une des revendications 1 à 4, caractérisé en ce que le joint à basse pression (12) est constitué par un joint plat ou un joint profilé.
  7. Dispositif d'étanchéité pour une région de jonction (5) sur des éléments à haute pression (2, 3) selon une des revendications 1 à 6, caractérisé en ce que, dans le joint à basse pression (12), est formée une fente (29) pour évacuer une fuite s'échappant du joint à haute pression (1).
  8. Dispositif d'étanchéité pour une région de jonction (5) sur des éléments à haute pression (2, 3) selon une des revendications 1 à 7, caractérisé en ce que le joint à haute pression (1) est constitué par une bague (7, 8, 9) possédant une section transversale en forme de C.
  9. Dispositif d'étanchéité pour une région de jonction (5) sur des éléments à haute pression (2, 3) selon la revendication 8, caractérisé en ce que le joint à haute pression (1) en forme de C en section transversale est de configuration symétrique.
  10. Dispositif d'étanchéité pour une région de jonction (5) sur des éléments à haute pression (2, 3) selon la revendication 8 ou 9, caractérisé en ce que le joint à haute pression (1) présente deux surfaces d'étanchéité (10, 11) ou trois surfaces d'étanchéité comportant un contact linéaire.
  11. Dispositif d'étanchéité pour une région de jonction (5) sur des éléments à haute pression (2, 3) selon une des revendications 1 à 7, caractérisé en ce que le joint à haute pression (1) est constitué par une bague ayant une section en forme d'angle.
  12. Dispositif d'étanchéité pour une région de jonction (5) sur des éléments à haute pression (2, 3) selon la revendication 11, caractérisé en ce que l'angle (α) entre deux branches (31, 32) de la bague est supérieur à 95° à l'état non monté et est compris entre 90° et 95° à l'état monté.
  13. Dispositif d'étanchéité pour une région de jonction (5) sur des éléments à haute pression (2, 3) selon une des revendications 1 à 12, caractérisé en ce que le joint à haute pression (1) présente une région (15) qui s'amincit en section transversale.
  14. Dispositif d'étanchéité pour une région de jonction (5) sur des éléments à haute pression (2, 3) selon la revendication 13, caractérisé en ce que la région (15) qui s'amincit présente en coupe une forme de parabole ou en ligne droite.
  15. Dispositif d'étanchéité pour une région de jonction (5) sur des éléments à haute pression (2, 3) selon une des revendications 1 à 14, caractérisé en ce que le joint à haute pression (1) présente une région (14) ayant un diamètre intérieur et un diamètre extérieur constants.
  16. Dispositif d'étanchéité pour une région de jonction (5) sur des éléments à haute pression (2, 3) selon une des revendications 1 à 15, caractérisé en ce que le joint à haute pression (1) présente une région de liaison centrale (17) qui présente au moins une ouverture de passage (18, 19, 20, 21).
  17. Dispositif d'étanchéité pour une région de jonction (5) sur des éléments à haute pression (2, 3) selon la revendication 16, caractérisé en ce qu'il est prévu quatre ouvertures de passage (18, 19, 20, 21).
  18. Dispositif d'étanchéité pour une région de jonction (5) sur des éléments à haute pression (2, 3) selon la revendication 16 ou 17, caractérisé en ce que le joint à haute pression (1) est en forme de bouton.
  19. Dispositif d'étanchéité pour une région de jonction (5) sur des éléments à haute pression (2, 3) selon une des revendications 16 à 18, caractérisé en ce que la région de liaison centrale (17) est formée à une extrémité, dans la direction verticale, d'une bague en forme de C en section transversale (7, 8, 9).
  20. Dispositif d'étanchéité pour une région de jonction (5) sur des éléments à haute pression (2, 3) selon une des revendications 16 à 19, caractérisé en ce que la région de liaison centrale (17) constitue une butée pour un élément de soupape (22).
  21. Dispositif d'étanchéité pour une région de jonction (5) sur des éléments à haute pression (2, 3) selon une des revendications 16 à 20, caractérisé en ce que la région de liaison centrale (17) présente une section transversale plus épaisse que d'autres régions du joint à haute pression (1).
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 EP1184572A2 (fr) 2002-03-06
EP1184572A3 EP1184572A3 (fr) 2003-03-19
EP1184572B1 true 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)

Families Citing this family (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE10253189A1 (de) * 2002-11-15 2004-05-27 Robert Bosch Gmbh Radialkolbenpumpe mit flächiger Dichtung zwischen Flansch und Gehäuse
DE10310123A1 (de) * 2003-03-07 2004-09-23 Siemens Ag Radialkolbenpumpe
DE102005023226B4 (de) 2005-05-20 2019-05-16 Audi Ag Maschinenbauteilanordnung mit einer Flachdichtung und Flachdichtung
ITMI20072300A1 (it) * 2007-12-06 2009-06-07 Bosch Gmbh Robert Guarnizione per pompa di alta pressione e pompa di alta pressione comprendente tale guarnizione
EP2072818A1 (fr) 2007-12-21 2009-06-24 Reinz-Dichtungs-GmbH & Co. KG Joint plat métallique et son utilisation
DE102008001587A1 (de) * 2008-05-06 2009-11-12 Robert Bosch Gmbh Hochdruckkraftstoffpumpe zum Betrieb einer Brennkraftmaschine
DE102010041213A1 (de) * 2010-09-22 2012-03-22 Robert Bosch Gmbh Hochdruckpumpe und Verfahren zum Herstellen eines Pumpengehäuses
GB2551562B (en) * 2016-06-23 2020-03-18 Delphi Tech Ip Ltd Gasket of a front plate of a high pressure pump

Citations (1)

* 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

Family Cites Families (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
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
JP4088738B2 (ja) * 1998-12-25 2008-05-21 株式会社デンソー 燃料噴射ポンプ

Patent Citations (1)

* 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

Also Published As

Publication number Publication date
EP1184572A2 (fr) 2002-03-06
DE10042305A1 (de) 2002-03-21
EP1184572A3 (fr) 2003-03-19
DE50114019D1 (de) 2008-07-24

Similar Documents

Publication Publication Date Title
DE4030484C2 (de) Verbindungsanordnung für ein abzweigendes Anschlußstück in einer Hochdruck-Kraftstoffschiene
DE10119534B4 (de) Metallische Dichtung
DE2920983C2 (de) Anordnung zur druckdichten Befestigung eines Schlauches auf einem Nippel
EP2492569A2 (fr) Liaison pour manchon
WO2007131468A1 (fr) Structure d'étanchéite pour décompression
EP1184572B1 (fr) Joint d'étanchéité haute pression
EP3824207B1 (fr) Soupape de levage et joint d'étanchéité
EP0832382B1 (fr) Bague d'etancheite pour milieu gazeux
DE102008008435B4 (de) Federbelastetes Ventil und Verfahren zur Einstellung einer Ventilbaugruppe eines federbelasteten Ventils
DE20300918U1 (de) Pressverbindungsanordnung
DE60214775T2 (de) Flanschglied mit einem ersten flanschende, das in einer radialrichtung mit einer konkaven endfläche ausgeführt ist, und einer flanschgliederumfassenden flanschverbindung
AT501851B1 (de) Verbindung von leitungen für hochdruckmedien
EP2436960A2 (fr) Agencement de douille d'étanchéité et appareil hydraulique
EP3324083B1 (fr) Agencement d'étanchéité et son utilisation
EP0412997A1 (fr) Garniture d'etancheite.
DE102007041950B4 (de) Ventilanordnung, für eine hydrostatische Kolbenmaschine
DE102007054830A1 (de) Hydraulischer Anschluss für ein Fluidelement und Verfahren zu seiner Herstellung
EP3839316A1 (fr) Pièce d'accouplement pour un accouplement de tuyau
WO2003098090A1 (fr) Collier d'attache pour tuyaux
DE2837977A1 (de) Schwenkverschraubung
DE102014209182A1 (de) Kraftstoffzuleitungseinrichtung an einem Kraftstoffinjektor und Kraftstoffinjektor
EP3135917B1 (fr) Pompe à vide
DE2045132C3 (de) Dichtungsring für ineinander steckbare Rohre hoher thermischer Belastung
EP3502524A1 (fr) Joint d'étanchéité à anneau glissant ainsi que groupe turbogénérateur doté d'un tel joint d'étanchéité à anneau glissant
DE10331381A1 (de) Pressverbindung und Stützhülse für eine Pressverbindung

Legal Events

Date Code Title Description
PUAI Public reference made under article 153(3) epc to a published international application that has entered the european phase

Free format text: ORIGINAL CODE: 0009012

AK Designated contracting states

Kind code of ref document: A2

Designated state(s): AT BE CH CY DE DK ES FI FR GB GR IE IT LI LU MC NL PT SE TR

AX Request for extension of the european patent

Free format text: AL;LT;LV;MK;RO;SI

PUAL Search report despatched

Free format text: ORIGINAL CODE: 0009013

AK Designated contracting states

Kind code of ref document: A3

Designated state(s): AT BE CH CY DE DK ES FI FR GB GR IE IT LI LU MC NL PT SE TR

AX Request for extension of the european patent

Extension state: AL LT LV MK RO SI

17P Request for examination filed

Effective date: 20030407

AKX Designation fees paid

Designated state(s): DE FR GB IT

17Q First examination report despatched

Effective date: 20060905

GRAP Despatch of communication of intention to grant a patent

Free format text: ORIGINAL CODE: EPIDOSNIGR1

GRAS Grant fee paid

Free format text: ORIGINAL CODE: EPIDOSNIGR3

GRAA (expected) grant

Free format text: ORIGINAL CODE: 0009210

RAP1 Party data changed (applicant data changed or rights of an application transferred)

Owner name: CONTINENTAL AUTOMOTIVE GMBH

AK Designated contracting states

Kind code of ref document: B1

Designated state(s): DE FR GB IT

REG Reference to a national code

Ref country code: GB

Ref legal event code: FG4D

Free format text: NOT ENGLISH

REF Corresponds to:

Ref document number: 50114019

Country of ref document: DE

Date of ref document: 20080724

Kind code of ref document: P

PLBE No opposition filed within time limit

Free format text: ORIGINAL CODE: 0009261

STAA Information on the status of an ep patent application or granted ep patent

Free format text: STATUS: NO OPPOSITION FILED WITHIN TIME LIMIT

26N No opposition filed

Effective date: 20090312

GBPC Gb: european patent ceased through non-payment of renewal fee

Effective date: 20080911

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: IT

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20080611

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: GB

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20080911

REG Reference to a national code

Ref country code: FR

Ref legal event code: PLFP

Year of fee payment: 16

REG Reference to a national code

Ref country code: FR

Ref legal event code: PLFP

Year of fee payment: 17

REG Reference to a national code

Ref country code: FR

Ref legal event code: PLFP

Year of fee payment: 18

PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: AT

Payment date: 20180821

Year of fee payment: 7

REG Reference to a national code

Ref country code: DE

Ref legal event code: R084

Ref document number: 50114019

Country of ref document: DE

REG Reference to a national code

Ref country code: DE

Ref legal event code: R081

Ref document number: 50114019

Country of ref document: DE

Owner name: VITESCO TECHNOLOGIES GMBH, DE

Free format text: FORMER OWNER: CONTINENTAL AUTOMOTIVE GMBH, 30165 HANNOVER, DE

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: FR

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20190731

PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: DE

Payment date: 20200731

Year of fee payment: 20

REG Reference to a national code

Ref country code: DE

Ref legal event code: R071

Ref document number: 50114019

Country of ref document: DE