EP1972779B1 - Coupleur hydraulique - Google Patents

Coupleur hydraulique Download PDF

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Publication number
EP1972779B1
EP1972779B1 EP20080101550 EP08101550A EP1972779B1 EP 1972779 B1 EP1972779 B1 EP 1972779B1 EP 20080101550 EP20080101550 EP 20080101550 EP 08101550 A EP08101550 A EP 08101550A EP 1972779 B1 EP1972779 B1 EP 1972779B1
Authority
EP
European Patent Office
Prior art keywords
coupler
hydraulic
sealing element
region
coupler part
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 - Fee Related
Application number
EP20080101550
Other languages
German (de)
English (en)
Other versions
EP1972779A1 (fr
Inventor
Dietmar Schmieder
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Robert Bosch GmbH
Original Assignee
Robert Bosch GmbH
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Robert Bosch GmbH filed Critical Robert Bosch GmbH
Publication of EP1972779A1 publication Critical patent/EP1972779A1/fr
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Expired - Fee Related legal-status Critical Current
Anticipated expiration legal-status Critical

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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
    • F02M51/00—Fuel-injection apparatus characterised by being operated electrically
    • F02M51/06—Injectors peculiar thereto with means directly operating the valve needle
    • F02M51/0603—Injectors peculiar thereto with means directly operating the valve needle using piezoelectric or magnetostrictive operating means
    • 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
    • F02M61/00—Fuel-injectors not provided for in groups F02M39/00 - F02M57/00 or F02M67/00
    • F02M61/16—Details not provided for in, or of interest apart from, the apparatus of groups F02M61/02 - F02M61/14
    • F02M61/167—Means for compensating clearance or thermal expansion
    • 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
    • F02M2200/70—Linkage between actuator and actuated element, e.g. between piezoelectric actuator and needle valve or pump plunger
    • F02M2200/703—Linkage between actuator and actuated element, e.g. between piezoelectric actuator and needle valve or pump plunger hydraulic
    • F02M2200/705—Linkage between actuator and actuated element, e.g. between piezoelectric actuator and needle valve or pump plunger hydraulic with means for filling or emptying hydraulic chamber, e.g. for compensating clearance or thermal expansion
    • F02M2200/706—Valves for filling or emptying hydraulic chamber

Definitions

  • the present invention relates to a hydraulic coupler, and more particularly to a hydraulic coupler for an injector for injecting a fuel.
  • Hydraulic couplers for injectors are known from the prior art in various configurations. Such hydraulic couplers have u.a. the task to compensate occurring during operation of the injector length changes of components.
  • the known couplers use at least two corrugated bellows for sealing a coupler volume.
  • this construction makes the coupler volume very large. This leads to large axial strokes of a piston of the coupler occurring during temperature changes. However, this results in the operation of the injector large drag losses, i. Oil losses due to axial movement.
  • the known couplers consist of a plurality of individual parts, and in particular the corrugated bellows, which ensure the mobility of the coupler, lead to very high production costs. It would therefore be desirable to have a coupler, which can be produced in addition to a simple structure in particular also cost.
  • a hydraulic coupler which comprises a first coupler part and a second coupler part and a coupler space arranged between the first coupler part and the second coupler part and which is filled with a coupler medium. Furthermore, the hydraulic coupler has a sealing element, which seals in a certain way the coupler space.
  • the sealing element is designed as a membrane-like flexible portion which is resilient and is deformed in the operating condition. A biasing force can be exerted on the sealing element with a spring to produce a predetermined pressure on the coupling medium in the compensation space.
  • the sealing element is arranged as a cup-shaped membrane such that it covers the two coupler parts on the side opposite the coupler space.
  • the hydraulic coupler according to the invention with the features of claim 1, in contrast, has the advantage that it does not require Wellbälge.
  • the hydraulic coupler according to the invention can be provided very inexpensively.
  • the coupler according to the invention has a simple and compact construction, which guarantees a long service life.
  • the hydraulic coupler according to the present invention has only a very small coupler volume, which results in virtually no losses of the coupler medium during operation.
  • the hydraulic coupler according to the present invention comprises a first coupler part and a second coupler part, and a coupler space disposed between the first and second coupler parts, which is filled with the coupler medium.
  • a sealing element for sealing the coupler space and a biasing means is provided, which exerts a biasing force on the sealing element, thereby to generate a predetermined pressure of the coupling medium in the coupler space.
  • the sealing element of the coupler according to the invention additionally has the function of generating the coupler pressure in the coupler medium.
  • the coupler according to the invention can have only a minimal number of individual parts and it is also possible to choose an enlarged piston diameter for the first and second coupler part. This leads to a significant improvement in the function of the hydraulic coupler.
  • the sealing element is arranged in an annular gap between the first coupler part and the second coupler part and seals there.
  • the sealing element is annular. This allows a particularly simple and inexpensive sealing element can be used.
  • the biasing means which exerts the biasing force on the sealing element, a spring, in particular a cylindrical spring.
  • the hydraulic coupler preferably further comprises a pressure plate, which is on the one hand with the sealing element and on the other hand with the biasing means in contact.
  • the thrust washer further ensures that the biasing means does not damage the sealing element.
  • the pressure disk preferably has an inner guide region on a radial inner side and an outer guide region on a radial outer side.
  • the inner guide region is in contact with the first coupler part and the outer guide region is in contact with the second coupler part.
  • the thrust washer can additionally assume a guiding function and a bearing function between the first coupler part and the second coupler part.
  • the hydraulic coupler comprises a spring plate, which is fixed to the first coupler part and supports one end of the biasing device.
  • the spring plate is preferably connected to the first coupler part by a press fit or a weld or an adhesive bond or a solder joint.
  • the biasing force can be changed to the coupler fluid.
  • the sealing element comprises an annular lip seal with an inner sealing lip and an outer sealing lip.
  • an annular recess is arranged between the inner sealing lip and the outer sealing lip. This recess is filled with coupler fluid, so that the pressure of the coupler fluid in particular acts in the radial direction of the inner and outer sealing lips.
  • the pressure disk has an inner groove-shaped recess and an outer groove-shaped recess.
  • the sealing element comprises a first sealing ring and a second sealing ring, wherein the first sealing ring is arranged in the inner groove-shaped recess and the second sealing ring in the outer groove-shaped recess.
  • simple sealing rings for the sealing element can be used, which can be mounted in a particularly simple and secure manner in the pressure disk. This embodiment is not part of the claimed subject matter.
  • the first piston part is designed as a stepped piston, wherein the stepped piston has a central first bore, a central second bore with a smaller diameter than the central first bore, a radial third bore, a lateral fourth bore parallel to the first bore and a throttle bore.
  • the throttle bore is located at the end of the fourth bore.
  • the hydraulic coupler further comprises a cover which partially seals at least the biasing means. This ensures a long life of the hydraulic coupler.
  • FIG. 1 a hydraulic coupler 1 according to a first preferred embodiment of the invention described in detail.
  • the hydraulic coupler 1 comprises a first coupler part 2 and a second coupler part 3.
  • the first coupler part 2 comprises a piston region 20 and an elongated shaft region 21 formed integrally thereon.
  • the first coupler part 2 is thus designed as a stepped piston.
  • the second coupler part 3 comprises a cylinder region 30 and a connecting region 31 formed integrally thereon.
  • the connecting region 31 serves for connection to a further component.
  • the second coupler part 3 as in FIG FIG. 1 shown, the first coupler part 2 in the cylinder portion 30 in itself.
  • a cylindrical coupler space 4 is formed between the first coupler part 2 and the second coupler part 3, a cylindrical coupler space 4 is formed.
  • the coupler space 4 is filled with a coupler medium, such as oil.
  • the first coupler part 2 comprises a first central bore 22 having a first diameter D1 along a central axis XX, a second central bore 23 having a second diameter D2, the second diameter D2 being smaller than the first diameter D1.
  • the first coupler part 2 comprises a third radial bore 24, which is formed perpendicular to the second bore 23, a fourth bore 25, which in turn is formed perpendicular to the third bore 24 and parallel to the first and second bore is located, and a throttle bore 26, which opens at an end face 2a of the first coupler part 2.
  • the plurality of holes in the first coupler part 2 are connected to the coupler space 4 and together with the coupler space 4 form the coupler volume of the hydraulic coupler.
  • a sealing element 5 is provided for sealing between the first coupler part 2 and the second coupler part 3, as in FIG. 1 seen.
  • the sealing element 5 is a sealing ring which seals with a radial inner side on the shaft region 21 of the first coupler part and with a radial outer side on the inner side of the cylinder region 30 of the second coupler part 3.
  • an annular space is formed between the sealing element 5 and the step-shaped first coupler part 2, which is also filled with coupler medium and thus also counts to the total coupler volume.
  • a pressure plate 7 is arranged, which is in contact with a biasing device 6 in the form of a cylindrical coil spring.
  • the cylindrical helical spring orbits the shaft region 21 of the first coupler part 2 and is supported on a spring plate 8, which is firmly fixed to the shaft region 21 of the first coupler part 2.
  • the pretensioning device 6 exerts a pressure force on the pressure plate 7 and the sealing element 5 on the coupling medium.
  • the biasing force can be adjusted to the coupler medium during assembly of the hydraulic coupler.
  • a closure ball 10 which seals the coupler volume in the second bore 23.
  • the seal by means of the closure ball 10 takes place after a filling of the coupler volume with the coupler medium.
  • the closure ball 10 can in this case for example be pressed into the second bore 23.
  • a cover 9 is further provided, which is attached at one end to the second coupler part 3 and with its other end on the spring plate 8.
  • the inventive hydraulic coupler 1 according to the first embodiment thus has a simple coupler construction with only a small number of individual parts.
  • the inventive hydraulic coupler 1 can be provided very inexpensively.
  • the hydraulic coupler 1 has only a minimal volume for the coupler medium.
  • an axial stroke of the sealing element 5 due to a thermal expansion of the coupling medium can be reduced to a minimum. This results in operation due to the small Axialhübe significantly less drag losses of coupler medium on the sealing medium 5.
  • the coupler according to the invention operates virtually leak-free.
  • the pressure plates 7 further ensures that tilting between the first coupler part 2 and the second coupler part 3 is significantly minimized during operation.
  • the pressure disk 7 has an inner guide region 7a and an outer guide region 7b.
  • the inner guide portion 7a is in contact with the shaft portion 21, and the outer guide portion 7b is in contact with the cylinder portion 30 of the second coupler portion.
  • the first coupler part 2 is guided twice in the second coupler part 3, namely on the one hand in the area of the piston area 20 and of the cylinder area 30 and in the area of the pressure disk 7.
  • the cover 9 is preferably an elastomer and prevents a possible escape of coupler medium, which could pass into the region of the biasing device 6 due to the operation of the sealing element 5 over. It should be noted that the cover 9 may be omitted, in particular, if an actuator can not be damaged by coupler oil or leakage through the sealing element 5 are negligible. The cover 9 also serves as protection against dirt and damage.
  • the sealing element 5 is further preferably designed such that the sealing element 5 compensates for the lifting movement predominantly by a material deformation.
  • the sealing element 5 must be as soft as possible and have the highest possible coefficient of friction for the first coupler part 2 and the second coupler part 3.
  • the sealing element 5 has the largest possible cord thickness.
  • the inventive hydraulic coupler 1 is particularly preferably used in injectors for the injection of fuels in vehicle engines.
  • FIG. 2 shows only an enlarged section of the hydraulic coupler 1, which illustrates the difference to the hydraulic coupler of the first embodiment.
  • the hydraulic coupler of the second embodiment comprises a sealing element as a first sealing ring 11 and a second sealing ring 12.
  • the two sealing rings 11, 12 are constructed substantially the same, but have different diameters.
  • an outer groove-shaped recess 71 is formed on a radial outer side, which receives the first sealing ring 11 and on an inner radial side an inner groove-shaped recess 72 is formed, which receives the second sealing ring 12.
  • the second embodiment instead of a single sealing element, two separate sealing elements, namely the first sealing ring 11 and the second sealing ring 12, are provided. In each case, a sealing ring only has to seal on one side.
  • the hydraulic coupler of the second embodiment has the advantage that the sealing element is integrated into the thrust washer 7. In this case, an even more compact design and in particular a simple assembly can be ensured. Otherwise, this embodiment corresponds to the first embodiment, so that reference may be made to the description given there.
  • FIG. 3 a hydraulic coupler 1 according to a third embodiment of the invention described in detail. Identical or functionally identical parts are again denoted by the same reference numerals as in the first embodiment.
  • the third embodiment substantially corresponds to the first embodiment, wherein, in contrast to the first embodiment, a sealing element 15 is provided, which is not designed as a sealing ring with a substantially circular cross-section, but as a lip seal.
  • the lip sealing ring comprises a first lip 15a, which is in contact with an inner side of the cylindrical region 30 of the second coupler part 3, and a second sealing lip 15b, which is in communication with an outer side of the shaft region 21 of the first coupler part 2.
  • a recess 15c is formed, which is also filled with Kopplermedium.
  • the lip seal has the particular advantage that on the one hand enables a better seal, so that the leakage through the sealing element 15 are very low, and on the other hand, a smaller volume for the coupler medium is possible. Otherwise, this embodiment corresponds to the previous embodiments, so that reference can be made to the description given there.

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  • Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Hydraulic Clutches, Magnetic Clutches, Fluid Clutches, And Fluid Joints (AREA)
  • Fuel-Injection Apparatus (AREA)

Claims (10)

  1. Coupleur hydraulique, comprenant une première partie de coupleur (2), une deuxième partie de coupleur (3) et un espace de coupleur (4) disposé entre la première partie de coupleur (2) et la deuxième partie de coupleur (3), lequel est rempli d'un fluide de coupleur, un élément d'étanchéité (5 ; 11, 12 ; 15) qui étanchéifie l'espace de coupleur (4), et un dispositif de précontrainte (6) qui exerce une force de précontrainte sur l'élément d'étanchéité (5 ; 11, 12 ; 15), afin de produire une pression prédéterminée sur le fluide de coupleur dans l'espace de coupleur (4), caractérisé en ce que
    la première partie de coupleur (2) comprend une région de piston (20) et une région de tige (21) de plus petit diamètre, de sorte qu'un piston étagé soit produit, et la région de piston (20) est guidée au niveau d'une paroi interne d'une région cylindrique (30) de la deuxième partie de coupleur (3) et l'élément d'étanchéité (5 ; 11, 12 ; 15) est monté entre la première et la deuxième partie de coupleur (2, 3) de telle sorte qu'il réalise l'étanchéité, avec son côté radial interne au niveau de la région de tige (21) de la première partie de coupleur (2) et avec un côté radial externe au niveau de la paroi interne de la région cylindrique (30) de la deuxième partie de coupleur (3).
  2. Coupleur hydraulique selon la revendication 1, caractérisé en ce que l'élément d'étanchéité (5 ; 11, 12 ; 15) est réalisé sous forme annulaire.
  3. Coupleur hydraulique selon l'une quelconque des revendications précédentes, caractérisé en ce que le dispositif de précontrainte (6) est un ressort, notamment un ressort cylindrique.
  4. Coupleur hydraulique selon l'une quelconque des revendications précédentes, comprenant en outre un disque de pression (7) qui se trouve en contact d'une part avec l'élément d'étanchéité (5 ; 11, 12 ; 15) et d'autre part avec le dispositif de précontrainte (6).
  5. Coupleur hydraulique selon la revendication 4, caractérisé en ce que le disque de pression (7) présente, au niveau d'un côté radial interne, une région de guidage interne (7a) et au niveau d'un côté radial externe, une région de guidage externe (7b), la région de guidage interne (7a) guidant la première partie de coupleur (2) et la région de guidage externe (7b) guidant la deuxième partie de coupleur (3).
  6. Coupleur hydraulique selon l'une quelconque des revendications précédentes, comprenant en outre une coupelle de ressort (8) qui est fixée sur la première partie de coupleur (2) et qui supporte une extrémité du dispositif de précontrainte (6).
  7. Coupleur hydraulique selon l'une quelconque des revendications précédentes, caractérisé en ce que l'élément d'étanchéité (5 ; 11, 12) est un joint torique ayant une section transversale essentiellement circulaire.
  8. Coupleur hydraulique selon l'une quelconque des revendications 1 à 6, caractérisé en ce que l'élément d'étanchéité est un joint d'étanchéité à lèvre annulaire (15) avec une première lèvre d'étanchéité (15a) et une deuxième lèvre d'étanchéité (15b), un évidement périphérique annulaire (15c) étant formé entre la première lèvre d'étanchéité (15a) et la deuxième lèvre d'étanchéité (15b).
  9. Coupleur hydraulique selon l'une quelconque des revendications précédentes, caractérisé en ce que la première partie de coupleur (2) est réalisée sous forme de piston étagé avec la région de piston (20) et la région de tige (21), la première partie de coupleur (2) présentant un premier alésage central (22), un deuxième alésage central (23) de plus petit diamètre (D2) qu'un diamètre (D1) du premier alésage central (22), un troisième alésage radial (24), un quatrième alésage (25) qui est parallèle au premier alésage (22), et un alésage d'étranglement (26) qui est disposé à l'extrémité du quatrième alésage (25).
  10. Coupleur hydraulique selon l'une quelconque des revendications précédentes, comprenant en outre un recouvrement (9) qui recouvre au moins en partie le dispositif de précontrainte (6).
EP20080101550 2007-03-19 2008-02-13 Coupleur hydraulique Expired - Fee Related EP1972779B1 (fr)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
DE200710012920 DE102007012920A1 (de) 2007-03-19 2007-03-19 Hydraulischer Koppler

Publications (2)

Publication Number Publication Date
EP1972779A1 EP1972779A1 (fr) 2008-09-24
EP1972779B1 true EP1972779B1 (fr) 2011-05-04

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Application Number Title Priority Date Filing Date
EP20080101550 Expired - Fee Related EP1972779B1 (fr) 2007-03-19 2008-02-13 Coupleur hydraulique

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EP (1) EP1972779B1 (fr)
DE (2) DE102007012920A1 (fr)

Families Citing this family (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP2273099B1 (fr) * 2009-06-17 2012-02-22 Delphi Technologies, Inc. Injecteur de carburant avec compensateur de jeu
DE102013209141A1 (de) * 2013-05-16 2014-06-18 Carl Zeiss Laser Optics Gmbh Gasdichter Aktuator und Gehäuse mit Aktuator

Family Cites Families (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE10233907A1 (de) * 2002-07-25 2004-02-12 Siemens Ag Vorrichtung zum Übertragen einer Auslenkung eines Aktors mit einem Elastomerring
DE60204565T2 (de) * 2002-08-20 2005-11-03 Siemens Vdo Automotive S.P.A., Fauglia Dosiergerät mit Thermalkompensationseinheit
DE10357189A1 (de) 2003-12-08 2005-07-07 Robert Bosch Gmbh Brennstoffeinspritzventil

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Publication number Publication date
DE102007012920A1 (de) 2008-09-25
DE502008003393D1 (de) 2011-06-16
EP1972779A1 (fr) 2008-09-24

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