EP0900334B1 - Soupape de refoulement - Google Patents

Soupape de refoulement Download PDF

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Publication number
EP0900334B1
EP0900334B1 EP98902953A EP98902953A EP0900334B1 EP 0900334 B1 EP0900334 B1 EP 0900334B1 EP 98902953 A EP98902953 A EP 98902953A EP 98902953 A EP98902953 A EP 98902953A EP 0900334 B1 EP0900334 B1 EP 0900334B1
Authority
EP
European Patent Office
Prior art keywords
valve
pressure
fuel
closing member
spring
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
EP98902953A
Other languages
German (de)
English (en)
Other versions
EP0900334A1 (fr
Inventor
Wolfgang Fehlmann
Ruben-Sebastian Henning
Walter Fuchs
Stephan Jonas
Kiyotaka Ogata
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 EP0900334A1 publication Critical patent/EP0900334A1/fr
Application granted granted Critical
Publication of EP0900334B1 publication Critical patent/EP0900334B1/fr
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

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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
    • F02M59/00—Pumps specially adapted for fuel-injection and not provided for in groups F02M39/00 -F02M57/00, e.g. rotary cylinder-block type of pumps
    • F02M59/44—Details, components parts, or accessories not provided for in, or of interest apart from, the apparatus of groups F02M59/02 - F02M59/42; Pumps having transducers, e.g. to measure displacement of pump rack or piston
    • F02M59/46—Valves
    • F02M59/462—Delivery valves
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
    • Y10T—TECHNICAL SUBJECTS COVERED BY FORMER US CLASSIFICATION
    • Y10T137/00—Fluid handling
    • Y10T137/7722—Line condition change responsive valves
    • Y10T137/7771—Bi-directional flow valves
    • Y10T137/7772—One head and seat carried by head of another
    • Y10T137/7774—Supporting valve spring carried by supporting valve

Definitions

  • the invention relates to a pressure valve of the type of claim 1.
  • a pressure valve of the type of claim 1. Such a thing from scripture DE 42 40 302 known pressure valve is in a delivery line between a pump workspace of a fuel injection pump and an injection point at the one to be supplied by this Internal combustion engine used.
  • the pressure valve has in a pipe socket forming a valve housing used valve body, which has an axial passage has and the with the pump workspace facing end face forms a first valve seat.
  • in the axial through channel of the valve body is an in Pressure valve closing element opening towards the injection point performed with the force of a first valve spring a sealing surface is held on the first valve seat.
  • there is an axial through hole in the pressure valve closing member arranged by a towards the pump work room opening backflow valve is closable.
  • the known pressure valve of the constant pressure valve design is that of the pump work room fuel flowing towards the injection point and the backflowing fuel is the first and the respectively Flow through the second valve spring radially from the outside inwards got to.
  • the gap between the two changes individual spring turns of the valve springs depending from the opening stroke of the respective valve member, so that when An undesired throttling effect flows through the valve springs occurs. This depends on the opening stroke of the The throttle effect that changes valve elements is impaired the flow behavior of the fuel at the pressure valve what affect the injection process at the injection valve Injection point can affect.
  • the pressure valve according to the invention with the characteristic Features of claim 1, however, has the Advantage that the pumped by the fuel injection pump Fuel does not flow radially through the valve springs, so that an unrestricted flow through the pressure valve is guaranteed is.
  • the fuel is used advantageously passed radially outside the valve springs, being between the radially outer peripheral surfaces of the valve springs and a housing wall surrounding each of them Fuel channel of large cross section is formed through the fuel can flow unthrottled.
  • the pressure valve closing element and the backflow valve axially one behind the other to arrange, the pressure valve closing member with its the End face facing the pump workspace at the same time second valve seat for the valve member of the backflow valve forms.
  • the opening stroke movements of the pressure valve closing member and the valve member of the backflow valve each advantageously by a stop piece limited, which at the same time the dead or damaged volume in Pressure valve reduced.
  • stop pieces on their the Valves facing away from recesses at their ends Circumferential surface that cross holes or cross openings with an axial blind hole in the valve member facing away End face are connected and with this blind hole connect each to the delivery line.
  • the second stop piece of the backflow valve in advantageously in the axial passage of the Valve body to be pressed in, being about the press-in depth the maximum opening stroke of the backflow valve can be adjusted.
  • the recesses or cuts on the Stop pieces, the spring plate of the backflow valve and Pressure valve closing member can be of all shapes have an unthrottled fuel flow simultaneous sufficient axial guidance of the components in the Allow valve body or in the valve housing.
  • the first stop of the pressure valve closing member prefferably be provided with an axial through hole, the injection-side part of the delivery line directly connects with the through hole in the pressure valve closing element, so that the fuel flowing back does not have a valve spring must flow through and unhindered to the backflow valve can overflow.
  • FIG. 1 shows this a longitudinal section through a first embodiment a pressure valve designed as a constant pressure valve which the fuel overflow on the second stop of the Backflow valve via cross bores
  • Figure 2 a second embodiment analogous to the representation of the figure 1, in which the fuel passage on the second stop the backflow valve via a bevel cut
  • Figure 3 shows a third embodiment analogous to the illustration of Figure 1, in which the passage of fuel on second stop piece via an oblique radial bore
  • Figure 4 shows a fourth embodiment analogous to the representation of Figure 1, in which in the first Stop piece of the pressure valve closing member has a through hole is provided.
  • Figure 1 shows a longitudinal section through a first Embodiment of the pressure valve 1 according to the invention, the one in a stepped through hole 3 Pipe socket forming valve housing 5 is used, the in turn in a housing, not shown, of a fuel injection pump is screwed in.
  • the pressure valve 1 is thereby in a conveyor line 7 between a part shown Pump working chamber 9 of the fuel injection pump and an injection point 11, in the form of an injection valve in the combustion chamber to be supplied, also not shown Internal combustion engine used, the through hole 3 in the valve housing 5 a part of this delivery line 7 forms.
  • the pressure valve 1 has a tubular Valve body 13 on the pump workspace in the Through hole 3 of the valve housing 5 is inserted.
  • the Valve body 13 has an axial through channel 15 and forms with its ring end face facing away from the pump work space a preferably conical first Valve seat surface 17.
  • This first valve seat surface 17 acts as a piston, partly in the axial passage 15 axially displaceably guided pressure valve closing member 19 together with a conical sealing surface 21.
  • the pressure valve closing member 19 is a first valve spring 23 held in contact with the first valve seat 17 and opens if the fuel pressure exceeds the closing force the first valve spring 23 in the direction of the injection point 11th
  • the pressure valve closing member 19 has an axial through hole 25 on that towards a pump work room 9 opening backflow valve 27 can be closed. there forms the annular end face facing the pump working space 9 of the pressure valve closing member 19 has a second valve seat surface 29 with which the valve member designed as ball 31 of the backflow valve 27 cooperates.
  • the valve ball 31 of the backflow valve 27 is by a second valve spring 33 via a spring plate 35 in contact with the second Valve seat 29 held, the second valve spring 33 on the other hand, stationary on a shoulder of the through-channel 15 is supported in the valve body 13.
  • a first stop 37 in one first valve spring 23 receiving enlarged in cross section Spring chamber 39 of the through bore 3 in the valve housing 5 is arranged.
  • the first stop piece 37 instructs its end facing away from the pressure valve closing member 19 Ring shoulder 41 on which the first valve spring 23 supports and so the first stop 37 against one Bore heel in the valve housing 5 delimiting the spring space 39 braced.
  • the first stop 37 also forms its end face facing the pressure valve closing member 19 a the lifting movement of the pressure valve closing member 19 delimiting stop surface, the first valve spring 23 encloses the first stop piece 37.
  • a second stop piece 43 is in the through channel 15 of the valve body 13 used that it with its Valve ball 31 facing away from the end face in contact with one Bore paragraph of the axial through channel 15 arrives and with its end face facing the valve ball 31 Stop face forms with a facing end face of the spring plate 35 interacts.
  • the second valve spring 33 is based on the same as for the first valve spring 23 Ring shoulder 45 of the second stop piece 43 and radially encloses that having the stop surface Part of the stop piece 43.
  • valve springs 23 and 33 are arranged so that between their outer circumferential surface and the wall of the Through hole 3 and the through channel 15 each Fuel channel is formed, unthrottled by the fuel from the pump work space 9 towards the injection point 11 can flow.
  • the second stop piece 43 has the Pump work space 9 facing a lower end face axial blind bore 47, which opens into the delivery line 7 and with radial transverse channels 49 (preferably grooves) the axial through channel 15 in the valve body 13 connected is.
  • The are in the area of the outlet openings Cross channels 49 also preferably three bevels 51 on second stop piece 43 provided one unthrottled fuel flow along the second Stop piece 43 with safe guidance of the Stop piece 43 in the axial through-channel 15 guarantee.
  • the spring plate 35 also preferably has 4 axially extending recesses 53 on its peripheral surface, the enable unimpeded passage of fuel.
  • the pressure valve closing member 19 has on his, on the Sealing surface 21 adjoining the through channel 15 of the Valve body 13 projecting end preferably three plane Grinds 55 on, which extend axially to the second valve seat 29 extend.
  • the first stop piece 37 has the same as the second Stop piece 43 on its injection point 11 facing End face a blind bore coaxial to the through hole 3 57 on the transverse channels 59 (preferably grooves) is connected to the spring chamber 39. Furthermore, that points first stop piece 37 in the area of the ring shoulder 41 to the Outlet openings of the transverse channels 59 preferably four planes Grindings for an unimpeded passage of fuel.
  • the pressure valve according to the invention works in the following Wise. Before the high-pressure delivery of the fuel injection pump begins there is a static pressure in the delivery line 7, in which the pressure valve 1 and the backflow valve 27 through the force of the first valve spring 23 and the second valve spring 33 are kept closed. Here is the preload the first valve spring 23 is larger than the biasing force of the second valve spring 33. With the start of High-pressure delivery at the fuel injection pump increases the pressure in the pump work space 9 above the opening pressure of the Pressure valve 1, so that the first valve seat 17 in the through channel 15 of the valve body 13 pending high fuel pressure the pressure valve closing member 19 against the restoring force the first valve spring 23 from the first valve seat 17 takes off.
  • the high pressure flows through it Fuel the second stop piece 43 via the Openings 47, 49, 51 continue to flow along the recesses 53 of the spring plate 35 and the pressure valve closing member 19 into the spring chamber 39 and from there via the openings 59, 57 on the first stop piece 37 further into the through hole 3 in the valve housing 5 and from there into the delivery line 7 Injection point 11.
  • This is where the high fuel pressure comes in known manner on the fuel injector Injection into the internal combustion engine to be supplied.
  • the fuel flows through the pressure valve 1 and the backflow valve 27 along the fuel passages radially outward of the valve springs 23, 33 so that the Fuel unthrottled through the constant pressure valve Injection point 11 can flow.
  • the spring preload can be the valve springs 23 and 33 on the training the thickness of the ring shoulder on the stop pieces 37 and 43 to adjust.
  • the second embodiment shown in Figure 2 of the pressure valve according to the invention differs first embodiment only in the training of second stop piece 43 of the return valve 27.
  • Das second connector 43 has instead of the simple Blind bore a contour bore 63 in its the ball valve member 31 facing away from the end face, which is inclined trained flat grinding 65 on the peripheral wall of the cylindrical second stop piece 43 with the axial Through channel 15 in the valve body 13 is connected.
  • Fuel flow geometry the advantage that the Flow resistance is very low and at the same time one sufficient contact area on the valve body 13 and for the second valve spring 33 is guaranteed.
  • the third embodiment of the Pressure valve according to the invention differs in that Figure 1 illustrated first embodiment only in the formation of the second stop piece 43.
  • the second Stop piece 43 is in Figure 3 with his in Cross section enlarged circumferential surface on its the ball valve member 31 facing away into the wall of the through-channel 15 pressed into the valve body 13.
  • the fuel flow now takes place on the second stop piece 43 via radial oblique bores 67 which are axial Surface grinding 69 on the peripheral surface of the second Stop piece 43 starting in the axial blind bore 47 in the end of the second stop piece facing away from the valve member 43 flow out.
  • the fourth embodiment shown in Figure 4 differs from that shown in FIG. 1 first embodiment in the design of the first stop piece 37 of the pressure valve 1 and second stop piece 43 of the backflow valve 27 now has the first stop 37 instead of one Blind bore an axial through bore 71, from which in in a known manner, preferably lead away four transverse channels 59.
  • the transverse channels 59 open in the area of the ring shoulder 41 on the peripheral wall of the first stop piece 47 which in this area has flat cuts.
  • the Passage of fuel in the direction of flow to the injection point 11 continues from the spring chamber 39 via the transverse channels 59 and the bore 71 in the through bore 3 and further the delivery line 7. This flow takes place especially when the pressure valve closing member is in contact with the stop piece 37 19.
  • the second stop piece 43 is like the sectional view the stop piece 43 removable, now with a Provided a plurality of radial oblique bores 67 which in an axial blind bore 47 open.
  • the outlet openings the oblique holes 67 in the through channel 15 are there on an inclined shoulder 73 of the second stop piece 43 provided, which once again has an advantageous effect on the flow behavior of fuel through the second stop 43 affects because the fuel flow is not strong is redirected.
  • the fourth embodiment has the special one Advantage that the fuel flow both towards Injection point 11 back as well as in the opposite direction the pump working space 9 never one of the valve springs 23, 33 must flow through.

Landscapes

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

Claims (2)

  1. Soupape de pression à monter dans une conduite de refoulement (7), entre une chambre de travail (9) d'une pompe d'injection de carburant et un point d'injection (11) sur le moteur à combustion interne qu'il s'agit d'alimenter, comprenant :
    un corps de soupape (13) présentant un premier siège de soupape (17) percé axialement d'un canal de passage (15) dans lequel se déplace en s'ouvrant en direction du point d'injection (11), contre l'action d'un premier ressort de soupape (23), un organe (19) de fermeture de soupape de pression qui possède une portée d'étanchéité (21) coopérant avec le premier siège de soupape (17),
    dans l'organe de fermeture de soupape (19), un alésage axial de passage (25) qui peut être fermé par une soupape de retour (27) s'ouvrant en direction de la chambre de travail (9) de la pompe et équipée d'un second ressort de soupape (33), avec un canal de carburant
    formé entre les surfaces périphériques externes du premier et du second ressort de soupape (23, 33) et une paroi de boítier qui les entoure, à travers lequel le carburant s'écoule sans étranglement de la chambre de travail (9) au point d'injection (11),
    caractérisé en ce que
    quand l'organe de fermeture de soupape est ouvert pour relier la chambre de travail de la pompe et le point d'injection, des pièces de butée (37, 43) destinées à l'organe de fermeture de soupape et à l'organe de soupape de retour, présentent à la surface périphérique de leurs extrémités éloignées des corps de soupape (19, 31) des évidements qui sont reliés par des canaux de liaison (49, 59) à un évidement central (47, 57) prévu dans chacune des faces frontales éloignées de l'organe de fermeture et sur lequel débouche chaque fois une partie de la conduite de refoulement (7),
    des évidements axiaux (53) sont prévus à la surface périphérique d'une coupelle de ressort (35) de la soupape de retour (27), et
    l'organe (19) de fermeture de la soupape de pression présente au moins une entaille axiale (55) à sa surface périphérique faisant suite à la portée d'étanchéité (21) et pénétrant dans le corps de soupape (13).
  2. Soupape de pression selon la revendication 1,
    caractérisée en ce que
    la seconde pièce de butée (43) est emmanchée à force le long d'une partie de sa surface périphérique, dans le canal de passage (15) du corps de soupape (13).
EP98902953A 1997-03-15 1998-01-12 Soupape de refoulement Expired - Lifetime EP0900334B1 (fr)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
DE19710891A DE19710891A1 (de) 1997-03-15 1997-03-15 Druckventil
DE19710891 1997-03-15
PCT/DE1998/000084 WO1998041755A1 (fr) 1997-03-15 1998-01-12 Soupape de refoulement

Publications (2)

Publication Number Publication Date
EP0900334A1 EP0900334A1 (fr) 1999-03-10
EP0900334B1 true EP0900334B1 (fr) 2003-08-27

Family

ID=7823559

Family Applications (1)

Application Number Title Priority Date Filing Date
EP98902953A Expired - Lifetime EP0900334B1 (fr) 1997-03-15 1998-01-12 Soupape de refoulement

Country Status (5)

Country Link
US (1) US6196201B1 (fr)
EP (1) EP0900334B1 (fr)
JP (1) JP2000511264A (fr)
DE (2) DE19710891A1 (fr)
WO (1) WO1998041755A1 (fr)

Families Citing this family (15)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE19829553A1 (de) * 1998-07-02 2000-01-05 Bosch Gmbh Robert Druckventil
DE29811791U1 (de) * 1998-07-02 1999-11-18 Bosch Gmbh Robert Druckventil
US6474359B1 (en) * 2000-03-08 2002-11-05 National Coupling Company, Inc. Undersea hydraulic coupling member
DE10059425A1 (de) * 2000-11-30 2002-06-06 Bosch Gmbh Robert Kraftstoffeinspritzpumpe für Brennkraftmaschinen, insbesondere Dieselmotoren
DE10124743A1 (de) * 2001-05-21 2002-11-28 Bosch Gmbh Robert Brennstoffeinspritzventil
JP4152814B2 (ja) * 2003-01-17 2008-09-17 株式会社ショーワ リリーフ弁
DE10313662B4 (de) * 2003-03-26 2005-10-13 Robert Bosch Gmbh Durchflussbegrenzungsventil mit Schwingungsdämpfung
JP2009209801A (ja) * 2008-03-04 2009-09-17 Yanmar Co Ltd 燃料噴射ポンプのデリベリバルブ
DE102010005101B4 (de) * 2010-01-20 2011-09-01 Poppe & Potthoff Gmbh Druckbegrenzungsventil, insbesondere zum Begrenzen des Fluiddruckes in einem Verteilerrohr eines Common-Rail-Einspritzsystems
DE102012208106A1 (de) * 2012-05-15 2013-11-21 Veritas Ag Druckhalteventilanordnung für eine Kraftstoffleitung
DE102012208110A1 (de) * 2012-05-15 2013-11-21 Veritas Ag Druckhalteventilanordnung für eine Kraftstoffleitung
US20130340861A1 (en) * 2012-06-20 2013-12-26 Caterpillar Inc Check valve of fuel system
US9194352B2 (en) * 2012-10-25 2015-11-24 Caterpillar Inc. Pressure relief valve for common rail fuel system
DE102014211622A1 (de) * 2014-06-17 2015-12-17 Robert Bosch Gmbh Kraftstoff-Hochdruckpumpe für ein Kraftstoffsystem für eine Brennkraftmaschine
DE102018201279B4 (de) * 2018-01-29 2019-11-28 Continental Automotive Gmbh Hochdruckanschluss für eine Kraftstoffhochdruckpumpe eines Kraftstoffeinspritzsystems sowie Kraftstoffhochdruckpumpe

Family Cites Families (10)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE1297935C2 (de) * 1965-06-03 1976-09-30 Klöckner-Humboldt-Deutz AG, 500OKoIn Kraftstoffeinspritzsystem
DE3341575C2 (de) * 1983-11-17 1996-06-05 Bosch Gmbh Robert Druckventil für Kraftstoffeinspritzpumpen
EP0325211B1 (fr) * 1988-01-18 1994-06-22 Diesel Kiki Co., Ltd. Soupape d'équilibrage de pression
DE3843819A1 (de) * 1988-09-09 1990-03-22 Bosch Gmbh Robert Druckventil
US5295469A (en) * 1990-07-09 1994-03-22 Nippondenso Co., Ltd. Safety valve for fuel injection apparatus
DE4202853A1 (de) * 1992-02-01 1993-08-05 Bosch Gmbh Robert Druckventil
DE4240302A1 (de) 1992-12-01 1994-06-09 Bosch Gmbh Robert Druckventil
US5365906A (en) * 1993-12-20 1994-11-22 Chrysler Corporation Fluid flow check valve for fuel system
DE19541507A1 (de) * 1995-11-08 1997-05-15 Bosch Gmbh Robert Kraftstoffeinspritzeinrichtung für Brennkraftmaschinen
DE19706591A1 (de) * 1997-02-20 1998-08-27 Bosch Gmbh Robert Druckventil

Also Published As

Publication number Publication date
WO1998041755A1 (fr) 1998-09-24
JP2000511264A (ja) 2000-08-29
DE59809397D1 (de) 2003-10-02
EP0900334A1 (fr) 1999-03-10
US6196201B1 (en) 2001-03-06
DE19710891A1 (de) 1998-09-17

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