EP0347581B1 - Pompe à injection pour moteurs à combustion interne - Google Patents

Pompe à injection pour moteurs à combustion interne Download PDF

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Publication number
EP0347581B1
EP0347581B1 EP89108890A EP89108890A EP0347581B1 EP 0347581 B1 EP0347581 B1 EP 0347581B1 EP 89108890 A EP89108890 A EP 89108890A EP 89108890 A EP89108890 A EP 89108890A EP 0347581 B1 EP0347581 B1 EP 0347581B1
Authority
EP
European Patent Office
Prior art keywords
accumulator chamber
pressure
valve
fuel
injection pump
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
EP89108890A
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German (de)
English (en)
Other versions
EP0347581A1 (fr
Inventor
Jaroslaw Dipl.-Ing. Hlousek
Gerhard Dr. Dipl.-Ing. Lehner
Theodor Dr. Dipl.-Ing. Stipek
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
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Application filed by Robert Bosch GmbH filed Critical Robert Bosch GmbH
Publication of EP0347581A1 publication Critical patent/EP0347581A1/fr
Application granted granted Critical
Publication of EP0347581B1 publication Critical patent/EP0347581B1/fr
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
    • F02M63/00—Other fuel-injection apparatus having pertinent characteristics not provided for in groups F02M39/00 - F02M57/00 or F02M67/00; Details, component parts, or accessories of fuel-injection apparatus, not provided for in, or of interest apart from, the apparatus of groups F02M39/00 - F02M61/00 or F02M67/00; Combination of fuel pump with other devices, e.g. lubricating oil pump
    • F02M63/0012—Valves
    • F02M63/0031—Valves characterized by the type of valves, e.g. special valve member details, valve seat details, valve housing details
    • F02M63/005—Pressure relief valves
    • 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
    • F02M55/00—Fuel-injection apparatus characterised by their fuel conduits or their venting means; Arrangements of conduits between fuel tank and pump F02M37/00
    • F02M55/001—Pumps with means for preventing erosion on fuel discharge
    • 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
    • F02M55/00—Fuel-injection apparatus characterised by their fuel conduits or their venting means; Arrangements of conduits between fuel tank and pump F02M37/00
    • F02M55/04—Means for damping vibrations or pressure fluctuations in injection pump inlets or outlets
    • 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

Definitions

  • the invention relates to an injection pump for internal combustion engines, with a pump piston sleeve and a pump piston guided therein with control edges for controlling the start and end of an injection process, which interact with control holes provided in the wall of the pump piston sleeve, which open into a collecting space surrounding the pump piston sleeve. into which fuel can be supplied under pressure and from which excess fuel or fuel that overflows at the end of an injection process can be derived, a suction valve opening to the collecting chamber being connected to the collecting chamber for the fuel supply and an organ influencing the flow being connected to the collecting chamber for fuel discharge is.
  • the invention now aims to achieve the control of the injection pressure at the end of delivery against the highest possible pressure without complex design measures.
  • the invention essentially consists in the collecting space being designed as a storage space with a pressure-maintaining valve opening away from the storage space. Because the collecting space or suction space is now not open to the inlet as in the known measures, but is designed as a storage space closed by valves and a check valve is arranged as a pressure-maintaining valve, a predetermined and relatively high pressure can be ensured as the control pressure. The pressure in the working chamber of the piston then drops further and only when the pressure has dropped to a pressure level sufficient that the pump pressure can be used to refill the working chamber, is the filling again carried out with the much lower pump pressure.
  • the training is so made that the storage space concentric with a suction space Control holes of the pump piston liner is connected, which results in a particularly simple design.
  • the training can be carried out in such a way that the pressure-maintaining valve opening away from the storage space and the suction valve opening toward the storage space are jointly connected on the side facing away from the storage space to the suction space supplied with fuel and are formed by check valves.
  • the suction valve which is designed as a non-return valve and opens to the storage chamber, causes fuel to be sucked in again when the pressure in the pump chamber drops below the set pressure of the suction valve.
  • the low pressure suction frame i.e. the space under pre-pump pressure, fuel sucked in to fill the injection pump.
  • the design can advantageously be such that the pressure-maintaining valve opening away from the storage space is connected to the storage space via a throttle point known per se.
  • the pressure to be maintained in the storage space is hereby defined by the check valve and kept at an exactly predetermined level, such additional throttle bores allowing short-term peak pressures to be reduced.
  • the pressure level remains constant after the predetermined pressure level has been reached and that the corresponding pressure level can be ensured in a simple manner by dimensioning or adjusting the pressure control valve.
  • the arrangement is such that the axes of the mouths of the check valves on the storage space side are arranged offset with respect to the axes of the control bores.
  • Impact protection rings of this type are not suitable for preventing cavitation phenomena, but only serve to provide materials which are particularly wear-resistant in the place of particularly high wear and tear and to create an easily replaceable wear part which can be replaced in the event of excessive wear .
  • Impact protection devices of the usual type in particular, can in no way counteract cavitation phenomena on the outer wall of the pump piston.
  • the design within the scope of the present invention can advantageously be made such that at the mouth on the storage space side At least one impact valve is arranged axially with a control bore check valve.
  • the design is such that a baffle plate that closes the bore is arranged in front of an axial bore of the check valve, on the rear side of which a transverse bore intersecting the axial bore of the check valve is provided with open ends, which in turn rinses or flushes away of any bubbles that may arise.
  • the baffle plate can be formed in one piece with the housing of the check valve, which considerably simplifies the installation of the check valve.
  • a known design of such an impact protection body is that it is frustoconical in cross-section and is rounded on the side facing the bore.
  • Such designs of impact protection bodies are characterized by particularly high wear resistance and with such a design, the arrangement of the check valve or pressure-maintaining valve opening to the storage space is advantageously made such that the control bore has a section that is frustoconically enlarged to the storage space such that the housing of the opening to the storage space
  • Non-return valve has a conical end part with a rounded tip which projects into the frustoconically widened section, leaving a space free, and that the outlet channel of the non-return valve opens off-center in the region of the conical jacket of the end part. The flow path resulting in this way in turn leads to a flushing out of particularly critical points.
  • FIG. 1 shows a partial section through the upper part of an injection pump for large diesel engines
  • 2 shows a development of a detail of the injection pump according to FIG. 1
  • 3 shows a diagram of the course of pump chamber pressure and storage chamber pressure over the cam angle
  • FIGS. 4, 5 and 6 in a representation similar to that of FIG. 1, variants of the construction of an injection pump with direct supply and discharge of fuel into and from the Storage space and training of an impact protection.
  • a pump piston 2 is moved up and down in a pump piston liner 1 by a cam drive, not shown.
  • the pump piston liner 1 is supported in a housing 3 which has a suction space 4, into which fuel is supplied via a pipe screw connection 5 or from which excess fuel is derived.
  • When going up the pump piston 2 closes with its upper edge 6 control bores 7.
  • a throttle 13 can be installed in the inlet of the pressure-maintaining valve 11, which causes a quantity-dependent increase in the storage space pressure, so that a further reduction in the risk of cavity formation in the fuel is achieved with larger delivery quantities and / or higher speeds or piston speeds.
  • the suction valve 10 and the pressure holding valve 11 are accommodated in a sleeve 14 which also contains the storage space 9.
  • a pressure seal of the storage space 9 and the suction space 4 is carried out by means of sealing rings 15, 16 and 17 down between pump piston 2 and pump piston liner 1, returned to the storage space 9.
  • valves 10, 11 or their flow openings are arranged in a sectional plane with the control bores 7 in the pump cylinder, but rather to arrange them rotated by 90 °, for example.
  • two or more pressure-maintaining or suction valves can also be arranged in the sleeve 14 if required.
  • FIG. 3 shows the curves of pump chamber pressure p P and storage chamber pressure p S over the cam angle, the start of delivery of the injection pump being designated FB and the end of delivery being FE. From the diagram it can be seen that the pressure p S in the storage space 9 already reaches the holding value of the valve 11 at the start of delivery and that a short-term dynamic pressure increase occurs in the storage space 9 immediately after the end of the delivery due to the deactivated fuel which shoots out of the control bores 7, after which Filling the pump chamber 8, the pressure initially drops to the delivery pressure of the backing pump, and then increases again after the upward gear of the pump piston 2 begins.
  • a throttle bore in front of the pressure-maintaining valve can also achieve a dependency of the storage space pressure on the delivery volume and the speed of the pump, different diameters of the throttle 13 resulting in different pressure profiles in the region of the pressure increase, as indicated in FIG. 3.
  • the axes of the bores towards the valves 10 and 11 are offset relative to the control bores 7, so that any cavities formed in the fuel can be quickly washed away by the jet emerging from the control bore 7 and any corrosion that may occur is kept away from hazardous areas.
  • feed 19 and discharge line 20 of the fuel lie coaxially with the control bores 7, but the bore of each of the valves 10, 11 facing the control bore 7 is connected upstream of a baffle plate 21 or 22, each of which with the Armature of the associated valve is integrally formed.
  • the suction valve 10 is installed on both sides in an impact protection which has a conical shape and projects far into the control bore 7.
  • the fuel is conveyed through a bore 23 coming from the suction valve 10 into the gap between the cone 24 of the impact protection and the conical extension 25 of the control bore.
  • the bore 23 is positioned in such a way that it allows the fuel to exit at the highest part of the gap, so that the cavities in the fuel are hit directly by the flushing stream and conveyed into the storage space 9.
  • a pressure control valve not shown, ensures the maintenance of an increased standing pressure in the storage space 9 after the end of the control process until it is sucked in again.
  • the fuel is advantageously supplied at a pressure of 5 to 20 bar, in order to achieve a sufficient flushing effect in the control bores 7.
  • a pressure accumulator in the fuel line between the feed pump and suction valve 10 appears to be useful for making the inlet pressure more uniform.

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 (9)

  1. Pompe à injection pour moteurs à combustion interne, comportant un cylindre (1) dans lequel coulisse un piston (2) dont les bords (6, 12) commandent le débit et la fin d'un processus d'injection en coopération avec des alésages de commande (7) pratiqués dans la paroi du cylindre et débouchant dans une chambre de stockage (9) qui entoure le cylindre (1) qui peut recevoir du carburant sous pression et être délestée du carburant se retrouvant en excès, c'est-à-dire de celui qui continue à arriver après la fin d'une phase d'injection, l'amenée du carburant s'effectuant à travers une soupape d'aspiration (10) raccordée à la chambre de stockage elle-même raccordée à une autre soupape (11) permettant l'évacuation du carburant en excès, caractérisée en ce que la soupape qui permet l'évacuation du carburant contenu dans la chambre de stockage (9) est constituée de manière à maintenir dans cette chambre une pression d'au moins 20 bars.
  2. Pompe à injection selon la revendication 1, caractérisée en ce que la chambre de stockage (9), concentrique à une chambre d'aspiration (4) est raccordée aux alésages de commande (7) du cylindre (1) de la pompe.
  3. Pompe à injection selon la revendication 2, caractérisée en ce que la soupape de maintien de pression (11) ouvrant à l'opposé de la chambre de stockage (9) et la soupape d'aspiration (10) ouvrant vers la chambre de stockage (9) sont équipées toutes deux du côté opposé à la chambre de stockage (9), d'une liaison commune à la chambre d'aspiration (4) alimentée en carburant et sont du type anti-retour.
  4. Pompe à injection selon la revendication 1, 2 ou 3, caractérisée en ce que la soupape de main tien de pression (11) ouvrant à l'opposé de la chambre de stockage (9) est raccordée à celle-ci par l'intermédiaire d'un orifice d'étranglement (13) connu en soi, à la chambre de stockage (9).
  5. Pompe à injection selon une des revendications 1 à 4, caractérisée en ce que les axes des orifices, côté chambre de stockage, des soupapes anti-retour (10, 11) sont décalés par rapport aux axes des alésages de commande (7).
  6. Pompe à injection selon une des revendications 1 à 4, caractérisée en ce que l'orifice, côté chambre de stockage, d'au moins une des soupapes anti-retour (10, 11) alignées axialement avec un alésage de commande (7), est équipée d'une plaque brise-jet ou palque de rebondissement.
  7. Pompe à injection selon la revendication 6, caractérisée en ce qu'on utilise comme protection devant l'orifice axial de la soupape anti-retour (10, 11), une plaque brise-jet (21, 22) couvrant l'orifice et dont la face arrière est équipée d'un perçage ouvert à ses extrémités et traversant perpendiculairement l'alésage axial de la soupape anti-retour.
  8. Pompe à injection selon la revendication 7, caractérisée en ce que la plaque brise-jet (21, 22) est réalisée monobloc avec le boîtier de la soupape anti-retour (10, 11).
  9. Pompe à injection selon la revendication 6, caractérisée en ce que l'alésage de commande (7) présente une partie (25) en forme de cône s'évasant vers la chambre de stockage (9) le boîtier de la soupape anti-retour (10, 11) ouvrant vers la chambre de stockage (9) ayant une extrémité conique (25) à pointe arrondie engagée à l'intérieur de l'évasement conique (25) en laissant libre un espace intermédiaire, le canal de décharge (23) de la soupape anti-retour (10, 11) débouchant extérieurement dans la partie conique de l'extrémité (24).
EP89108890A 1988-06-18 1989-05-18 Pompe à injection pour moteurs à combustion interne Expired - Lifetime EP0347581B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE3820707A DE3820707A1 (de) 1988-06-18 1988-06-18 Einspritzpumpe fuer brennkraftmaschinen
DE3820707 1988-06-18

Publications (2)

Publication Number Publication Date
EP0347581A1 EP0347581A1 (fr) 1989-12-27
EP0347581B1 true EP0347581B1 (fr) 1993-02-03

Family

ID=6356795

Family Applications (1)

Application Number Title Priority Date Filing Date
EP89108890A Expired - Lifetime EP0347581B1 (fr) 1988-06-18 1989-05-18 Pompe à injection pour moteurs à combustion interne

Country Status (4)

Country Link
US (1) US5015160A (fr)
EP (1) EP0347581B1 (fr)
JP (1) JP2721243B2 (fr)
DE (2) DE3820707A1 (fr)

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
KR101178681B1 (ko) 2006-11-06 2012-08-30 미츠비시 쥬고교 가부시키가이샤 회전식 디플렉터를 갖는 연료 분사 펌프

Families Citing this family (14)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE19541507A1 (de) * 1995-11-08 1997-05-15 Bosch Gmbh Robert Kraftstoffeinspritzeinrichtung für Brennkraftmaschinen
DK176162B1 (da) * 1997-04-21 2006-10-23 Man B & W Diesel As Brændstofpumpe til forbrændingsmotorer, især store langsomtgående marinedieselmotorer
DE19719046A1 (de) * 1997-05-06 1998-11-12 Man B & W Diesel Ag Brennstoffeinspritzpumpe
JP3471587B2 (ja) * 1997-10-27 2003-12-02 三菱電機株式会社 筒内噴射用高圧燃料ポンプ
FR2774132B1 (fr) * 1998-01-27 2000-04-07 Semt Pielstick Dispositif pour eviter la cavitation dans les pompes a injection
DE69938613T2 (de) * 1999-02-09 2009-07-09 Hitachi, Ltd. Hochdruckbrennstoffpumpe für eine Brennkraftmaschine
DE10220281A1 (de) * 2002-05-07 2003-11-27 Bosch Gmbh Robert Kraftstoffpumpe, insbesondere für eine Brennkraftmaschine mit Direkteinspritzung
DE102004013307B4 (de) * 2004-03-17 2012-12-06 Robert Bosch Gmbh Kraftstoffhochdruckpumpe mit einem Druckbegrenzungsventil
FI118055B (fi) * 2005-11-23 2007-06-15 Waertsilae Finland Oy Mäntämoottorin ruiskutuspumppu
JP4595996B2 (ja) * 2007-11-16 2010-12-08 トヨタ自動車株式会社 内燃機関の高圧燃料供給装置
KR100992227B1 (ko) * 2008-10-27 2010-11-05 현대중공업 주식회사 디젤엔진 연료분사펌프의 캐비테이션 손상방지장치
IT1396473B1 (it) * 2009-03-30 2012-12-14 Magneti Marelli Spa Pompa carburante con una valvola di massima pressione perfezionata per un sistema di iniezione diretta
US20130312706A1 (en) * 2012-05-23 2013-11-28 Christopher J. Salvador Fuel system having flow-disruption reducer
DE102015201855A1 (de) * 2015-02-03 2016-08-04 Robert Bosch Gmbh Überströmventil für eine Hochdruckpumpe, insbesondere Steckpumpe, sowie Hochdruckpumpe mit einem solchen Überströmventil

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US2131779A (en) * 1934-06-16 1938-10-04 Deckel Friedrich Fuel injection pump
DE673809C (de) * 1936-06-16 1939-07-14 Bosch Gmbh Robert Brennstoff-Foerderanlage fuer Einspritzbrennkraftmaschinen
US2157737A (en) * 1936-07-15 1939-05-09 Bosch Gmbh Robert Fuel delivery apparatus for injection internal combustion engines
US2298936A (en) * 1940-12-07 1942-10-13 Ernest C Gambrell Fuel injection pump
DE843763C (de) * 1942-08-19 1952-07-14 Bosch Gmbh Robert Einspritzpumpe fuer Brennkraftmaschinen
DE762581C (de) * 1943-06-27 1952-08-14 Bosch Gmbh Robert Kraftstoffeinspritzanlage fuer Brennkraftmaschinen
CH295782A (de) * 1950-10-19 1954-01-15 Gmbh Robert Bosch Einspritzpumpe mit drehzahlabhängiger Fördermengenregelung, insbesondere für Brennkraftmaschinen.
CH515418A (de) * 1970-01-29 1971-11-15 Bosch Gmbh Robert Kraftstoffeinspritzpumpe für Brennkraftmaschinen
FR2093250A5 (fr) * 1970-06-08 1972-01-28 Peugeot
DE2309916C3 (de) * 1973-02-28 1981-03-26 Franz Prof. Dipl.-Ing. Dr.Techn. 5100 Aachen Pischinger Kraftstoffeinspritzvorrichtung für Brennkraftmaschinen
CH594134A5 (fr) * 1975-07-15 1977-12-30 Sulzer Ag
US4118156A (en) * 1976-12-01 1978-10-03 Sulzer Brothers Limited Fuel injection pump having choke means in overflow line
US4355961A (en) * 1978-04-03 1982-10-26 Ingersoll-Rand Company Controlling means for a fuel valve
JPS5947359U (ja) * 1982-09-22 1984-03-29 株式会社小松製作所 エンジンの燃料噴射装置
DE3245142A1 (de) * 1982-12-07 1984-06-07 Robert Bosch Gmbh, 7000 Stuttgart Verfahren und vorrichtung zum einspritzen von kraftstoff
DE3535808A1 (de) * 1985-10-08 1987-04-09 Bosch Gmbh Robert Kraftstoffeinspritzpumpe fuer brennkraftmaschinen

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
KR101178681B1 (ko) 2006-11-06 2012-08-30 미츠비시 쥬고교 가부시키가이샤 회전식 디플렉터를 갖는 연료 분사 펌프

Also Published As

Publication number Publication date
JPH0237166A (ja) 1990-02-07
DE3820707A1 (de) 1989-12-21
JP2721243B2 (ja) 1998-03-04
US5015160A (en) 1991-05-14
DE58903432D1 (de) 1993-03-18
EP0347581A1 (fr) 1989-12-27

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