EP0713002A1 - Pompe à combustible haute pression pour moteurs à combustion interne - Google Patents

Pompe à combustible haute pression pour moteurs à combustion interne Download PDF

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Publication number
EP0713002A1
EP0713002A1 EP95115120A EP95115120A EP0713002A1 EP 0713002 A1 EP0713002 A1 EP 0713002A1 EP 95115120 A EP95115120 A EP 95115120A EP 95115120 A EP95115120 A EP 95115120A EP 0713002 A1 EP0713002 A1 EP 0713002A1
Authority
EP
European Patent Office
Prior art keywords
pump
control
piston
pressure
pump piston
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Granted
Application number
EP95115120A
Other languages
German (de)
English (en)
Other versions
EP0713002B1 (fr
Inventor
Manfred Dipl.-Ing. Kraemer
Gottfried Dipl.-Phys. Kuehne
Uwe Dipl.-Ing. Kuhn (Fh)
Jürgen Dr.-Ing. Maschinenbau Kirschner
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
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Filing date
Publication date
Application filed by Robert Bosch GmbH filed Critical Robert Bosch GmbH
Publication of EP0713002A1 publication Critical patent/EP0713002A1/fr
Application granted granted Critical
Publication of EP0713002B1 publication Critical patent/EP0713002B1/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
    • 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
    • F02M63/02—Fuel-injection apparatus having several injectors fed by a common pumping element, or having several pumping elements feeding a common injector; Fuel-injection apparatus having provisions for cutting-out pumps, pumping elements, or injectors; Fuel-injection apparatus having provisions for variably interconnecting pumping elements and injectors alternatively
    • F02M63/0225—Fuel-injection apparatus having a common rail feeding several injectors ; Means for varying pressure in common rails; Pumps feeding common rails
    • 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
    • F02M59/20—Varying fuel delivery in quantity or timing
    • F02M59/24—Varying fuel delivery in quantity or timing with constant-length-stroke pistons having variable effective portion of stroke
    • F02M59/26—Varying fuel delivery in quantity or timing with constant-length-stroke pistons having variable effective portion of stroke caused by movements of pistons relative to their cylinders
    • F02M59/265—Varying fuel delivery in quantity or timing with constant-length-stroke pistons having variable effective portion of stroke caused by movements of pistons relative to their cylinders characterised by the arrangement or form of spill port of spill contour on the piston
    • 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
    • F02M63/0003—Fuel-injection apparatus having a cyclically-operated valve for connecting a pressure source, e.g. constant pressure pump or accumulator, to an injection valve held closed mechanically, e.g. by springs, and automatically opened by fuel pressure
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02B—INTERNAL-COMBUSTION PISTON ENGINES; COMBUSTION ENGINES IN GENERAL
    • F02B3/00—Engines characterised by air compression and subsequent fuel addition
    • F02B3/06—Engines characterised by air compression and subsequent fuel addition with compression ignition

Definitions

  • the invention is based on a high-pressure fuel pump for internal combustion engines according to the preamble of claim 1.
  • a high-pressure fuel pump known from EP 0 307 947 A2 conveys fuel from a low-pressure chamber into a high-pressure collecting chamber, from which in turn discharge a large number of injection lines to the individual injection valves protruding into the combustion chamber of the internal combustion engine to be supplied (common rail).
  • the known high-pressure pump is designed as a piston pump with a plurality of pump pistons, the pump pistons of which are each guided in a cylinder bore in a cylinder liner and are driven axially back and forth by a common cam drive.
  • the pump pistons delimit a pump working chamber which can be filled with fuel from the low-pressure chamber via a control bore in the wall of the cylinder liner and which is connected to the high-pressure collecting chamber via a pressure line.
  • the high-pressure delivery in the pump workspace begins with the pump piston completely passing over the control bore during its delivery stroke movement, as a result of which a high fuel pressure builds up in the enclosed pump workspace during the further delivery stroke of the pump piston, which pressure valve in the pressure line starts at a certain pressure controls so that the fuel under high pressure is fed into the high-pressure plenum.
  • the high-pressure delivery volume is controlled on the known high-pressure pump by means of a pressure control valve which is used in a bypass line between the pressure line and the low-pressure chamber and is designed there as a solenoid valve and which, depending on the desired delivery volume, pumps the pump work chamber at a certain point in time during the delivery stroke movement of the pump piston Closes the low-pressure chamber and thus initiates the high-pressure delivery, which continues until the top of the pump piston stroke is reached.
  • a pressure control valve which is used in a bypass line between the pressure line and the low-pressure chamber and is designed there as a solenoid valve and which, depending on the desired delivery volume, pumps the pump work chamber at a certain point in time during the delivery stroke movement of the pump piston Closes the low-pressure chamber and thus initiates the high-pressure delivery, which continues until the top of the pump piston stroke is reached.
  • the known high pressure pump has the disadvantage that the control of the delivery rate by means of a solenoid valve provided on each pump piston is relatively complex and expensive.
  • the control of the fuel that is not required at the end of the high-pressure delivery has the disadvantage that the fuel under high pressure enters the low-pressure system, influences the suction process of the individual pump pistons and can cause damage to the walls of the high-pressure pump as a result of the sharp control jet.
  • the high-pressure fuel pump according to the invention with the characterizing features of claim 1 has the advantage that it is possible to deliver fuel under high pressure in a structurally simple manner, in which only the currently required delivery rate is actually promoted.
  • the delivery volume that is not required is pushed out of the pump work space into the pump work space during the delivery stroke of the pump piston before the start of high-pressure delivery, this being done advantageously via the control bore that enables the inlet takes place in the wall of the cylinder liner, so that no additional opening or line must be provided, which reduces the manufacturing effort compared to the known system.
  • the control of the high-pressure delivery rate is advantageously carried out by a variable start of the high-pressure delivery at a constant end of delivery, the start and end of delivery of the high-pressure delivery being controlled by mechanical means.
  • a control recess which is permanently connected to the pump work chamber, is made in the outer surface of the pump piston, the lower edge of which, facing away from the pump work chamber, forms a control edge that controls the start of delivery of the high-pressure delivery.
  • the control edge cooperating with the control bore is arranged obliquely to the pump piston axis, so that a variable useful stroke for high-pressure delivery can be set depending on the rotational position of the pump piston.
  • the delivery end is constant at the top dead center of the pump piston, whereby an additional recess on the pump piston, which is relieved of the residual pressure of the pump work chamber and is connected to the pump work chamber and which covers the control bore in the area of the top dead center of the pump piston, can be provided.
  • Another advantage is the relatively simple adjustment of the rotational position of the pump piston by means of a control rod reached. This is particularly advantageous if a plurality of pump pistons (in-line pump design) arranged in series with one another are provided, which can then be adjusted by means of a single common control rod, wherein the individual pump piston elements can also be easily equalized by using the control sleeves on the pump pistons.
  • FIGS. 1 to 1 show a longitudinal section through the high-pressure fuel pump
  • FIGS. 2 to 6 show the upper part of the pump piston facing the pump working space with five exemplary embodiments of the shape of the control recesses on the pump piston
  • FIGS. 7 to 10 show the pump piston in different delivery stroke positions for the control bore.
  • a cylinder liner 3 is inserted into a pump housing 5, which has a cylinder bore 7 in which a pump piston 9 is guided.
  • the pump piston 9 is driven in a known manner axially back and forth by a cam drive 11 against the force of a return spring 13 and delimits one with its end face 15 facing away from the cam drive 11
  • the pump work space 17 is connected via a radially arranged control bore 19 in the wall of the cylinder liner 3 to a low-pressure space 21, which can be filled with fuel from a fuel storage tank, also not shown, via an inlet line (not shown).
  • a pressure line 25 which contains a pressure valve 23, leads off, which on the other hand opens into a high-pressure collecting chamber 27, from which a plurality of injection lines 29 corresponding to the number of injection points on the internal combustion engine to be supplied to the in FIG discharge the combustion chamber of the internal combustion engine projecting injection valves 31 (common rail system).
  • the pump piston 9 can be rotated in a known manner via a control rod 33 acted upon by an actuator, for which purpose the control rod 33 acts on a control sleeve 35 which is arranged on the pump piston 9 in a manner fixed against rotation.
  • the pump piston 9 has at its end facing the pump workspace a control recess 37 which is permanently connected to the pump workspace 17 and whose lower edge facing away from the pump workspace 17 forms a control edge 39 which, in cooperation with the control bore 19, starts the delivery of the high-pressure delivery in the pump workspace 17 controls and which is arranged obliquely to the pump piston axis, five possible design variants of the shape of the control recess 37 being shown in FIGS. 2 to 6.
  • FIG. 2 shows a first exemplary embodiment of the shape of the control recess 37 on the pump piston 9, which directly adjoins the end face 15 of the pump piston 9 and thus enables an unimpeded fuel flow from the pump work space 17 into the control recess 37.
  • the control edge 39 runs at an angle to the pump piston axis, the size of which depends on the size of the maximum amount of fuel to be delivered.
  • a web 43 forming a head collar is provided between the upper edge 41 of the control recess 37 facing the pump working space 17 and the end face 15 of the pump piston 9, which improves the guidance of the pump piston 9 in the cylinder bore 7 and thus counteracts a so-called "seizure" of the pump piston 9.
  • the hydraulic connection between the control recess 37 and the pump work space 17 takes place in FIG. 3 via an axial groove 45 which opens into the control recess 37 starting from the end face 15.
  • the third exemplary embodiment shown in FIG. 4 differs from the second in the design of the hydraulic connection between the pump working space 17 and the control recess 37, which is formed there by an axial blind bore 47 extending from the end face 15 of the pump piston 9, which is formed by a, in the control recess 37 opening transverse bore 49 is cut in the pump piston 9.
  • the fourth exemplary embodiment shown in FIG. 5 of the shape of the control recess 37 on the pump piston 9 essentially corresponds to the second exemplary embodiment shown in FIG. 3 and in addition to this has a second recess 51 arranged on the side facing away from the pump working space 17 below the control recess 37 , which is designed there as a rectangular pocket, alternatively a transverse groove is also possible.
  • This recess 51 is arranged on the pump piston 9 in such a way that it comes into overlap with the control bore 19 in the upper dead position of the pump piston 9, ie at the end of the conveying stroke movement, the second recess 51 in FIG. 5 being hydraulic via an extension of the axial groove 45 is connected to the control recess 37 and further to the pump work space 17.
  • the third exemplary embodiment shown in FIG. 4 is expanded analogously to FIG. 5 by the second recess 51, which was likewise introduced into the outer surface of the pump piston 9 at the top dead center position of the pump piston 9 and is connected by the axial extension of the blind bore 47 and a second transverse bore 53 opening into the second recess 51 to the pump work chamber 17 adjoining the end face 15 of the pump piston 9.
  • the recesses 37, 53 shown in FIGS. 2 to 6 can be provided in pairs, the recesses 37, 53 then being diametrically opposed and interacting with an associated control bore 19.
  • FIGS. 7 to 10 represents the position of the pump piston 9 with the control recess 37 according to FIG. 2 in different positions relative to the control bore 19 in the wall of the cylinder liner 3.
  • the pump piston 9 in FIG. 7 is in its lower dead position, in which an overflow cross section between the control bore 19 and the pump working space 17 is released along the recess 37. It is also possible to arrange the control bore 19 so that it opens into the pump working space 17 in this stroke position of the pump piston 9 directly above the end face 15 of the pump piston 9. In this piston position at the end of the downward suction stroke movement, the pump work chamber 17 is filled with fuel from the low pressure chamber 21 that is under low pressure.
  • the useful stroke of the pump piston 9 for high-pressure delivery continues up to the top dead center shown in FIG. 10, in which case the high-pressure fuel has completely flowed into the high-pressure collection chamber and the pressure valve 23 closes from a certain drop in the pressure in the pump work chamber 17, so that the end of delivery the high-pressure delivery is the same in every rotational position of the pump piston.
  • the recess 51 can be opened at the top dead center to reduce a possible residual pressure in the pump work space 17, which results in a pressure relief of the pump work space 17, which also has a favorable effect on refilling the pump work space 17.
  • the high-pressure fuel pump according to the invention can represent a variable start of delivery and a fixed end of delivery in a structurally simple manner and thus to limit the high-pressure delivery to the required amount of fuel.

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  • Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Fuel-Injection Apparatus (AREA)
EP95115120A 1994-11-18 1995-09-26 Pompe à combustible haute pression pour moteurs à combustion interne Expired - Lifetime EP0713002B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE4441113 1994-11-18
DE4441113A DE4441113C1 (de) 1994-11-18 1994-11-18 Kraftstoffhochdruckpumpe für Brennkraftmaschinen

Publications (2)

Publication Number Publication Date
EP0713002A1 true EP0713002A1 (fr) 1996-05-22
EP0713002B1 EP0713002B1 (fr) 2002-10-23

Family

ID=6533586

Family Applications (1)

Application Number Title Priority Date Filing Date
EP95115120A Expired - Lifetime EP0713002B1 (fr) 1994-11-18 1995-09-26 Pompe à combustible haute pression pour moteurs à combustion interne

Country Status (3)

Country Link
EP (1) EP0713002B1 (fr)
JP (1) JPH08210223A (fr)
DE (2) DE4441113C1 (fr)

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR2750740A1 (fr) * 1996-07-08 1998-01-09 Mitsubishi Electric Corp Systeme d'injecteurs de carburant

Families Citing this family (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP0863308A1 (fr) * 1997-03-05 1998-09-09 Wärtsilä NSD Schweiz AG Pompe à piston pour refoulement des liquides
JP4616822B2 (ja) * 2006-11-30 2011-01-19 三菱重工業株式会社 エンジンの燃料噴射装置及び運転方法
DE102008050380A1 (de) * 2008-10-02 2010-04-08 Motorenfabrik Hatz Gmbh & Co Kg Einspritzsystem für Dieselkraftstoffe
RU2630953C2 (ru) * 2015-02-11 2017-09-14 Виктор Семенович Савченков Плунжерная пара топливного насоса высокого давления (варианты)

Citations (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB348097A (en) * 1928-11-08 1931-04-28 Hugo Junkers An improved method of and means for controlling the fuel injection in diesel engines
US2044814A (en) * 1934-03-29 1936-06-23 Addison M Rothrock Fuel injection system
GB486378A (en) * 1937-08-31 1938-06-02 Rudolf L Orange Improvements in fuel injection pumps for internal combustion engines
DE940384C (de) * 1938-07-01 1956-03-15 Messerschmitt Boelkow Blohm Brennstoffeinspritzpumpe fuer Brennkraftmaschinen
GB984688A (en) * 1962-02-01 1965-03-03 Suizer Freres Sa Fuel injection pumps for internal combustion engines
DE1942610A1 (de) * 1969-08-21 1971-03-11 Bosch Gmbh Robert Kraftstoffeinspritzanlage fuer Brennkraftmaschinen
EP0307947A2 (fr) 1987-09-16 1989-03-22 Nippondenso Co., Ltd. Pompe haute pression à débit variable

Family Cites Families (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE590916C (de) * 1926-02-27 1934-01-12 E H Hugo Junkers Dr Ing Brennstoffpumpe
DE861762C (de) * 1942-09-29 1953-01-05 Fritz Dipl-Ing Eideneier Leichtoeleinspritzpumpe fuer Brennkraftmaschinen
DE3215046C2 (de) * 1982-04-22 1986-07-31 M.A.N. Maschinenfabrik Augsburg-Nürnberg AG, 8900 Augsburg Brennstoffeinspritzpumpe für Brennkraftmaschinen
JPH04179854A (ja) * 1990-11-13 1992-06-26 Nippondenso Co Ltd 燃料噴射ポンプ

Patent Citations (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB348097A (en) * 1928-11-08 1931-04-28 Hugo Junkers An improved method of and means for controlling the fuel injection in diesel engines
US2044814A (en) * 1934-03-29 1936-06-23 Addison M Rothrock Fuel injection system
GB486378A (en) * 1937-08-31 1938-06-02 Rudolf L Orange Improvements in fuel injection pumps for internal combustion engines
DE940384C (de) * 1938-07-01 1956-03-15 Messerschmitt Boelkow Blohm Brennstoffeinspritzpumpe fuer Brennkraftmaschinen
GB984688A (en) * 1962-02-01 1965-03-03 Suizer Freres Sa Fuel injection pumps for internal combustion engines
DE1942610A1 (de) * 1969-08-21 1971-03-11 Bosch Gmbh Robert Kraftstoffeinspritzanlage fuer Brennkraftmaschinen
EP0307947A2 (fr) 1987-09-16 1989-03-22 Nippondenso Co., Ltd. Pompe haute pression à débit variable

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR2750740A1 (fr) * 1996-07-08 1998-01-09 Mitsubishi Electric Corp Systeme d'injecteurs de carburant

Also Published As

Publication number Publication date
JPH08210223A (ja) 1996-08-20
EP0713002B1 (fr) 2002-10-23
DE4441113C1 (de) 1996-04-04
DE59510432D1 (de) 2002-11-28

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