EP0396127B1 - Appareil d'injection de combustible - Google Patents

Appareil d'injection de combustible Download PDF

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Publication number
EP0396127B1
EP0396127B1 EP90108342A EP90108342A EP0396127B1 EP 0396127 B1 EP0396127 B1 EP 0396127B1 EP 90108342 A EP90108342 A EP 90108342A EP 90108342 A EP90108342 A EP 90108342A EP 0396127 B1 EP0396127 B1 EP 0396127B1
Authority
EP
European Patent Office
Prior art keywords
pump plunger
valve
head
suction
pressure
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
EP90108342A
Other languages
German (de)
English (en)
Other versions
EP0396127A1 (fr
Inventor
Gerhard Dipl.-Ing. Finsterwalder
Reda Rizk
Hans-Gottfried Michels
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.)
Kloeckner Humboldt Deutz AG
Original Assignee
Kloeckner Humboldt Deutz AG
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 Kloeckner Humboldt Deutz AG filed Critical Kloeckner Humboldt Deutz AG
Priority to AT90108342T priority Critical patent/ATE94256T1/de
Publication of EP0396127A1 publication Critical patent/EP0396127A1/fr
Application granted granted Critical
Publication of EP0396127B1 publication Critical patent/EP0396127B1/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
    • F02M59/464—Inlet valves of the check valve type
    • 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 relates to a fuel injection device for a diesel internal combustion engine, in particular according to the preamble of claims 1 and 4.
  • DE-PS 90 11 20 describes a generic fuel injection device which has a suction valve in a pump plunger with a pressure spring which loads the suction valve and which is arranged in the high-pressure chamber of the fuel injection device.
  • a fuel injection device with a suction valve offers the advantage that the high-pressure space is always connected to the fuel pressure of the suction space during the suction stroke of the pump plunger, as a result of which no cavities can form in the high-pressure space.
  • the arrangement of the compression spring in the high-pressure chamber has the advantage that the suction valve is small and can therefore also be accommodated in pump plungers with a relatively small diameter.
  • the invention has for its object to provide a fuel injection device with a suction valve, which has a small harmful volume in the high pressure chamber and makes the use of small pump plunger possible.
  • An advantageous embodiment of the invention according to claim 1 ensures that the turns of the conical compression spring are pushed into one another during the upward movement of the pump plunger and thus the harmful space of the conical compression spring is minimized in the compressed state. It can be advantageous to design the conical compression spring with only one turn. However, cases are also conceivable in which several spring turns are advantageous.
  • the spring windings can have the same or different slopes. This arrangement has the effect that the conical compression spring is compressed into a disc with its diameter when the pump plunger is moving upward. As a result, the conical compression spring takes up practically no additional, harmful volume.
  • the conical compression spring is usually punched out of a spring steel washer. However, it can also be advantageous to manufacture them from plastic.
  • valve cone achieves a smooth pump plunger base, which is an important prerequisite for minimizing the harmful volume in the high pressure area.
  • An advantageous embodiment of the invention realizes a self-centering suction valve without special guide elements.
  • the embodiment of the invention according to claim 4 ensures that the suction valve in the pump plunger without spring is opened and closed only by taking advantage of the inertia of the suction valve body and the pressure gradient between the high-pressure chamber and the suction chamber of the fuel injection device.
  • the stroke movement of the suction valve body is limited by a stroke limiting means.
  • a further embodiment according to the invention offers the advantage of a particularly low harmful volume, since the pin with a square cross section used as a stroke limiter is arranged flush in the valve base and thereby enables a particularly small depth of the rectangular groove in the valve cone base.
  • Both embodiments of the stroke limiting means offer the advantage that they do not require a seal from the high-pressure space, since they are located in it.
  • stroke limiting means for. B. a stop ring above the valve cone bottom or below of the valve cone. All solutions with stroke limiting means do not require a compression spring.
  • An advantageous development of the invention brings about a secure flow connection of the high-pressure chamber to the suction chamber of the fuel injection device during the time in which the inlet bore is still closed by the pump plunger.
  • the annulus serves as a return oil leakage, which prevents the dilution of lubricating oil by fuel.
  • An advantageous development of the invention significantly reduces the harmful volume in the high-pressure area of the fuel injection device.
  • a prerequisite for the omission of the pressure valve is the suction valve according to the invention, by means of which an overpressure at the level of the suction chamber pressure is always ensured in the high pressure chamber during the downward movement of the pump plunger. In spite of the lack of a pressure or relief valve, this relieves the pressure on the injection line to the suction chamber pressure and prevents the injection line from being sucked dry and prevents cavities from forming.
  • the arrangement according to the invention leads to a particularly simple construction with low manufacturing and maintenance expenditure, which is also suitable for small pump plungers.
  • the small, harmful volume results in high hydraulic rigidity, which enables the high injection pressures that modern diesel engines require for combustion and emissions reasons.
  • the fuel injection device consists, among other things, of a plunger bushing 2 in which a pump plunger 1 is guided in a sealing manner.
  • the plunger bushing 2 is terminated at the high-pressure end by a plunger bushing end 4, from which a high-pressure line 18 leads to the pressure connection 19.
  • a plunger bushing end 4 from which a high-pressure line 18 leads to the pressure connection 19.
  • the inlet bore 16 in the plunger bushing 2 from which a connecting line 15 located in the plunger bushing 2 and extending obliquely in the direction of the pump plunger 1 branches off.
  • the inlet bore 16 opens into a suction chamber 21, which is supplied with fuel by a low-pressure pump, not shown, via a pressure valve 23 and is kept at a specific admission pressure by a pressure-maintaining valve 22.
  • the pressure valve 23 and the pressure holding valve 22 are designed to be particularly tight-closing in order to prevent the fuel injection device from running dry while the internal combustion engine is at a standstill and to prevent the resulting starting difficulties.
  • the pump plunger 1 has a pump plunger base 3, into which the conical valve seat 25 of a suction valve body 10 is incorporated.
  • the suction valve body 10 has a valve cone base 11, which forms a smooth surface together with the pump plunger base 3 when the suction valve 6 is closed.
  • a plunger bore 12 extends from the valve seat 25 of the suction valve 6 and a transverse bore 13 branches off from its end.
  • the transverse bore 13 opens into an annular space 14 arranged on the circumference of the pump plunger 1, which is connected to the connecting line 15 at least in the stroke area of the pump plunger 1 is in flow connection in which the high-pressure delivery takes place.
  • the pump plunger 1 and the plunger bushing 2 delimit a high-pressure chamber 5.
  • a conical compression spring 7 with a rectangular or square spring wire cross section is arranged in the high-pressure chamber 5.
  • the high-pressure chamber 5 is in temporary flow connection with an injection valve 9 via the high-pressure line 18, the pressure connection 19 and the injection line 8 with a suction chamber 21 via the inlet bore 16 or the connecting line 15, namely only when no high-pressure delivery takes place.
  • the fuel injector works as follows:
  • the suction valve 6 is closed. After completion of the suction bore 16 through the pump plunger 1, the high-pressure delivery begins. The fuel is displaced from the high-pressure chamber 5 and passes between the windings of the conical compression spring 7 via the high-pressure line 18, the injection line 8, and the injection valve 9 into the combustion chamber (not shown).
  • the conical compression spring 7 is compressed so that it forms a disk at the top dead center of the pump plunger 1.
  • the spring coils are designed in such a way that there is only a minimal distance between them in the compressed state and thus only a minimally harmful space.
  • the suction valve 6 opens due to the excess pressure in the suction space 21 and supplies the high-pressure space 5 with fuel via the connecting line 15, the annular space 14, the transverse bore 13 and the plunger bore 12.
  • the high-pressure chamber 5 is again in direct connection with the suction chamber 21, so that this closes due to the lack of differential pressure at the suction valve 6.
  • the suction valve 6 is therefore only open as long as the inlet bore 16 is closed when the pump plunger 1 is in the downward direction.
  • the suction valve 6 is closed before the high-pressure delivery begins. This begins when the inlet bore 16 is closed. This gives an exact and constant start of the injection.
  • suction valve 6 Since the suction valve 6 is only opened and closed with a low differential pressure, it is not exposed to any significant stress and therefore not to wear.
  • suction valve 6 An important advantage of the suction valve 6 is the fact that no negative pressure occurs in the high-pressure chamber 5 during the downward movement of the pump plunger 1. It is therefore possible to dispense with a pressure or relief valve in the high-pressure region of the fuel injection device without the injection line 8 being sucked empty and cavitation forming. In the high-pressure area of the fuel injection pump, the suction space pre-pressure to which the high-pressure area is relieved always prevails during the downward movement of the pump plunger 1.
  • Another important advantage of the solution according to the invention is the simplicity of the construction. This is characterized by a simple suction valve body 10, which can also be accommodated in small pump plungers 1, a conventional pump plunger version in which the annular space 14 together with the connecting line 15 also takes over the function of the leakage oil return and finally by the elimination of the pressure valve and its screwing, which are caused by an integrated pressure port 19 are replaced. Simplified through all these measures and The fuel injection device according to the invention becomes cheaper in manufacture and maintenance compared to a commercially available design.
  • FIGS. 2 and 3 A further possibility for realizing a space-saving suction valve in the pump plunger which causes little harmful volume is shown in FIGS. 2 and 3.
  • a suction valve 6a, 6b is provided with a valve body 10a, 10b, the stroke movement of which is not controlled by a spring, but is limited by a pin 28, 28a.
  • the pin 28 with a round cross section is arranged in a pin bore 29 with a slight press fit.
  • the pin bore 29 is located just below the pump plunger base 3a. It intersects the axis of the pump plunger 1a.
  • the pin 28a with a square cross section is fastened in a pin groove 31 with the same cross section in the region of the pump plunger base 3b.
  • the attachment is carried out by welding, preferably by laser beam welding.
  • the pin 28 with the round cross section is operatively connected to a groove 30 of a valve cone 27a of the suction valve body 10a, and accordingly the pin 28a with the square cross section is operatively connected to a rectangular groove 32 of a valve cone 27b of the suction valve body 10b.
  • the suction valve bodies 10a, 10b have a guide part 33 with the axial grooves for the fuel flow shown in FIG. 2b.
  • the guide part 33 is guided in the plunger bore 12. It serves for an exact guidance of the suction valve body 10a, 10b and thus for a secure sealing of the suction valves 6a, 6b.
  • the opening and closing movement of the suction valve bodies 10a, 10b is triggered by their inertia in connection with the stroke movement of the pump plungers 1a, 1b and is temporarily unsupported by the pressure difference between the high pressure chamber 5 and the suction chamber 21.
  • the pump plunger 1a, 1b reduces its speed to 0, while the suction valve bodies 10a, 10b continue to move at the high plunger speed and in this way the suction valves 6a, 6b open. Supported by the pressure difference between the high pressure chamber 5 and the suction chamber 21, these remain open during the downward thrust of the pump plunger 1a, 1b.

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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)

Claims (7)

  1. Dispositif d'injection de carburant, de préférence pour des moteurs à combustion interne Diesel, avec un arbre qui entraîne au moins un piston plongeur de pompe (1), qui comporte un fond de piston plongeur de pompe (3) et qui est guidé de façon étanche dans une douille de piston plongueur de pompe (2) et délimite conjointement avec celle-ci ainsi qu'avec une fermeture de douille de piston plongeur de pompe (4) une chambre haute pression (5), qui par l'intermédiaire d'une canalisation d'injection (8) est en liaison d'écoulement avec une soupape d'injection (9), tandis que dans le piston plongeur de pompe (1) est disposée, au voisinage du fond (3) de ce piston plongeur de pompe, une soupape d'aspiration (6) avec un corps de soupape d'aspiration (10), et le corps de soupape d'aspiration (10) comporte un cône de soupape (27) avec un fond de cône de soupape (11), qui est chargé par un ressort de pression de soupape d'aspiration disposé dans la chambre haute pression (5), cependant que le corps de soupape d'aspiration (10) est susceptible d'être déplacé à l'intérieur de la chambre haute pression (5) et relie ainsi celle-ci à une chambre d'aspiration (21), dispositif d'injection de carburant caractérisé en ce que le piston plongeur de pompe (1) prévu à au moins un exemplaire, est entraîné contre l'action d'un ressort de pression par une came d'un arbre à came pour établir la pression d'injection, et en ce que le ressort de pression de la soupape d'aspiration revêt la forme d'un ressort de pression en forme de cône (7) avec des spires (26) élastiques ainsi qu'avec une extrémité pointue (7a) et une extrémité tronquée (7b), l'extrémité pointue (7a) coopérant avec le fond du cône de soupape (11) tandis que l'extrémité tronquée (7b) coopère avec la fermeture (4) de la douille du piston plongeur de pompe, et les spires du ressort de pression (7) sont réalisées de façon qu'elles soient poussées les unes dans les autres lors de la course de la pompe du piston plongeur de pompe.
  2. Dispositif d'injection de carburant selon la revendication 1, caractérisé en ce que le ressort de pression en forme de cône (7), qui comporte un fil métallique de ressort avec une section transversale de préférence, rectangulaire, forme dans la position de point mort haut du piston plongeur de pompe (1), un disque à peu près plan qui est à une distance minimale du fond (3) du piston plongeur de pompe et de la fermeture (4) de la douille du piston plongeur de pompe, tandis que le diamètre externe de l'extrémité tronquée (7b) du ressort de pression conique (7) correspond approximativement au diamètre du piston plongeur de pompe (1) et que ces différentes spires (26) sont disposées, à l'état comprimé, à une distance réciproque minimale.
  3. Dispositif d'injection de carburant selon une des précédentes revendications, caractérisé en ce que le fond (11) du cône de soupape forme avec le fond (3) du piston plongeur de pompe, une surface lisse à peu près continue lorsque la soupape d'aspiration (6) est fermée.
  4. Dispositif d'injection de carburant, de préférence pour des moteurs à combustion interne Diesel, avec un arbre qui entraîne au moins un piston plongeur de pompe (la, 1b), lequel comporte un fond de piston plongeur de pompe (3a, 3b) et est guidé de façon étanche dans une douille de piston plongeur de pompe (2) et délimite avec celle-ci ainsi qu'avec une fermeture de douille de piston plongeur de pompe (4), une chambre haute pression (5), qui par l'intermédiaire d'une canalisation d'injection (8) est en liaison d'écoulement avec une soupape d'injection (9), tandis que dans le piston plongeur de pompe (1a, 1b), au voisinage du fond (3a, 3b) de ce piston plongeur de pompe, est disposée une soupape d'aspiration (6a, 6b) avec un corps de soupape d'aspiration (10a, 10b), et ce corps de soupape d'aspiration (10a, 10b) comporte un cône de soupape (27a, 27b) avec un fond de cône de soupape (11a, 11b), cependant que le corps de soupape d'aspiration (10a, 10b) est susceptible d'être déplacé à l'intérieur de la chambre haute pression (5), et relie ainsi cette chambre haute pression (5) à une chambre d'aspiration (21), tandis que la course du corps de soupape d'aspiration (10a, 10b) est limitée par un moyen de limitation de course, dispositif caractérisé en ce que le piston plongeur de pompe (1a, 1b) existant à au moins un exemplaire est entraîné par un arbre à came par l'intermédiaire d'un poussoir à galets contre l'action d'un ressort de pression et en ce que le moyen de limitation de la course pour le corps de soupape d'aspiration (10a, 10b) est prévu au voisinage du fond conique de soupape (11a, 11b), et en ce que la soupape d'aspiration (6a, 6b) est ouverte et fermée sans l'intervention d'un ressort et uniquement en utilisant l'inertie de masse du corps de soupape d'aspiration (10a, 10b) et la chute de pression entre la chambre haute pression (5) et la chambre d'aspiration (21).
  5. Dispositif d'injection de carburant selon la revendication 4, caractérisé en ce que comme moyen de limitation de la course, il est prévu une broche (28) de section transversale ronde, qui est disposée, d'une part, sans jeu dans un perçage (29) du piston plongeur de pompe (la) à la distance minimale du fond (3a) du piston plongeur de pompe compatible avec la solidité de ce piston, et, d'autre part, avec du jeu dans une gorge (30) du fond (11a) du cône de soupape, cependant que ce fond (11a) du cône de soupape se situe à peu près dans le plan du fond (3a) du piston plongeur de pompe lorsque la soupape d'aspiration (6a) est fermée.
  6. Dispositif d'injection de carburant selon la revendication 5, caractérisé en ce que le perçage (29), en partant d'une gorge de commande (17) disposée à la périphérie du piston plongeur de pompe (1a), croise à angle droit l'axe du piston plongeur de pompe (1a) et se termine en tant que perçage borgne à l'intérieur du contour du piston plongeur de pompe (1a).
  7. Dispositif d'injection de carburant selon la revendication 4, caractérisé en ce qu'il est prévu comme moyen de limitation, une broche (28a) ayant de préférence une section transversale quadratique et qui est fixée sans jeu et, de préférence, par soudage, dans une gorge de broche (31) de même section transversale, usinée dans le fond (3b) du piston plongeur de pompe, et cette broche coopère, avec du jeu, avec une gorge rectangulaire (32) du fond (11b) du cône de soupape, ce fond (11b) de cône de soupape, le fond (3b) du piston plongeur de pompe et la face supérieure de la broche (28a) se situant à peu près dans un même plan lorsque la soupape d'aspiration (6b) est fermée.
EP90108342A 1989-05-03 1990-05-03 Appareil d'injection de combustible Expired - Lifetime EP0396127B1 (fr)

Priority Applications (1)

Application Number Priority Date Filing Date Title
AT90108342T ATE94256T1 (de) 1989-05-03 1990-05-03 Kraftstoffeinspritzvorrichtung.

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE3914582A DE3914582A1 (de) 1989-05-03 1989-05-03 Brennstoffeinspritzvorrichtung
DE3914582 1989-05-03

Publications (2)

Publication Number Publication Date
EP0396127A1 EP0396127A1 (fr) 1990-11-07
EP0396127B1 true EP0396127B1 (fr) 1993-09-08

Family

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Family Applications (1)

Application Number Title Priority Date Filing Date
EP90108342A Expired - Lifetime EP0396127B1 (fr) 1989-05-03 1990-05-03 Appareil d'injection de combustible

Country Status (4)

Country Link
US (1) US5135367A (fr)
EP (1) EP0396127B1 (fr)
AT (1) ATE94256T1 (fr)
DE (2) DE3914582A1 (fr)

Families Citing this family (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2884454B2 (ja) * 1991-11-20 1999-04-19 株式会社ゼクセル 燃料噴射ポンプ用プランジャのリード加工法
GB9207986D0 (en) * 1992-04-10 1992-05-27 Lucas Ind Plc Fuel pump
DE4225803A1 (de) * 1992-08-05 1994-02-10 Bosch Gmbh Robert Kraftstoffeinspritzpumpe für Brennkraftmaschinen
US6135073A (en) * 1999-04-23 2000-10-24 Caterpillar Inc. Hydraulic check valve recuperation

Citations (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP0195175A1 (fr) * 1985-02-15 1986-09-24 WEBER S.r.l. Pompe d'injection de combustible pour moteurs diesel

Family Cites Families (10)

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Publication number Priority date Publication date Assignee Title
US1640579A (en) * 1925-07-27 1927-08-30 Frank W Severin Fuel-feed mechanism for oil engines
US1900385A (en) * 1926-03-05 1933-03-07 Franklin Valveless Engine Comp Fuel feeding means
DE598094C (de) * 1932-05-05 1934-06-05 Wagner Otto Mehrstempelbrennstoffpumpe fuer mehrzylindrige Brennkraftmaschinen
US2101221A (en) * 1932-12-05 1937-12-07 Frederick Richard Simms Liquid fuel pump
DE735206C (de) * 1936-06-17 1943-05-08 Rudolf L Orange Dipl Ing Kolbenpumpe zum Einspritzen von Brennstoff
DE901120C (de) * 1944-05-16 1954-01-07 Verwertungsgesellschaft Dr Ing Einspritzpumpe mit Mengensteuerung ohne Rueckstroemung
US2633082A (en) * 1950-06-14 1953-03-31 Arthur E Mcfarland Fluid feeding apparatus
FR1407851A (fr) * 1964-06-19 1965-08-06 Labo Cent Telecommunicat Perfectionnements aux circulateurs pour liquides
US3692438A (en) * 1969-10-21 1972-09-19 Rodney E Schapel Positive displacement pump
FR2481752A1 (fr) * 1980-04-30 1981-11-06 Renault Vehicules Ind Amelioration des dispositifs mecaniques d'injection de combustible, notamment pour des moteurs diesel

Patent Citations (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP0195175A1 (fr) * 1985-02-15 1986-09-24 WEBER S.r.l. Pompe d'injection de combustible pour moteurs diesel

Also Published As

Publication number Publication date
DE3914582A1 (de) 1990-11-08
ATE94256T1 (de) 1993-09-15
US5135367A (en) 1992-08-04
EP0396127A1 (fr) 1990-11-07
DE59002609D1 (de) 1993-10-14

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