EP0261154B1 - Pompe a injection de carburant pour moteurs a combustion interne - Google Patents

Pompe a injection de carburant pour moteurs a combustion interne Download PDF

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Publication number
EP0261154B1
EP0261154B1 EP87901395A EP87901395A EP0261154B1 EP 0261154 B1 EP0261154 B1 EP 0261154B1 EP 87901395 A EP87901395 A EP 87901395A EP 87901395 A EP87901395 A EP 87901395A EP 0261154 B1 EP0261154 B1 EP 0261154B1
Authority
EP
European Patent Office
Prior art keywords
shaft
pump
shaft part
fuel injection
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
EP87901395A
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German (de)
English (en)
Other versions
EP0261154A1 (fr
Inventor
Walter Häfele
Manfred KRÄMER
Johann Warga
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 EP0261154A1 publication Critical patent/EP0261154A1/fr
Application granted granted Critical
Publication of EP0261154B1 publication Critical patent/EP0261154B1/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
    • 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
    • F02M59/243—Varying fuel delivery in quantity or timing with constant-length-stroke pistons having variable effective portion of stroke caused by movement of cylinders relative to their pistons
    • F02M59/246—Mechanisms therefor
    • 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
    • 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

Definitions

  • the invention relates to a fuel injection pump for internal combustion engines according to the preamble of the main claim.
  • the exact and also synchronous control of the control slide is important for the injection quality and thus the combustion quality in the engine.
  • Higher loads on the torsion shaft such as occur during jerky twisting, can lead to a slight bending of the torsion shaft, which not only falsifies the synchronization of the individual control slides to one another, but also considerable additional friction can occur at the bearing points of the torsion shaft. Since the shaft is rotated by a controller, the adjustment forces of which are sensitive and dependent on the speed, variable frictional forces in particular have a negative effect on the control quality.
  • the fuel injection pump according to the invention with the characterizing features of the claim has the advantage that no bending stresses are transmitted to the bearings due to the cardanic rotational connection between the two shaft parts.
  • the bearing of the second shaft part on the drive side of the torsion shaft can work stress-free and therefore almost frictionless. Due to this lateral force relief, the bearing between the second shaft part and the pump housing can be designed in a very fine fit, as is common, for example, between the injection pump piston and the cylinder, so that there is extensive tightness against fuel outflow from the injection pump into the regulator.
  • the one shaft part on the coupling side has a slightly convex end pin which runs in the shaft axis and is mounted in a corresponding blind hole on the end side of the other shaft part.
  • the shaft parts each have an expanded section on the mutually facing end faces, for example a collar on which driving claws or recesses are provided for the rotational connection.
  • a collar on which driving claws or recesses are provided for the rotational connection e.g. a large collar, on which an axial nose is attached, which engages in a corresponding recess of the opposite collar, creates a favorable lever arm for taking along without adverse transverse forces.
  • the second shaft part is mounted in a central bore of a bearing bush, which is arranged in a pump housing bore by means of sealing rings and in which an oil ring groove with an relief channel leading to the outside is present in the central bore, advantageously the second shaft part is guided in this central bore in the manner of an injection pump element seal. Since there is hardly any axial movement of the second shaft part, little fuel will leak through between the shaft and the bore if the fit is good. These small quantities are then caught and drained through the oil ring groove, so that no diesel fuel from the injection pump gets into the regulator, in which it could inadmissibly dilute the lubricating oil present there (leakage fuel return).
  • a shaft end runs at the free end of the first shaft part in a blind bore of a bearing cover inserted in a bore of the pump housing, a pin located at the shaft end also being spherical here.
  • the spherical design enables tension-free turning of the adjustment shaft.
  • annular groove is present in the shaft end dipping into the blind bore, into which a locking pin arranged in the bearing cover or housing engages as a safeguard against axial displacement of the first shaft part.
  • EP-A-0 0150 343 describes a fuel injection pump in which the control rod mounted at both ends in the housing is divided between the bearings (see FIGS. 3, 4, 6 and 7).
  • a longitudinally displaceable control rod is divided into a first control rod part, which has free ends in the pump housing and a second control rod part, which, however, is non-positively, i.e. firmly coupled to the first control rod part and sealed in the pump housing, and one is sealed forms radial guidance for the end of the first control rod part facing it.
  • the guide collars provided for guiding the second control rod part are very short, that is to say they are narrower than their diameter, so that only "quasi-cardanic" mounting can be achieved. Since, due to this short guide length, the corresponding sealing gap is also relatively short, a relatively good seal, which is not suitable for all applications and especially not suitable for a rotary shaft, can be achieved with such a construction.
  • FIG. 1 shows a longitudinal section through a fuel injection pump according to the invention along line I-I in FIG. 2; 2 shows a cross section through this pump along line 11-11 in FIG. 1, only one pump piston and control slide being shown in cross section, and FIGS. 3 and 4 end shields of the adjusting shaft according to section 111-111 in FIG. 2 and according to view IV in Fig. 2.
  • cylinder liners 2 are embedded in series in a housing 1, in each of which a pump piston 3, with the interposition of a roller tappet 4 with roller 5, is driven by a camshaft 6 against the force of a spring 7 for its axial movement forming the working stroke.
  • Partial suction chambers 8 are formed by cutouts in the cylinder liners 2, each of which is assigned to a pump element formed from the cylinder liner 2 and the pump piston 3.
  • a control slide 9 is arranged axially displaceably on the pump piston 3.
  • the individual partial suction chambers 8 open on the outlet side into a main suction chamber 10 which extends over the length of the housing 1 and is closed at its longitudinal ends by end shields 11.
  • a rotating shaft 12 is arranged, which is rotatably mounted in the end shields 11 and through which the control slide 9 are displaceable.
  • driving pins 14a In transverse bores of the rotating shaft 12 there are radially protruding driving pins 14a, each of which engages in a groove 13 of the control slide 9, namely as end sections of an eccentric bolt 14, which can be fixed in position on the rotating shaft 12 by means of a clamping nut 15.
  • a locking plug 16 of which only two are shown in FIG. 2, is provided in each case opposite these clamping nuts 15, after removal of which an adjustment of the individual driving pins 14a after loosening and tightening the clamping nut 15 is possible, in order in this way the individual control slides 9 to adjust to each other.
  • These oblique grooves 24 interact with radial bores 25 of the control slide 9 in that they are opened by these radial bores 25 after a certain stroke of the pump piston 3 and thus serve as control openings.
  • a guide pin 26 is arranged in the cylinder liner 2, which engages in a longitudinal groove 27 of the control slide 9.
  • the pump piston 3 has at its lower section a flattened area 28 on which a driving member 31, which can be rotated by a control rod 29 in a known manner, engages, so that an axial displacement of the control rod 29, a rotation of the pump piston 3 and thus a change in the assignment of the oblique grooves 24 to the radial bores 25.
  • a suction hole 32 is provided, which is exposed by the pump piston 3 in its bottom dead center position (as shown in the drawing).
  • the fuel supply to the individual partial suction chambers 8 takes place through an inflow channel 33 which runs in a pipe 34 laid in the housing 1.
  • this tube 34 there are radial branch openings 35 which open into openings 36 connected to the partial suction chambers 8.
  • the torsion shaft 12 consists of two shaft parts which are connected to one another in a rotationally locking manner via a claw coupling 37, namely a first shaft part 38 which supports the eccentric bolts 14 and a second shaft part 39 which acts on the regulator from outside the pump.
  • the two shaft parts 38 and 39 are axially inserted into one another, for which purpose a blind hole 40 is provided in the corresponding end face of the first shaft part 38 and there is a slightly curved pin 41 which plunges into this blind hole 40 and which provides a support for this end of the first shaft part 38.
  • the two mutually facing end faces of the shaft parts are widened like a flange, so that two frets 42 lie opposite one another. While a claw 43 is located on one collar, a corresponding recess 44 is provided on the other collar.
  • the second shaft part 39 itself is mounted in a central bore 45 of a bearing bush 46, which is inserted in the housing bore receiving this end shield and is held by a screw 47. Between the housing 1 and this bearing bush 46 are two rings 48 available. An oil ring groove 49 is arranged in the central bore 45, from which a relief channel 51 branches off. This second shaft part 39 is guided in the central bore 45 with very little play, as is the case, for example, when guiding the pump piston in the cylinder. The oil ring groove 49 collects the fuel that may still leak through from the main suction chamber 10 and discharges it via the relief channel 51 in order not to get into the regulator housing filled with lubricating oil (leakage fuel return).
  • a shaft end 54 of the first shaft part 38 is mounted in a blind bore 52 of the second bearing plate 11 designed as a bearing cover 53.
  • the shaft end 54 has a pin 54a, which is also crowned to have only line contact for storage, so that slight bending of the shaft part 38 or an incorrectly aligned installation position of the bearing cover 53 does not lead to any additional frictional forces.
  • the axial position of the first shaft part 38 is secured by a pin 55 which engages in an annular groove 56 of the shaft part 38 and is arranged in the bearing cover 53.
  • a flattening 57 is present on the shaft end 54 between the ring groove 56 and the pin 54a, which reaches approximately the same depth as the ring groove 56. This makes it possible to push this free end of the first shaft part 38 into the blind bore 52 at the location of the flattened portion 57 in order to then turn the shaft part 38 in a bayonet-like manner so that the pin 55 engages in the annular groove 56.
  • the bearing cover 53 is fastened to the housing by screws 58.
  • the rotation shaft 12 is assembled as follows: First, the first part 38 of the rotation shaft is pushed into the pump housing, namely rotated by 90 degrees with respect to the operating position. Then this shaft is rotated back into the working position by 90 degrees and inserted with the driving pins 14a into the grooves 13 of the control slide 9. Then the two end shields are mounted, namely the bearing cover 53 in the manner described by bayonet-like turning, then the bearing bush 46 with the second shaft part 39 already installed.

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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)

Abstract

Pompe à injection de carburant pour moteurs à combustion interne équipé de plusieurs éléments de pompe (2, 3) disposés en série, dans laquelle le déclenchement de l'injection est réalisé par un distributeur (9) qui se glisse axialement sur le piston (3) de la pompe et en agissant sur les canaux de décharge (22 à 25) des chambres de travail (18) de la pompe. Les distributeurs (9) de la pompe sont entraînés au moyen d'un arbre de torsion (12) conçu en deux parties, notamment une première partie (38) d'arbre qui de préférence est immobilisée dans le sens axial, et une deuxième partie (39) d'arbre qui est introduite de manière étanche dans un manchon de palier disposé dans le boîtier. L'une des deux parties d'arbre est introduite dans l'autre grâce à un goujon (41) et un trou borgne (40) disposés sur les faces mutuellement opposées des extrémités, et sont reliés par un crabotage (43, 44) qui les bloque pendant la rotation.

Claims (8)

1. Pompe d'injection de carburant pour moteurs à combustion interne à plusieurs éléments de pompe disposés en ligne dans un carter de pompe (1) et entraîné par un arbre à cames (6) commun, chacun comprenant un piston de pompe (3) et une chemise cylindrique (2) et délimitant un espace de travail de la pompe (18),
-avec un tiroir de distribution (9) mobile axialement sur chaque piston (3), commandant au moins une ouverture de commande (24) en liaison avec un alésage central borgne (22) du piston (3) ouvert vers l'espace de travail de la pompe (18) et débouchant dans la surface enveloppe du piston (3),
-avec un espace d'aspiration (8, 10) entourant les tiroirs de distribution individuels (9), limité par le carter de pompe, parcouru par le carburant à faible pression et,
-avec un arbre de rotation (12) prévu pour une action simultanée sur tous les tiroirs de distribution (9) pour le début et la fin du refoulement, avec double logement par palier dans le carter de pompe et accouplé avec les tiroirs de distributions (9) par des tourillons d'entraînement (14) ajustables, caractérisé en ce que l'arbre de rotation (12) est divisé entre ses paliers (11), à savoir, en une première partie d'arbre (38) supportant les tourillons d'entraînement (14a), logée dans le carter de pompe (1) par son extrémité libre et pouvant pivoter et une deuxième partie d'arbre (39), qui est accouplée à la première partie d'arbre (38), pour assurer la continuité de rotation, est de même logée sur palier d'une façon étanche dans le carter de pompe et forme un guidage radial (40, 41) pour l'extrémité de la première partie d'arbre (38) tournée vers elle et en ce que comme guidage radial, cette partie d'arbre (39) comprend sur le côté de l'accouplement un tourillon (41) axé sur l'arbre et légèrement bombé qui est logé dans un alésage borgne (40) correspondant sur la face frontale de l'autre partie d'arbre (38).
2. Pompe d'injection de carburant selon la revendication 1, caractérisée en ce que les parties d'arbres (38, 39) présentent sur leurs faces frontales tournées l'une vers l'autre chacune un tronçon (42) élargi radialement, sur lesquels existent des pattes d'entraînement (43) ou des creux d'entraînement (44) pour assurer la rotation.
3. Pompe d'injection de carburant suivant l'une ou l'autre des revendications précédentes, caractérisée en ce que la deuxième partie d'arbre (39) est logée dans l'alésage central (45) d'un coussinet (46) qui est disposé dans un alésage du carter de pompe isolé radialement par un anneau d'étanchéité (48), et en ce qu'il existe dans l'alésage central (45) une rainure annulaire pour huile (49) avec un canal de décharge (51) pour récupérer le carburant de fuite.
4. Pompe à injection de carburant selon la revendication 3, caractérisé en ce que la deuxième partie d'arbre (39) est guidée dans l'alésage central (45) à la façon d'une garniture d'étanchéité d'élément de pompe utilisée pour pompes à injection.
5. Pompe à injection de carburant selon une quelconque des revendications précédentes, caractérisée en ce qu'une extrémité d'arbre (54) à l'extrémité libre de la première partie d'arbre (38) tourne dans un alésage borgne (52) d'un chapeau de palier (53) enfilé dans un alésage du carter de pompe (1).
6. Pompe à injection de carburant selon la revendication 5, caractérisée en ce qu'un tourillon (54a) situé à l'extrémité d'arbre (54) est réalisé bombé.
7. Pompe à injection de carburant selon l'une ou l'autre des revendications 5 ou 6, caractérisée en ce qu'il existe à l'extrémité de l'arbre (54) placée dans l'alésage borgne (52), une rainure annulaire (56), dans laquelle entre une cheville de sécurité (55) disposée dans le chapeau de palier (53) comme sécurité contre un déplacement axial de la première partie d'arbre (38).
8. Pompe à injection de carburant selon la revendication 7, caractérisée en ce que l'extrémité de l'arbre (54) comporte un plat (57) jusqu'à environ la base de la rainure annulaire, de sorte que après introduction de cette extrémité de l'arbre dans l'alésage borgne (52) et le passage de ce plat (57) au-delà de la goupille (55), a lieu un ancrage axial par torsion relative du type baïonnette de la première partie d'arbre (38) par rapport au chapeau de palier (53).
EP87901395A 1986-03-22 1987-03-19 Pompe a injection de carburant pour moteurs a combustion interne Expired - Lifetime EP0261154B1 (fr)

Applications Claiming Priority (4)

Application Number Priority Date Filing Date Title
DE3609760 1986-03-22
DE3609760 1986-03-22
DE3630799 1986-09-10
DE19863630799 DE3630799A1 (de) 1986-03-22 1986-09-10 Kraftstoffeinspritzpumpe fuer brennkraftmaschinen

Publications (2)

Publication Number Publication Date
EP0261154A1 EP0261154A1 (fr) 1988-03-30
EP0261154B1 true EP0261154B1 (fr) 1990-05-30

Family

ID=25842233

Family Applications (1)

Application Number Title Priority Date Filing Date
EP87901395A Expired - Lifetime EP0261154B1 (fr) 1986-03-22 1987-03-19 Pompe a injection de carburant pour moteurs a combustion interne

Country Status (7)

Country Link
US (1) US4842497A (fr)
EP (1) EP0261154B1 (fr)
JP (1) JPS63502915A (fr)
KR (1) KR880701327A (fr)
BR (1) BR8706767A (fr)
DE (2) DE3630799A1 (fr)
WO (1) WO1987005664A1 (fr)

Families Citing this family (10)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE3844430A1 (de) * 1988-12-31 1990-07-05 Bosch Gmbh Robert Kraftstoffeinspritzpumpe fuer brennkraftmaschinen
DE4041503C2 (de) * 1990-12-22 2001-02-15 Bosch Gmbh Robert Kraftstoffeinspritzpumpe für Brennkraftmaschinen
DE4140759A1 (de) * 1991-12-11 1993-06-17 Bosch Gmbh Robert Kraftstoffeinspritzpumpe fuer brennkraftmaschinen
DE4143040C1 (fr) * 1991-12-24 1993-07-08 Robert Bosch Gmbh, 7000 Stuttgart, De
DE4227854B4 (de) * 1992-08-22 2005-12-15 Robert Bosch Gmbh Kraftstoffeinspritzpumpe für Brennkraftmaschinen
DE19712872A1 (de) * 1997-03-27 1998-10-01 Bosch Gmbh Robert Pumpe, insbesonder Hochdruckpumpe für eine Kraftstoffeinspritzvorrichtung eines Verbrennungsmotors
JP2000130279A (ja) * 1998-10-21 2000-05-09 Toyota Motor Corp 内燃機関の高圧燃料供給装置
US6871629B2 (en) * 2001-07-31 2005-03-29 Thermo King Corporation Refrigeration system with low-fuel shutdown
US7311087B2 (en) * 2004-11-23 2007-12-25 Cummins Inc. Fuel pump with a guided tappet assembly and methods for guiding and assembly
GB2554731B (en) * 2016-10-07 2019-04-03 Caterpillar Motoren Gmbh & Co Piston pump having push rod assembly and stopping assembly

Family Cites Families (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2110314A (en) * 1934-12-03 1938-03-08 Citroen Sa Andre Pump for injection engines
US3385221A (en) * 1967-03-07 1968-05-28 Caterpillar Tractor Co Multi-plunger engine fuel oil pump
FR1585785A (fr) * 1968-10-10 1970-01-30
US3667437A (en) * 1970-08-19 1972-06-06 Allis Chalmers Mfg Co Multiple plunger fuel injection pump
GB2042629B (en) * 1979-02-17 1983-01-06 Lucas Industries Ltd Fuel pumping apparatus
EP0027790A1 (fr) * 1979-10-15 1981-04-29 Friedmann & Maier Aktiengesellschaft Pompe d'injection
DE3442953A1 (de) * 1983-12-12 1985-06-20 Robert Bosch Gmbh, 7000 Stuttgart Kraftstoffeinspritzpumpe fuer brennkraftmaschinen
US4576130A (en) * 1984-11-24 1986-03-18 Robert Bosch Gmbh Fuel injection pump for internal combustion engines

Also Published As

Publication number Publication date
DE3630799A1 (de) 1987-09-24
BR8706767A (pt) 1988-02-23
US4842497A (en) 1989-06-27
EP0261154A1 (fr) 1988-03-30
DE3762984D1 (de) 1990-07-05
WO1987005664A1 (fr) 1987-09-24
KR880701327A (ko) 1988-07-26
JPS63502915A (ja) 1988-10-27

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