EP0261154A1 - Pompe a injection de carburant pour moteurs a combustion interne. - Google Patents

Pompe a injection de carburant pour moteurs a combustion interne.

Info

Publication number
EP0261154A1
EP0261154A1 EP87901395A EP87901395A EP0261154A1 EP 0261154 A1 EP0261154 A1 EP 0261154A1 EP 87901395 A EP87901395 A EP 87901395A EP 87901395 A EP87901395 A EP 87901395A EP 0261154 A1 EP0261154 A1 EP 0261154A1
Authority
EP
European Patent Office
Prior art keywords
pump
shaft
fuel injection
shaft part
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.)
Granted
Application number
EP87901395A
Other languages
German (de)
English (en)
Other versions
EP0261154B1 (fr
Inventor
Walter Hafele
Manfred Kramer
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

Links

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.
  • slide-controlled injection pumps is tzqua for the injection.
  • the quality of the combustion in the engine the exact and synchronous control of the spool is important.
  • Higher loads on the torsion shaft such as occur in the event of sudden jerking, 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.
  • There the rotation of the shaft takes place via a controller, the adjustment forces of which are sensitive and dependent on the speed, above all variable frictional forces have a negative effect on the quality of the control.
  • the fuel injection pump according to the invention with the characterizing features of the main 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. Because of this lateral force relief, the bearing between the second shaft part and the pump housing can be formed in a very fine fit, as is customary, for example, between the injection pump piston and the cylinder, so that there is extensive tightness against the outflow of fuel from the injection pump into the regulator.
  • the axial guide of the one shaft part on the coupling side has an end pin running in the shaft axis, which is arranged in a corresponding blind hole on the end side of the other shaft part, wherein this end pin can be slightly spherical.
  • the shaft parts each have an enlarged section on the mutually facing end faces, for example a collar on which driving claws or recesses are provided for the rotational connection.
  • 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 driving 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 sealing rings in a radial manner and in which an oil ring groove with an outwardly leading leakage bore 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 collected and drained through the oil ring groove, so that no diesel fuel from the injection pump gets into the controller, in which it could inadmissibly dilute the lubricating oil there (leakage oil return).
  • the free end of the first shaft part runs in a blind hole of a bearing cover inserted in a hole in the pump housing, the bearing section of the first shaft part also being spherical here.
  • the spherical design in particular enables tension-free turning of the adjusting shaft
  • annular groove is present in the section that dips into the blind bore, into which a locking pin arranged in the bearing cover or housing engages against axial displacement of the first shaft part.
  • FIG. 1 shows a longitudinal section through a fuel injection pump according to the invention according to line I-I in FIG. 2; 2 shows a cross section through this pump according to line II-II 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 III-III 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 is driven by a camshaft 6 with the interposition of a roller tappet 4 with roller 5 against the force of a spring 7 for its axial movement forming the working stroke.
  • Partial suction chambers 8 are formed by recesses 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. In these partial suction chambers 8, a control slide 9 is arranged on the pump piston 3-axially displaceable.
  • 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 passes through at its longitudinal ends End shields 11 is closed.
  • 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 which engage in a groove 13 of the control slide 9, namely as end sections of an eccentric bolt zensl ⁇ gebi 1 det, which can be fixed in position on the twisting shaft 12 by means of a clamping nut 15.
  • a sealing plug 16 of which only two are shown in FIG.
  • These oblique grooves 24 cooperate with radial bores 25 of the spool 9 by being driven through these radial bores 25 after a certain stroke of the pump piston 3. So that the control slide 9 is displaced against twisting during its axial displacement on the pump piston 3 and thus an exact assignment of oblique grooves 24 and radial bores 25 is ensured in FIG.
  • Cylinder liner 2 a guide pin 26 is arranged, which engages in a longitudinal groove 27 of the spool 9.
  • the pump piston 3 has a flattened portion 28 on its lower section, on which a driving member 31 which can be rotated in a known manner by a control rod 29 acts, 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 causes to the radial bores 25.
  • a suction ring 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 spaces 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, the driving pin
  • the two shaft parts 38 and 39 are axially inserted into one another, for which a blind hole 40 is provided in the corresponding end face of the first shaft part 38 and a slightly curved pin 41 is provided which dips 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 flanged, so that two collars 42 are opposite. 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 locating bore receiving this end shield and is held by a screw 47.
  • Two ring seals 48 are present between the housing 1 and this bearing bush 46.
  • 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 fuel ring possibly leaking from the main suction chamber 10 is collected by the oil ring groove 49 and discharged by means of the relief channel 51 in order not to get into the regulator housing filled with lubricating oil (leakage oil return).
  • the other end 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 part 38 has a pin 54 which also is spherical to have only line contact for the 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 a ring 56 of the shaft part 38 and is arranged in the bearing cover 53.
  • a flattening 57 is present on the shaft section between the ring groove 56 and the pin 54, which flatness reaches approximately the depth of the ring groove 56. This makes it possible to slide 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 bracket 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, and then the bearing bush 46 with the second shaft part 39 already installed.

Landscapes

  • 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.
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
DE19863630799 DE3630799A1 (de) 1986-03-22 1986-09-10 Kraftstoffeinspritzpumpe fuer brennkraftmaschinen
DE3630799 1986-09-10

Publications (2)

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

Non-Patent Citations (1)

* Cited by examiner, † Cited by third party
Title
See references of WO8705664A1 *

Also Published As

Publication number Publication date
EP0261154B1 (fr) 1990-05-30
KR880701327A (ko) 1988-07-26
DE3630799A1 (de) 1987-09-24
BR8706767A (pt) 1988-02-23
JPS63502915A (ja) 1988-10-27
WO1987005664A1 (fr) 1987-09-24
US4842497A (en) 1989-06-27
DE3762984D1 (de) 1990-07-05

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