EP0534993A1 - 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
EP0534993A1
EP0534993A1 EP91909403A EP91909403A EP0534993A1 EP 0534993 A1 EP0534993 A1 EP 0534993A1 EP 91909403 A EP91909403 A EP 91909403A EP 91909403 A EP91909403 A EP 91909403A EP 0534993 A1 EP0534993 A1 EP 0534993A1
Authority
EP
European Patent Office
Prior art keywords
fuel injection
injection pump
ring
drive shaft
roller ring
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
EP91909403A
Other languages
German (de)
English (en)
Other versions
EP0534993B1 (fr
Inventor
Wolfgang Fehlmann
Wolfgang Braun
Dieter Junger
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 EP0534993A1 publication Critical patent/EP0534993A1/fr
Application granted granted Critical
Publication of EP0534993B1 publication Critical patent/EP0534993B1/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
    • F02M41/00—Fuel-injection apparatus with two or more injectors fed from a common pressure-source sequentially by means of a distributor
    • F02M41/08—Fuel-injection apparatus with two or more injectors fed from a common pressure-source sequentially by means of a distributor the distributor and pumping elements being combined
    • F02M41/10—Fuel-injection apparatus with two or more injectors fed from a common pressure-source sequentially by means of a distributor the distributor and pumping elements being combined pump pistons acting as the distributor
    • F02M41/12—Fuel-injection apparatus with two or more injectors fed from a common pressure-source sequentially by means of a distributor the distributor and pumping elements being combined pump pistons acting as the distributor the pistons rotating to act as the distributor
    • 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
    • F02M41/00—Fuel-injection apparatus with two or more injectors fed from a common pressure-source sequentially by means of a distributor
    • F02M41/08—Fuel-injection apparatus with two or more injectors fed from a common pressure-source sequentially by means of a distributor the distributor and pumping elements being combined
    • F02M41/10—Fuel-injection apparatus with two or more injectors fed from a common pressure-source sequentially by means of a distributor the distributor and pumping elements being combined pump pistons acting as the distributor
    • F02M41/12—Fuel-injection apparatus with two or more injectors fed from a common pressure-source sequentially by means of a distributor the distributor and pumping elements being combined pump pistons acting as the distributor the pistons rotating to act as the distributor
    • F02M41/121—Fuel-injection apparatus with two or more injectors fed from a common pressure-source sequentially by means of a distributor the distributor and pumping elements being combined pump pistons acting as the distributor the pistons rotating to act as the distributor with piston arranged axially to driving shaft
    • 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
    • F02M59/48—Assembling; Disassembling; Replacing
    • 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
    • F02M65/00—Testing fuel-injection apparatus, e.g. testing injection timing ; Cleaning of fuel-injection apparatus
    • 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
    • F02M2200/00—Details of fuel-injection apparatus, not otherwise provided for
    • F02M2200/24—Fuel-injection apparatus with sensors

Definitions

  • the invention is based on a fuel injection pump for internal combustion engines according to the preamble of claim 1.
  • a fuel injection pump is already known from DE-OS 33 36 871.
  • the encoder part which is fixed in itself, is directly firmly attached to the roller ring and is located radially opposite the encoder wheel on the drive shaft.
  • the stationary encoder part can be displaced in the circumferential direction on the roller ring and can be fixed there again.
  • This solution has the disadvantage that the bearing of the roller ring in the housing of the fuel injection pump is free of play, so that the roller ring can carry out movements in its radial plane if forces act on it when the cam of the cam disc hits the rollers Act.
  • the bolt represents a one-sided bearing point of the roller ring, so that when the roller ring is acted upon by forces in its circumferential direction it executes these tilting movements around the bolt articulation as a pivotal point.
  • the pin linkage itself is also subject to play, as is the pin itself to a certain extent when force is applied transversely to the longitudinal extent of the pin the sprayer can give way. When force is applied to the roller ring, its articulation point also executes a movement in the circumferential direction. If the stationary transmitter part is now fastened on the roller ring, then this moves along with it.
  • the stationary transmitter is generally arranged diametrically opposite the point of articulation of the bolt.
  • the movement components of the roller ring are greatest when it moves around the pin.
  • this error is added or subtracted, so that the measurement result and the resultant injection start setting have an uncontrolled proportion of errors. If the speed detection required for the quantity calculation lies in the relevant area, this angular error has the effect of a speed error, as a result of which the quantity calculation is also incorrect.
  • the fuel injection pump according to the invention with the characterizing features of patent claim 1 has the advantage over the fact that with the aid of the carrier ring, the movement of the roller ring is switched off by measurement technology or at least essentially rendered ineffective due to the retroactive forces of the cam drive.
  • the configuration according to claim 2 provides an advantageous arrangement of the coupling part for coupling the carrier ring to the roller ring.
  • the roller ring intrinsic movements can be practically completely switched as a result of the retroactive forces from the cam drive in relation to the measuring position of the fixed encoder part.
  • the teaching of claim 4 provides an effective arrangement of the coupling part that is easy to find and to manufacture.
  • the configuration according to claims 6 to 8 provides advantageous storage options for the carrier ring and its fixing in relation to the relative movement of the stationary transmitter part to the encoder wheel. This results in a particularly advantageous solution with the embodiment according to claim 7.
  • FIG. 1 shows a partial section along the axis of the drive shaft of a distributor fuel injection pump with the parts arranged according to the invention
  • FIG. 2 shows a partial section corresponding to the section according to FIG. 1 in a first modified embodiment as a second exemplary embodiment
  • FIG. 3 shows a section according to the section according to FIG. 1 a second modified form as a third embodiment
  • Figure 4 is a partial section according to the section of Figure 1 with a fourth embodiment of the invention.
  • FIG. 1 shows a partial section through a distributor fuel injection pump along the axis of its drive shaft 2, which is mounted with slide bearings 3 in the wall of the housing 4 of the distributor injection pump.
  • the housing includes a pump interior 5 inside, which is filled with fuel under pressure. The filling of the interior is achieved with the aid of a feed pump 6, which is driven by the drive shaft via a feather key 7 and is located in the interior of the pump housing.
  • a feed pump 6 which is driven by the drive shaft via a feather key 7 and is located in the interior of the pump housing.
  • At the end of the drive shaft there is a pair of claws 9 on the end face, which rotates a front cam disk 11 via a driving piece 10 and corresponding claws, not shown.
  • a pump piston 12 is coupled to the end cam disk via a pin 14, which is held on the end face by a spring 15 on the end cam disk 11.
  • the cams 16 of the end cam disc run over rollers 17 which are mounted in a radial orientation in a roller ring 18. With its circular outer contour, this is rotatably mounted in a corresponding circular cylindrical recess 19 of the pump housing, wherein it is supported axially via a skirt 20 and its end face on a disk 21 covering the feed pump 6.
  • the central opening 22 of the roller ring serves for the passage of the claws 9 of the drive shaft or the coupling between the drive shaft and the pump piston with the driving piece and claws of the cam disk 11.
  • the roller ring together with the disk 21 closes a zy ⁇ Lindrischen space 23 into which the drive shaft 2 protrudes.
  • This closing collar is larger in diameter than the supporting collar and bears against the end face 27 of the roller ring 18 delimiting the space 23.
  • a transmitter wheel 30 is now shrunk on the support collar adjacent to the collar 26 and is provided, for example, with teeth 31 on its end circumference.
  • a carrier ring 33 is rotatable and arranged axially secured between the intermediate disk 28 and the sensor wheel, adjacent to the transmitter wheel towards the intermediate disk 28.
  • the carrier ring has an axially encompassing the encoder wheel 30 ring wall 34, on which a fixed part 36 of an angle encoder is arranged, the interacts with its active side with the toothing 31 of the transmitter wheel 30 and adjoins it in a radially aligned manner.
  • the stationary transmitter part is connected to an electronic control device (not shown here) via this cable connection 39.
  • the carrier ring also has a radially projecting pin 41, which projects into a groove 42 in the apron 20 of the roller ring with the least possible play and thus serves to couple the carrier ring to the roller ring.
  • this pin is arranged at an angular distance of 90 ° from the stationary transmitter part 26 and is only shown folded into the plane of the drawing in FIG. 1 for illustrative reasons.
  • roller ring can be rotated in a known manner by an injection adjuster piston 43.
  • the roller ring is coupled to the injection adjuster piston 43 via a bolt 45 which extends radially to the drive shaft.
  • the bolt is usually fixed in the roller ring and connected to the injection adjuster piston 43 by means of a pivotable connection via a sliding block 46.
  • the drive shaft 2 When the fuel injection pump is in operation, the drive shaft 2 is set in rotating motion. At the same time, the feed pump 6 is also started and the pump interior 5 is supplied with fuel under pressure which is dependent on the speed. This fuel also acts on the injection adjuster piston 43 against a return spring (not shown here) and adjusts this piston more with increasing speed. The resulting rotation of the roller ring causes the cam disc to be set in its conveying stroke movement at an ever earlier point in time when it runs onto the rollers 17. In a known manner, the pump piston 12 guides several per revolution of the drive shaft in this distributor injection pump Delivery strokes from the number of fuel injectors to be supplied per revolution.
  • the cam disk 11 has a plurality of cams which also act simultaneously with the rollers 17 distributed around the circumference of the roller ring.
  • the cam disk When the cam disk is lifted against the force of the spring 15 and the pressure prevailing in front of the pump piston 12 in the pump work space, forces are exerted on the rollers and the roller ring, which are also effective in the circumferential direction according to the cam profile.
  • this causes a turning back moment on the injection adjuster piston, and on the other hand it also causes the roller ring to move within its guide play in the cylindrical recess.
  • the roller ring held on the bolt 45 the play in the radial plane of the roller ring can cause the roller ring to tilt around the bolt as a fulcrum. This tilting movement is also superimposed on the playful connection between pin 45 and roller ring or adjusting piston.
  • the roller ring carries out transverse movements in its radial plane within the scope of the specified play.
  • the instantaneous speed required for the quantity calculation is to be determined, which, if it coincides with the "tipping" in time, can cause a quantity error.
  • the movable part of the angle encoder, the encoder wheel 30, communicates the stationary encoder part 36 via the toothing 31 with the rotation of the drive shaft and the angular distance, which a reference mark, the angular position of which is defined in relation to the base cam, is required to overlap with the stationary one Encoder part to come. If the stationary encoder part moves back and forth together with the roller ring as described above, no exact results are obtained. For this reason, the stationary transmitter part 36 is arranged on the carrier ring 33 and this is mounted on the drive shaft and coupled to the roller ring in the manner described.
  • the position of the coupling pin 41 at a 90 ° distance from the clamping point on the bolt 45, which lies diametrically opposite the stationary transmitter part 36, causes the adjusting component in the circumferential direction on the carrier ring to become negligibly small when the roller ring is tilted within the radial plane.
  • Both the deflection of the roller ring in the area of the pin 45 and its tilting movement about the pin 45 or injection adjuster piston 43 are taken into account.
  • the coupling pin should be arranged and aligned in such a way that it should be arranged and aligned in the direction of the vertical of the bolt 45 on the roller ring axis.
  • the groove must also be designed or arranged accordingly.
  • the pin 141 which corresponds to the pin 41 in FIG. 1, is provided with a spherical head 48 which projects into the groove 42 of the roller ring 18 with play.
  • This has the advantage that the play between pin 41 and roller ring 18 can be kept even smaller, since alignment error compensation is possible with the help of head 48, particularly when the roller ring 18 is tilted.
  • the carrier ring is fitted between the collar 26 and the encoder wheel 30 with the least possible play and free mobility in the circumferential direction.
  • the arrangement of the carrier ring 33, 233, 333 on the drive shaft 2 has the advantage that the wear on the slide bearings 3 caused by the operation of the pump and the resulting drive shaft tilting do not change the distance between the encoder wheel 30 and the encoder part 36, as a result of which the signal strength remains the same over the service life.
  • the simultaneous axial assignment allows the width of the encoder wheel 30 to be reduced to a minimum (manufacturing advantages) without the toothing, as a result of drive shaft axial play, coming from the overlap to the active encoder part, which likewise results in a deterioration in the signal strength would have.

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

Il est décrit une pompe à injection de carburant pour moteurs à combustion interne, comportant un détecteur de position angulaire comprenant une partie fixe (36) et une partie mobile se présentant sous la forme d'une roue de détection (30). Pour obtenir une mesure aussi exacte que possible du début de l'injection jusqu'à l'instant correspondant au début effectif de la course du piston de la pompe, ainsi que du nombre de tours lors du refoulement, la partie fixe est disposée sur une bague-support (33) qui est accouplée à la bague de roulement (18) par l'intermédiaire d'une goupille (41). La goupille se trouve à un angle d'environ 90° par rapport à l'axe (45) entraînant la bague de roulement. Ainsi, les résultats des mesures obtenus avec le détecteur de position angulaire ne sont que très faiblement altérés par les mouvements propres de la bague de roulement dus aux forces de réaction exercées pendant la course du piston.
EP91909403A 1990-06-20 1991-05-25 Pompe a injection de carburant pour moteurs a combustion interne Expired - Lifetime EP0534993B1 (fr)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
DE4019642A DE4019642A1 (de) 1990-06-20 1990-06-20 Kraftstoffeinspritzpumpe fuer brennkraftmaschinen
DE4019642 1990-06-20
PCT/DE1991/000439 WO1991019899A1 (fr) 1990-06-20 1991-05-25 Pompe a injection de carburant pour moteurs a combustion interne

Publications (2)

Publication Number Publication Date
EP0534993A1 true EP0534993A1 (fr) 1993-04-07
EP0534993B1 EP0534993B1 (fr) 1994-08-17

Family

ID=6408725

Family Applications (1)

Application Number Title Priority Date Filing Date
EP91909403A Expired - Lifetime EP0534993B1 (fr) 1990-06-20 1991-05-25 Pompe a injection de carburant pour moteurs a combustion interne

Country Status (7)

Country Link
US (1) US5357930A (fr)
EP (1) EP0534993B1 (fr)
JP (1) JP3166857B2 (fr)
KR (1) KR0185734B1 (fr)
DE (2) DE4019642A1 (fr)
ES (1) ES2057896T3 (fr)
WO (1) WO1991019899A1 (fr)

Families Citing this family (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE4344865A1 (de) * 1993-12-29 1995-07-06 Bosch Gmbh Robert Kraftstoffeinspritzpumpe
GB9404253D0 (en) * 1994-03-05 1994-04-20 Lucas Ind Plc Fuel injection pumping apparatus
GB9511996D0 (en) * 1995-06-13 1995-08-09 Lucas Ind Plc Fuel system
US6076968A (en) * 1996-11-26 2000-06-20 The Coca-Cola Company Easy open flexible pouch
DE10124265B4 (de) * 2001-05-18 2015-10-29 Gustav Klauke Gmbh Pumpe

Family Cites Families (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS555423A (en) * 1978-06-24 1980-01-16 Diesel Kiki Co Ltd Distribution-type electronic-control fuel injection system
JPS59221432A (ja) * 1983-05-31 1984-12-13 Toyota Motor Corp 分配型燃料噴射ポンプ
DE3336871A1 (de) * 1983-10-11 1985-04-25 Robert Bosch Gmbh, 7000 Stuttgart Kraftstoffeinspritzpumpe fuer mehrzylindrige brennkraftmaschinen
JPS60116853A (ja) * 1983-11-26 1985-06-24 Diesel Kiki Co Ltd 分配型燃料噴射ポンプ
JPS60162267U (ja) * 1984-04-05 1985-10-28 株式会社ボッシュオートモーティブ　システム 分配型燃料噴射ポンプ
JPS62240465A (ja) * 1986-04-10 1987-10-21 Diesel Kiki Co Ltd 燃料噴射ポンプ
DE3704578A1 (de) * 1987-02-13 1988-08-25 Bosch Gmbh Robert Kraftstoffeinspritzpumpe fuer brennkraftmaschinen
US5000668A (en) * 1988-04-27 1991-03-19 Diesel Kiki Co., Ltd. Distribution-type fuel injection pump
GB9026013D0 (en) * 1990-11-29 1991-01-16 Lucas Ind Plc Fuel pumping apparatus

Non-Patent Citations (1)

* Cited by examiner, † Cited by third party
Title
See references of WO9119899A1 *

Also Published As

Publication number Publication date
EP0534993B1 (fr) 1994-08-17
WO1991019899A1 (fr) 1991-12-26
DE59102577D1 (de) 1994-09-22
KR930700767A (ko) 1993-03-16
US5357930A (en) 1994-10-25
KR0185734B1 (ko) 1999-03-20
DE4019642A1 (de) 1992-01-02
JPH05507776A (ja) 1993-11-04
ES2057896T3 (es) 1994-10-16
JP3166857B2 (ja) 2001-05-14

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