EP0615063A1 - Pompe à injection de combustible - Google Patents

Pompe à injection de combustible Download PDF

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Publication number
EP0615063A1
EP0615063A1 EP94101869A EP94101869A EP0615063A1 EP 0615063 A1 EP0615063 A1 EP 0615063A1 EP 94101869 A EP94101869 A EP 94101869A EP 94101869 A EP94101869 A EP 94101869A EP 0615063 A1 EP0615063 A1 EP 0615063A1
Authority
EP
European Patent Office
Prior art keywords
pump
rollers
pump piston
lifting
fuel injection
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
EP94101869A
Other languages
German (de)
English (en)
Other versions
EP0615063B1 (fr
Inventor
Kurt Oberklammer
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 EP0615063A1 publication Critical patent/EP0615063A1/fr
Application granted granted Critical
Publication of EP0615063B1 publication Critical patent/EP0615063B1/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
    • 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
    • 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
    • F02M41/123—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 characterised by means for varying fuel delivery or injection timing
    • F02M41/125—Variably-timed valves controlling fuel passages

Definitions

  • the invention relates to a fuel injection pump of the distributor type for a multi-cylinder internal combustion engine of the type defined in the preamble of claim 1.
  • the number of injection lines is limited to a maximum of four, since with an angle of rotation of the lifting disk still available for a front cam of the lifting disk, sufficient injection adjustment by the solenoid valve is possible.
  • the spray adjustment is brought about by the fact that by closing and opening the solenoid valve during the piston stroke, the start of delivery and the end of delivery of the pump piston are shifted towards different cam angles in accordance with the respective load case, i.e. sooner or later, based on the angle of rotation of the lifting disk.
  • the fuel injection pump according to the invention with the characterizing features of claim 1 has the advantage that its use with a sufficiently sensitive spray adjustment by the solenoid valve is also possible in internal combustion engines with more than four cylinders.
  • a larger cow of the pump piston than in the known fuel injection pump can be achieved with smaller cam elevations, since the cam heights of the two lifting disks add up for the pump piston stroke. Due to the higher stroke, a larger displacement angle of the start of delivery can be achieved.
  • the cam gear consisting of a roller holder with double-layer rollers and two lifting discs, can be easily lubricated by connecting it to the oil lubrication of the engine circuit. Lubrication with fuel is also possible, for which purpose the pump interior receiving the cam gear is filled with fuel in a known manner and coupled to the drive shaft of a fuel delivery pump rotating in the pump interior.
  • the two lifting disks are of the same diameter and the axes of the first and second rollers are offset from one another in the axial direction of the roller holder.
  • the cam formation of the two lifting disks are the same, so that each lifting disk contributes 50% of the piston stroke.
  • the axial displacement of the rollers and the associated increased length of the fuel injection pump can be kept small in that the axial distance between the roller axes is chosen smaller than the roller diameter and the axes of the first and second rollers are rotated radially against each other so that the latter do not touch each other .
  • the diameter of the first lifting disk, which is non-rotatable with the pump piston is selected to be smaller than that of the second lifting disk, which is non-rotatable with the drive shaft.
  • the first and second rollers are arranged one behind the other with radially aligned axes.
  • the total pump length of the fuel injection pump is not increased. Due to the larger cam track radius, the larger-diameter lifting disc now takes over more than 50% of the total stroke. The difference in the piston stroke is realized via the first lifting disc, which is non-rotatable with the puncture piston.
  • This cam has a smaller mass due to its smaller cam track radius is advantageous because this cam disc takes the full stroke of the pump piston.
  • a bushing 12 is arranged in a front cover 10 that closes off a pump housing 11, in which a pump piston 13, which also serves as a distributor, executes a reciprocating and simultaneously rotating movement.
  • a drive shaft 15 is rotatably mounted in the pump housing 11 and is connected in a rotationally fixed manner to the pump piston 13 via a dog clutch 16, which permits an axial relative movement between the pump piston 13 and the drive shaft 15.
  • the stroke movement of the pump piston 13 is even closer to Descriptive cam gear 14 is generated, which is arranged in the interior of the pump housing 11.
  • the drive shaft 15 rotates in synchronism with the speed of the internal combustion engine supplied with fuel by the fuel injection pump, e.g. is designed six-cylinder.
  • a pump working space 17 is delimited by the end face of the pump piston 13 and the bushing 12, the end face of which is sealed pressure-tight by the valve housing of a solenoid valve 18.
  • the solenoid valve 18 controls a relief channel 19, which opens on the one hand in the pump work chamber 17 and on the other hand via a bore 20 in a fuel delivery chamber 21, which is filled with fuel and is kept at delivery pressure by a fuel delivery pump.
  • an inlet bore 22 running in the end cover 10 is connected to the bore 20, via which the pump working chamber 17 is filled with fuel from the fuel delivery chamber 21.
  • the fuel is distributed via a distributor groove 23 in the pump piston 13, with the pump piston 13 in a corresponding rotational position, to pressure lines 24, which are designed as bores in the bushing 12 and in the end cover 10 and in a number corresponding to the number of cylinders of the internal combustion engine, here e.g. six, are evenly distributed over the circumference of the socket 12.
  • Each pressure line 24 leads to an injection valve via a constant pressure valve 25.
  • the pump working chamber 17 is filled with fuel from the fuel delivery chamber via the inlet bore 22.
  • the fuel in the pump work chamber 17 is brought to injection pressure and conveyed via the distributor groove 23 to one of the pressure lines 24 and via the Injection nozzles injected into the respective cylinder of the internal combustion engine.
  • the start and end of the injection of the fuel injection pump are controlled by the solenoid valve 18 as a function of various operating parameters of the internal combustion engine, such as load, speed, temperature and others. When the solenoid valve 18 is not excited, it is open and releases the relief channel 19. No sufficient injection pressure can be built up in the pump work space 17 to open the spray nozzles 25.
  • the relief channel 19 is shut off.
  • the start of delivery FB of the pump piston 13 is identified, and a pressure build-up takes place in the pump work chamber 17.
  • Fuel is conveyed via the distributor groove 23 to the injection nozzles 25 and injected into the cylinders of the internal combustion engine.
  • the de-excitation of the solenoid valve 18 is synonymous with the delivery end FE of the pump piston 13, since this opens the relief channel 19 and there is a pressure drop in the pump work space 17.
  • a metered amount of fuel is injected into a cylinder of the internal combustion engine via one of the injection nozzles 25. This injected fuel quantity represents a partial quantity of the maximum possible fuel quantity conveyed during a delivery stroke of the pump piston 13.
  • the cam gear 14 which generates the stroke of the pump piston 13 consists of a first lifting disk 26 which is connected to the pump piston 13 in a rotationally fixed manner and a second lifting disk 27 which is connected to the drive shaft 15 in a rotationally fixed manner, as well as first rollers 28 rolling on the first lifting disk 26 and on the second lifting disk 27 rolling second rollers 29.
  • the first and second rollers 28, 29, four of which are present and arranged offset by 90 ° to each other are arranged in a roll holder 30 in two axially offset planes.
  • the roller holder 30 is rotatably but axially displaceable in the pump housing 11 coaxially to the axis of the pump piston 13 and the drive shaft 15.
  • Each lifting disk 26, 27 carries a number of end cams 31 and 32 corresponding to the number of cylinders of the internal combustion engine, which generate the stroke of the pump piston 13 when the lifting disks 26, 27 rotate, the pump piston stroke being determined by the sum of the front cam heights on both lifting disks 26, 27
  • a pressure spring which is realized here by two coaxial compression springs 33, 34, is supported on the one hand on the end cover 10 and on the other hand on a spring plate 40, which in turn is supported on the first lifting disk 26 via an axial bearing 41.
  • These helical compression springs 33, 34 press the rollers 28, 29 and the end cams 31, 32 against one another so that they remain in engagement with one another during the lifting movement of the pump piston 13.
  • the second lifting disk 27, which is rotationally fixed with the drive shaft 15, is in turn supported by an axial bearing 35 on a shoulder of the pump housing 11.
  • the rotationally fixed and axially displaceable mounting of the roller holder 30 is brought about by a guide ring 36 which is clamped in the pump housing 11.
  • the roller holder 30 rotatably receives the rollers 28 and 29 with a radially aligned roller axis.
  • the first rollers 28 and the second rollers 29 with roller axes aligned parallel to one another could be arranged in two axially offset planes.
  • this axial distance is directly involved in the overall length of the fuel injection pump.
  • the axial center distances between the rollers 28 and the rollers 29 are made smaller than the diameter of the rollers 28, 29 and the axes of the first Rollers 28 are rotated by a circumferential angle with respect to the axes of the second rollers 29 so that the running surfaces of the rollers 28, 29 do not touch (FIG. 2).
  • the two lifting disks 26, 27 have the same diameter.
  • the number of four first rollers 28 and four second rollers 29 is not mandatory, but with a plurality of rollers the axial forces generated during operation can be better transmitted. For reasons of space, more than four rollers 28 and 29 distributed over the circumference 28 and 29, respectively, are difficult.
  • each lifting disk 26, 27 effects 50% of the piston stroke of the pump piston 13.
  • the division of the cam height necessary for the pump piston stroke into two lifting disks 26, 27 enables smaller end cams 31, 32 per lifting disk 26, 27, whereby a larger number of end cams 31, 32 than four can be arranged over a 360 ° circumferential angle of the lifting disk 26, 27.
  • the nevertheless large stroke of the pump piston 13 permits a sufficient spray adjustment by moving the delivery area on the respective end cam 31, 32 by means of the solenoid valve 18.
  • the fuel injection pump described can thus be used in internal combustion engines with a higher number of cylinders than four without any problems.
  • the fuel injection pump shown in FIGS. 3 and 4 is modified compared to the fuel injection pump just described only with regard to the cam gear 14 '.
  • the diameter of the first lifting disk 26, which is fixed with the pump piston 13 is smaller than the diameter of the one with the Drive shaft 15 non-rotatable second lifting disk 27.
  • the first rollers 28 and second rollers 29 are arranged one behind the other in the radial direction with aligned roller axes in the same plane (FIG. 4).
  • This constructive design of the cam gear 14 ' has the advantage that the total length of the fuel injection pump is not greater than that of conventional fuel injection pumps of the distributor type due to the rollers 28, 29 arranged in the same plane.
  • the piston-side lifting disk 26 has a lower mass.
  • a smaller mass takes part in the stroke movement of the pump piston 13, which has an extremely favorable effect on the control of the axial forces.
  • the stroke of the pump piston 13 is not divided 1: 1 between the two lifting disks 26 and 27, rather the second lifting disk 27, which is non-rotatable with the drive shaft 15, takes on more than 50% of the total stroke due to its larger diameter and the associated larger cam track radius .
  • the difference in the stroke of the pump piston 13 is realized via the first lifting disk 26, which is fixed with the pump piston 13 and is again rotatably coupled to the drive shaft 15 via the dog clutch 16.
  • the torque transmission of the claw clutch takes place through a cross disk 37, which is seated on claws 38 of the drive shaft 15 and in turn engages with claws 39 in the first lifting disk 26, which is rotatable with the pump piston 13.

Landscapes

  • Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Fuel-Injection Apparatus (AREA)
EP94101869A 1993-03-06 1994-02-08 Pompe à injection de combustible Expired - Lifetime EP0615063B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE4307111 1993-03-06
DE4307111A DE4307111A1 (de) 1993-03-06 1993-03-06 Kraftstoffeinspritzpumpe

Publications (2)

Publication Number Publication Date
EP0615063A1 true EP0615063A1 (fr) 1994-09-14
EP0615063B1 EP0615063B1 (fr) 1996-12-27

Family

ID=6482140

Family Applications (1)

Application Number Title Priority Date Filing Date
EP94101869A Expired - Lifetime EP0615063B1 (fr) 1993-03-06 1994-02-08 Pompe à injection de combustible

Country Status (4)

Country Link
US (1) US5474430A (fr)
EP (1) EP0615063B1 (fr)
JP (1) JPH06299925A (fr)
DE (2) DE4307111A1 (fr)

Citations (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS60147544A (ja) * 1984-01-10 1985-08-03 Diesel Kiki Co Ltd 分配型燃料噴射ポンプ
EP0192978A1 (fr) * 1985-02-28 1986-09-03 Robert Bosch Gmbh Pompe d'injection de combustible pour moteurs à combustion interne

Family Cites Families (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2699766A (en) * 1946-11-21 1955-01-18 Micro Prec Inc Fuel injection pump
US2759422A (en) * 1951-12-13 1956-08-21 Bosch Arma Corp Fuel injection apparatus
CH341027A (de) * 1955-05-04 1959-09-15 Bosch Gmbh Robert Kraftstoffeinspritzpumpe mit Verteiler
GB814589A (en) * 1956-12-19 1959-06-10 Bosch Gmbh Robert Improvements in or relating to fuel injection pumps
GB2069596B (en) * 1980-01-17 1984-01-11 Nissan Motor Fuel injection pump electrical fuel delivery control system
DE3633107A1 (de) * 1986-04-10 1987-10-15 Bosch Gmbh Robert Kraftstoffeinspritzvorrichtung fuer brennkraftmaschinen

Patent Citations (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS60147544A (ja) * 1984-01-10 1985-08-03 Diesel Kiki Co Ltd 分配型燃料噴射ポンプ
EP0192978A1 (fr) * 1985-02-28 1986-09-03 Robert Bosch Gmbh Pompe d'injection de combustible pour moteurs à combustion interne

Non-Patent Citations (1)

* Cited by examiner, † Cited by third party
Title
PATENT ABSTRACTS OF JAPAN vol. 9, no. 313 (M - 437)<2036> 10 December 1985 (1985-12-10) *

Also Published As

Publication number Publication date
DE59401363D1 (de) 1997-02-06
JPH06299925A (ja) 1994-10-25
DE4307111A1 (de) 1994-09-08
EP0615063B1 (fr) 1996-12-27
US5474430A (en) 1995-12-12

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