EP0543805A1 - Pompe d'injection de carburant pour moteurs a combustion interne. - Google Patents

Pompe d'injection de carburant pour moteurs a combustion interne.

Info

Publication number
EP0543805A1
EP0543805A1 EP90910587A EP90910587A EP0543805A1 EP 0543805 A1 EP0543805 A1 EP 0543805A1 EP 90910587 A EP90910587 A EP 90910587A EP 90910587 A EP90910587 A EP 90910587A EP 0543805 A1 EP0543805 A1 EP 0543805A1
Authority
EP
European Patent Office
Prior art keywords
slide valve
rotary slide
fuel injection
rotary
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
EP90910587A
Other languages
German (de)
English (en)
Other versions
EP0543805B1 (fr
Inventor
Helmut Rembold
Ernst Linder
Gottlob Haag
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 EP0543805A1 publication Critical patent/EP0543805A1/fr
Application granted granted Critical
Publication of EP0543805B1 publication Critical patent/EP0543805B1/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
    • F02M59/38—Pumps characterised by adaptations to special uses or conditions
    • 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
    • F02M59/36—Varying fuel delivery in quantity or timing by variably-timed valves controlling fuel passages to pumping elements or overflow passages
    • F02M59/366—Valves being actuated electrically
    • 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
    • F02M41/02—Fuel-injection apparatus with two or more injectors fed from a common pressure-source sequentially by means of a distributor the distributor being spaced from pumping elements
    • F02M41/06—Fuel-injection apparatus with two or more injectors fed from a common pressure-source sequentially by means of a distributor the distributor being spaced from pumping elements the distributor rotating
    • 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
    • F02M41/02—Fuel-injection apparatus with two or more injectors fed from a common pressure-source sequentially by means of a distributor the distributor being spaced from pumping elements
    • F02M41/06—Fuel-injection apparatus with two or more injectors fed from a common pressure-source sequentially by means of a distributor the distributor being spaced from pumping elements the distributor rotating
    • F02M41/063—Fuel-injection apparatus with two or more injectors fed from a common pressure-source sequentially by means of a distributor the distributor being spaced from pumping elements the distributor rotating the distributor and rotary valve controlling fuel passages to pumping elements being combined
    • 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
    • F02M63/00—Other fuel-injection apparatus having pertinent characteristics not provided for in groups F02M39/00 - F02M57/00 or F02M67/00; Details, component parts, or accessories of fuel-injection apparatus, not provided for in, or of interest apart from, the apparatus of groups F02M39/00 - F02M61/00 or F02M67/00; Combination of fuel pump with other devices, e.g. lubricating oil pump
    • F02M63/0012—Valves
    • F02M63/0031—Valves characterized by the type of valves, e.g. special valve member details, valve seat details, valve housing details
    • F02M63/0038—Valves characterized by the type of valves, e.g. special valve member details, valve seat details, valve housing details rotary

Definitions

  • the invention is based on a fuel injection pump according to the preamble of the main claim.
  • Such a fuel injection pump can be found, for example, in the older German application P 38 04 025.
  • the distribution of the fuel flow from a plurality of pumps z the injection openings of the injection valves was carried out by a rotary slide valve, which was driven in synchronism with the given gear ratio to the motor shaft for rotating movement.
  • the injection quantity and injection timing were controlled by opening or closing an overflow channel to a relief volume by means of a solenoid valve.
  • the possibility is created of counteracting seizure of the rotary slide valve in its guidance by axially displacing the rotary slide valve. Allows at the same time an axial displacement of the rotary slide valve with a corresponding design of the recesses running in the circumferential direction for the distribution of the fuel flow to individual cylinders and / or a relative rotation of the rotary slide valve to the rotary drive, the possibility of adjusting the injection timing over a larger angular range than is possible due to the geometrical Limits for the configuration of the circumferentially measured length of the distribution grooves of the rotary slide valve would be possible.
  • the design is advantageously made such that the rotary slide valve can be determined in its rotational position or displacement position depending on an operating parameter of the internal combustion engine.
  • the operating parameters of the internal combustion engine are primarily the speed of the internal combustion engine, or a control variable related to the speed of the internal combustion engine, such as the fuel pressure of a fuel pump driven synchronously with the motor shaft, an oil pressure or the like. into consideration.
  • the corresponding control variable can also be derived from a centrifugal governor.
  • the rotary slide valve can preferably be displaceable in the direction of this axis of rotation against a stop which is adjustable as a function of an operating parameter.
  • a stop which is adjustable as a function of an operating parameter.
  • the rotary slide valve itself can also be designed in a simple manner as a piston, the application of pressure to such a rotary slide valve designed as a piston on the piston end face being able to be used directly to displace the rotary slide valve, with advantage the working space of this piston can be pressurized against the force of a spring acting on the rotary slide valve.
  • a pressure suitable for the displacement of the rotary slide valve can be derived directly from the high-pressure side of the pump, wherein if the rotary slide valve designed as a piston is acted upon by such a pump pressure, the design is preferably such that the working area of the Piston-formed rotary slide valve is connected to the return line via a throttle and possibly a pressure relief valve.
  • the pump pressure is reduced via the throttle, a shifting pressure corresponding to an operating parameter of the internal combustion engine being present on the side of the rotary slide valve designed as a piston, taking into account the dynamic flow behavior of the fuel.
  • the axial displacement initially only gives the advantage that seizure of the rotary valve is countered.
  • the design of the circumferential, distribution-serving grooves of the rotary slide valve is changed or a rotation de Rotary slide valve is made relative to its drive, the angular range of a possible influence of the injection process can be adjusted by the solenoid valve.
  • the design can be such that the rotary slide valve is coupled to the rotary drive via oblique teeth or grooves.
  • Such coupling of the rotary slide valve to the rotary drive via oblique teeth or grooves simultaneously leads to a relative rotation of the rotary slide valve relative to the rotary drive due to the oblique teeth or grooves when the rotary slide valve is axially displaced.
  • the design can be made in a particularly simple manner in such a way that the rotary slide valve engages in an oblique groove on the inner circumference of a hollow drive wheel connected to the rotary drive via at least one pin which is oriented essentially radially to the axis of rotation, as a result of which a particularly compact Education is achieved.
  • the synchronous rotary drive of the rotary slide valve can be derived directly from the motor shaft in a simple manner.
  • the pump camshaft can be driven to achieve a uniform pressure level even with a small number of piston pumps with a correspondingly lowest possible but higher speed than the drive shaft of the rotary slide valve, for which purpose the design is preferably such that the hollow drive wheel of the rotary slide valve than with a gearwheel a gear cam meshing gear is formed, and that the gear of the pump camshaft has a smaller diameter than the hollow drive gear of the rotary slide valve.
  • the design is advantageously made such that the circumferential grooves of the rotary slide valve have a width measured in the axial direction, which is at least equal to the maximum axial displacement of the rotary slide valve that occurs when the rotary slide valve is rotated relative to its rotary drive.
  • the supply with fuel under pressure must be ensured in each axial displacement position, for which the design is preferably such that a circumferential groove of the rotary slide valve connected to the pressure-side pump connection has a width in the axial direction corresponding to the maximum axial displacement path of the rotary slide valve Direction.
  • the design can be made in such a simple manner that the injection timing and the injection duration or injection quantity can be determined by a solenoid valve which opens into the return line and which is connected to a pressure-side line the pump (s) is connected, and that the solenoid valve with the interposition of the working space of the rotary slide valve designed as a piston or the working space of an adjusting piston and a throttle is connected to the return line, which at the same time results in particularly compact dimensions.
  • FIG. 1 shows a partial section through a first embodiment of a fuel injection pump according to the invention in the region of the rotary slide valve; 2 shows, in a representation similar to FIG. 1, a modified embodiment of a fuel injection pump according to the invention; and FIG. 3 shows a further modified embodiment in which the axial movement of the rotary slide valve is intended to largely prevent it from seizing.
  • Fig. 1, 1 denotes a pump housing of a distributor fuel injection pump, in which a rotary slide valve 2 acting as a distributor is rotatably arranged in a cylindrical bore 3 and can be displaced in the axial direction.
  • the rotary slide valve 2 is driven by a hollow gear 4 which meshes with a gear 5 of a pump camshaft, not shown.
  • the gear wheel 5 of the pump camshaft has a smaller diameter than the drive wheel 4 of the rotary slide valve 2, the dimensioning of the gear wheels 4 and 5 providing a desired transmission ratio between the number of revolutions of the pump camshaft, which is not shown in more detail, and which has fuel under a large number of pump pistons Pressure to the rotary slide valve via a feed line 6, and the number of revolutions of the rotary slide valve 2 can be adjusted, the rotary slide valve 2 being driven in synchronism with the drive shaft of the internal combustion engine in each case at half the speed of the drive shaft.
  • the fuel passes under pressure into an annular space 7, which extends from a circumferential recess in the axial direction of the rotary slide valve 2 or Groove is formed.
  • a line 9 leading to a solenoid valve 8 also opens in the area of the circumferential groove 7 of the rotary slide valve 2, the solenoid valve 8 controlling both the start of injection and the injection quantity or injection duration.
  • the fuel under pressure which is switched off by the solenoid valve in its open position, passes through a bore 10 into a working space 11, which is limited by the rotary slide valve 2, of the rotary slide valve, which is simultaneously designed as a stop piston, in order to achieve a larger possible injection range by axial displacement and / or relative rotation of the rotary slide valve 2 relative for rotating the same, as will be explained in more detail below.
  • the pressure in the working space 11 is set via a pressure-maintaining valve 12 and the fuel emerging from the working space 11 opens into a return line to the tank, indicated schematically by 13.
  • the fuel passes under pressure from the annular space or the circumferential groove 7 of the rotary slide valve into a bore 15 running obliquely to the axis 14 of the rotary slide valve to a recess or groove 16 arranged on the circumference of the rotary slide valve, which in a corresponding rotational position of the rotary slide valve via a feed line 17 to a schematically indicated injection valve 18 supplies fuel under pressure.
  • a pressure equalization bore 19 opens into the recess 16 in the rotary slide valve at an angle corresponding to the angle of the bore 15.
  • a corresponding number of feed bores are provided for the individual injection valves of the engine cylinders, and there is only a limited range of angles for the separation of the injection processes in the individual cylinders at the synchronous to the motor shaft Rotary movement of the rotary slide valve 2 available.
  • the rotary slide valve 2 is displaced and / or rotated relative to the drive gear 4.
  • two bolts 20 are provided on the rotary slide valve 2 which extend essentially radially on the rotary slide axis 14 and which engage in schematically indicated grooves 21 on the inner circumference of the drive gear 4 which run obliquely to the rotary slide axis 14.
  • the rotary slide valve 2 rotates relative to the drive wheel 4 via the radial bolts 20 engaging in the oblique grooves 21, and the recess 16 therefore arrives at a different point in time, ie in a different angular range of the motor drive drive shaft in a position aligned with a bore 17 to an injection valve, so that the start of injection can be adjusted within wide limits.
  • the rotary slide valve is held in contact with a control piston 22, which is acted upon by a spring 23, via the pressure prevailing in the working space 11.
  • the control piston is acted upon via a schematically indicated feed line 24 as a function of an operating parameter, such as, for example, the engine oil pressure or the gasoline inlet pressure.
  • the resulting axial movement of the control piston and thus of the rotary slide valve is, as mentioned above, rotated relative to the pump drive shaft and thus to the motor drive shaft via the radial bolts running in the oblique groove 21 into a rotary movement of the rotary slide valve 2.
  • both the recess 7, which cooperates with the inlet 6, and the recess 16, which cooperates with an injection valve in each case via the bore 17, have one extending in the direction of the axis of the rotary slide valve Width, which corresponds at least to the maximum axial displacement of the rotary slide valve 2.
  • helical teeth can also be provided on the rotary slide valve 2 and on the inner circumference of the drive wheel 4, in order to axially move the rotary slide valve 2 in a relative rotation to implement the drive wheel 4.
  • a leakage bore is also indicated at 25, which interacts with a circumferential groove 26 on the rotary slide valve 2.
  • FIG. 2 the reference numerals of FIG. 1 have been retained for the same components.
  • an axial movement of the rotary slide valve 2 into a rotary movement thereof relative to the drive wheel 4 is used to adjust the angular range that can be used for an injection.
  • the rotary slide valve is acted upon in the axial direction via a piston 28 loaded by a spring 27, and the axial displacement in the working space 11 of the rotary slide valve 2 designed as a piston is used to adjust the axial position and thus the rotational position relative to the drive wheel .
  • the fuel flow controlled via the solenoid valve 8 passes from the working space 11 via a throttle 29 into the return 13 to the tank.
  • a higher mean pressure level is set in the space 11, through which the rotary slide valve 2 is pushed ver against the spring-loaded piston 28.
  • a pressure relief valve 31 is also switched on, so that after a travel of the adjustment path, ie after the piston 2 comes into contact with the stop 32, the pressure relief valve i opens the return line 13.
  • the tuning of the throttle 2 and the biasing force of the spring 27 takes place in such a way that an axial movement of the rotary slide valve takes place only from a predetermined speed.
  • this circumferential groove is formed obliquely to the axis 14 of the rotary slide valve 2, so that at an axial displacement of the rotary slide valve 2 in different rotational positions, the feed bores 17 are smoothed over, in which case the circumferential recess 16 would naturally have to extend over a larger angular range than the embodiment shown in FIGS.
  • FIG. 3 shows a modified embodiment of the rotary slide valve 2, which in turn is connected to the pump drive shaft or the motor shaft via a drive wheel 4 in a manner not shown in any more detail.
  • fuel passes through recesses 33 provided on the circumference of the rotary slide valve 2 into an axial channel 34 of the rotary slide valve, fuel in pressure in corresponding angular positions passing through recesses 35 arranged in a further plane in feed lines 36 to injection valves
  • a further circumferential groove 37 is connected via the axial channel 34 to a relief bore 38, into which a solenoid valve 39 analogous to the solenoid valve 8 is switched on.
  • the fuel flow controlled by the solenoid valve 39 in turn reaches a working space 41 via a line 40, which is connected to a return 42. Since when turning off in Every time a pressure wave is triggered, the rotary slide valve 2 is thereby acted upon in the axial direction and moved in the axial direction against the force of a spring 43. Since, in contrast to the design according to FIGS. 1 and 2, neither a pressure holding valve nor a throttle and a pressure relief valve are switched on in the return line 42, the pressure drops rapidly again after the pressure wave occurs in the working space 41 and it becomes so Rotary slide valve 2 in turn moved back to its normal position by the force of the spring 43.

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

Une pompe d'injection de carburant, notamment pour l'injection directe de carburant dans des moteurs à combustion interne à allumage piloté, comprend au moins une pompe qui génère un courant de carburant sous pression et un tiroir rotatif (2) qui se déplace synchroniquement à l'arbre moteur du moteur à combustion interne afin de relier le courant de carburant avec au moins un orifice d'injection (18) du moteur à combustion interne et/ou de dévier le courant de carburant soumis à la pression de la pompe vers un conduit de reflux (13). Le déplacement du tiroir rotatif (2) dans le sens de son axe de rotation (14) est limité ou le tiroir rotatif (2) est monté de manière à limiter sa rotation par rapport à son entraînement rotatif. De préférence, la position de rotation ou de déplacement du tiroir rotatif peut être déterminée en fonction d'un paramètre de fonctionnement du moteur à combustion interne. La mobilité axiale du tiroir rotatif (2) l'empêche de se coincer dans son guidage (3) et le réglage en fonction des paramètres de fonctionnement du moteur permet d'ajuster le moment de l'injection sur une plus grande plage angulaire qu'il ne serait possible normalement, étant donné les limitations géométriques de la structure du tiroir rotatif.
EP90910587A 1989-08-23 1990-07-26 Pompe d'injection de carburant pour moteurs a combustion interne Expired - Lifetime EP0543805B1 (fr)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
DE3927742 1989-08-23
DE3927742A DE3927742A1 (de) 1989-08-23 1989-08-23 Kraftstoffeinspritzpumpe fuer brennkraftmaschinen
PCT/DE1990/000573 WO1991002897A1 (fr) 1989-08-23 1990-07-26 Pompe d'injection de carburant pour moteurs a combustion interne

Publications (2)

Publication Number Publication Date
EP0543805A1 true EP0543805A1 (fr) 1993-06-02
EP0543805B1 EP0543805B1 (fr) 1994-10-05

Family

ID=6387640

Family Applications (1)

Application Number Title Priority Date Filing Date
EP90910587A Expired - Lifetime EP0543805B1 (fr) 1989-08-23 1990-07-26 Pompe d'injection de carburant pour moteurs a combustion interne

Country Status (6)

Country Link
US (1) US5245971A (fr)
EP (1) EP0543805B1 (fr)
JP (1) JPH04501451A (fr)
KR (1) KR0167113B1 (fr)
DE (2) DE3927742A1 (fr)
WO (1) WO1991002897A1 (fr)

Families Citing this family (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB2275307B (en) * 1993-02-18 1996-06-05 Bosch Gmbh Robert A fuel-injection system for internal combustion engines
GB9500294D0 (en) * 1995-01-07 1995-03-01 Lucas Ind Plc Fuel pump
US6058910A (en) * 1998-04-15 2000-05-09 Cummins Engine Company, Inc. Rotary distributor for a high pressure fuel system
DE19854509C2 (de) * 1998-11-25 2000-11-23 Siemens Ag Vorrichtung zum Erzeugen eines variablen Volumenstromes bei einer Kraftstoffzuführung
DE19951999B4 (de) * 1999-10-28 2004-11-18 Siemens Ag Einspritzanlage für eine Brennkraftmaschine
DE10216205B4 (de) * 2002-04-12 2007-04-05 Robert Bosch Gmbh Kraftstoffhochdruckpumpe mit Fördermengenregelung
DE102010022134A1 (de) * 2010-05-20 2011-11-24 Gm Global Technology Operations Llc (N.D.Ges.D. Staates Delaware) Ölpumpenmodul mit einem Ölpumpenmodulgehäuse

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US3046894A (en) * 1960-01-27 1962-07-31 Simmonds Aerocessories Inc Metering pump mechanism
FR1387296A (fr) * 1963-12-19 1965-01-29 Sigma Perfectionnements apportés aux pompes d'injection de combustible à distributeur rotatif
FR1527768A (fr) * 1966-11-15 1968-06-07 Bosch Gmbh Robert Perfectionnements apportés aux pompes d'injection à pistons radiaux et à avance à l'injection variable
US3615043A (en) * 1969-03-07 1971-10-26 Ambac Ind Fluid metering and distributing system
US3752138A (en) * 1971-08-09 1973-08-14 Int Harvester Co Engine injection pump operating all cylinders or less
US4200072A (en) * 1977-05-18 1980-04-29 Caterpillar Tractor Co. Fuel injection pump
JPS5522708A (en) * 1978-08-04 1980-02-18 Dainippon Screen Mfg Co Ltd Method and apparatus for recording of color image
DE3124500A1 (de) * 1981-06-23 1983-01-13 Robert Bosch Gmbh, 7000 Stuttgart Kraftstoffeinspritzpumpe
DE3243348A1 (de) * 1982-11-24 1984-05-24 Robert Bosch Gmbh, 7000 Stuttgart Kraftstoffeinspritzpumpe
DE3320835A1 (de) * 1983-06-09 1984-12-13 Dieter 7460 Balingen Fuoß Multipositionsantrieb
SU1621816A3 (ru) * 1987-02-10 1991-01-15 Интератом Гмбх (Фирма) Гидравлическое устройство управлени клапанами двигател внутреннего сгорани
DE3719807A1 (de) * 1987-06-13 1988-12-22 Bosch Gmbh Robert Verteilerkraftstoffeinspritzpumpe der radialkolbenbauart
DE3719831A1 (de) * 1987-06-13 1988-12-22 Bosch Gmbh Robert Kraftstoffeinspritzpumpe
DE3804025A1 (de) * 1988-02-10 1989-08-24 Bosch Gmbh Robert Kraftstoffeinspritzpumpe fuer brennkraftmaschinen
DE3819996A1 (de) * 1988-06-11 1989-12-14 Bosch Gmbh Robert Hydraulische steuereinrichtung insbesondere fuer kraftstoffeinspritzanlagen von brennkraftmaschinen
JP2525777Y2 (ja) * 1988-09-26 1997-02-12 株式会社ユニシアジェックス バルブタイミング制御装置の組立構造

Non-Patent Citations (1)

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Title
See references of WO9102897A1 *

Also Published As

Publication number Publication date
US5245971A (en) 1993-09-21
DE59007406D1 (de) 1994-11-10
JPH04501451A (ja) 1992-03-12
EP0543805B1 (fr) 1994-10-05
KR920701662A (ko) 1992-08-12
WO1991002897A1 (fr) 1991-03-07
KR0167113B1 (ko) 1998-12-15
DE3927742A1 (de) 1991-02-28

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