EP0489740A1 - Kraftstoffverteilereinspritzpumpe für brennkraftmaschinen. - Google Patents
Kraftstoffverteilereinspritzpumpe für brennkraftmaschinen.Info
- Publication number
- EP0489740A1 EP0489740A1 EP90910549A EP90910549A EP0489740A1 EP 0489740 A1 EP0489740 A1 EP 0489740A1 EP 90910549 A EP90910549 A EP 90910549A EP 90910549 A EP90910549 A EP 90910549A EP 0489740 A1 EP0489740 A1 EP 0489740A1
- Authority
- EP
- European Patent Office
- Prior art keywords
- pump
- fuel
- piston
- pump piston
- pressure
- 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
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
- F02M41/123—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
-
- 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
- F02M55/00—Fuel-injection apparatus characterised by their fuel conduits or their venting means; Arrangements of conduits between fuel tank and pump F02M37/00
- F02M55/04—Means for damping vibrations or pressure fluctuations in injection pump inlets or outlets
-
- 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
-
- 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
- F02M63/0001—Fuel-injection apparatus with specially arranged lubricating system, e.g. by fuel oil
Definitions
- the invention relates to a fuel distributor injection pump for internal combustion engines of the type defined in the preamble of claim 1.
- the solenoid valve In a known fuel injection pump of this type of distributor (DE 36 05 452 AI), the solenoid valve is designed so that it closes when an excitation current is applied and opens when it is omitted. During the suction stroke of the pump piston, the solenoid valve remains de-energized, so that fuel can be drawn into the pump working space from the fuel inlet by the pump piston. As soon as the solenoid valve is energized, it closes and the suction process is finished. Then the compression or pressure stroke of the pump piston begins, whereby the fuel present in the pump work space is pressurized.
- the fuel under pressure passes through the axial bore and the distributor bore in one of the distributor channels in the pump cylinder, from where the fuel is fed into the connected injection valve for injection into one of the cylinders of the internal combustion engine.
- the fuel injection is ended as soon as the excitation of the solenoid valve is switched off.
- the solenoid valve opens and any fuel that may still be in the pump workspace is pushed out into the fuel supply via the solenoid valve.
- the process of opening and closing the solenoid valve thus controls the amount of fuel injection to be injected.
- the dimensioning of the flow cross section for the fuel in the solenoid valve is problematic. In order to fill the pump workspace well, it should be as large as possible. A large flow cross section, however, requires longer ones
- the fuel injector fuel pump according to the invention with the characterizing features of claim 1 has the advantage that the flow cross section of the solenoid valve can be kept small with good filling of the pump work space and accordingly the solenoid valve is characterized by short switching times and low power consumption. This is achieved according to the invention in that during the suction stroke of the pump piston an additional filling of the pump work space takes place via the filling and relief bore, bypassing the solenoid valve. The relief hole is thus used twice. On the one hand - as already described in DE 24 49 332 C2 - to compensate for the lateral forces during the pressure stroke of the pump piston, which act on the pump piston via the distributor bore, and - on the other hand, as an additional filling aid during the suction stroke of the pump piston.
- the use of the relief bore for filling the pump work s has the advantage that no additional dead volume is created in the filling area, which is particularly important when using the fuel type gasoline because of its low compression module.
- the diaphragm accumulator prevents brief pressure drops during the suction stroke of the pump piston, so that an exactly reproducible filling of the pump work space is ensured with each suction stroke.
- the filling bores in the pump cylinder are inclined, i.e. arranged at an acute angle of inclination to the cylinder axis. This results in an elliptical opening area of the filling bores at the transition from the pump cylinder to the pump piston, which is advantageous for cross-sectional reasons, since the pump piston also executes an axial movement during the rotation.
- the diaphragm accumulator is connected to an unpressurized fuel return via a throttle, a certain amount of fuel continuously flows out. This will make the
- Membrane accumulator specifically flushed and additional heat loss dissipated, which promotes the accuracy and reliability of the fuel filling of the pump work space during the suction stroke.
- the pump piston carries a on its piston section near the engine compartment within the pump cylinder annular leakage oil groove, which is connected on the one hand to the diaphragm accumulator and on the other hand to the fuel return. In this way, the small amount of leakage oil coming from the engine compartment into the annular gap between the pump piston and the pump cylinder is discharged.
- a non-return valve is arranged in the lubricant inflow of the drive chamber and in the fuel inlet, and a pressure limiter is arranged in the lubricant outflow of the drive chamber, and in addition the feed chamber with a
- Immersion of the pump piston in the drive chamber is used to support the filling of the pump work space due to the volume displacement of the lubricant.
- This pressure surge acts on the membrane of the membrane accumulator
- the lubricant pressure in the engine compartment is set approximately equal to the fuel pressure in the fuel storage space of the diaphragm accumulator.
- a higher lubricant pressure would bias the membrane in the wrong direction and severely affect the intended effect.
- the lubricant drain receives a pressure relief valve for pressure adjustment.
- the lubricant flow is limited by a Throttle in lubricant inflow reached.
- the drawing shows a longitudinal section of a fuel injection pump of the distributor type.
- Internal combustion engine has a two-part pump housing 10, which consists of a base body 11 with a hollow cylindrical recess and a pump body 12 which is placed on the end face of the latter and which seals the hollow cylindrical recess in a liquid-tight manner.
- the hollow cylindrical recess forms a drive chamber 13 filled with lubricating oil, which is connected to a lubricating oil circuit via a lubricating oil inflow 14 and a lubricating oil outflow 15.
- a drive unit 16 is arranged in the drive unit space 13 and is driven by a drive shaft 17 mounted in the base body 11.
- a pump cylinder 19 In a coaxial through bore 18 in the pump body 12, a pump cylinder 19 is inserted, in which a pump piston 20 is guided so as to be axially displaceable.
- the pump piston 20 has an axial blind bore 26 which opens into the pump work chamber 22.
- a radial distributor bore 27 leads from the blind bore 26 and on the other hand two radial relief bores 28, 29 arranged at a distance from one another and symmetrically to the distributor bore 27.
- the relief bores 28, 29 are arranged diametrically to the distributor bore 27, that is to say they are rotated through 180 ° in the pump piston 20.
- the distributor bore 27 communicates with a number of distributor channels (not visible) in the pump cylinder 19.
- the number of distributor channels arranged offset by the same circumferential angle in the pump cylinder 19 corresponds to the number of cylinders of the internal combustion engine.
- Each distribution channel is connected to an injection valve or injection nozzle assigned to a cylinder of the internal combustion engine.
- the relief bore 28 connects during the rotation of the pump piston 20 with a number of filling bores 30, which are arranged offset by the same angle of rotation in the pump cylinder 19.
- the filling bores 30, which run obliquely at an acute angle to the pump piston axis, are connected to an annular channel 31 which is connected to the inclined channel 24 leading to the diaphragm accumulator 23.
- the number of filling bores 30 corresponds to the number of distribution channels, the
- Filling bores 30 are arranged so that the relief bore 28 is always connected to one of the filling bores 30 when the distributor bore 27 does not correspond to one of the distributor channels.
- the pump piston 20 is driven in a rotating and at the same time axially back and forth movement by the drive mechanism 16, for which purpose the pump piston 20 projects with its free end remote from the pump working chamber 22 into the drive mechanism chamber 13 and there with a Cam 32 is rotatably connected.
- the cam disk 32 is axially movably connected to the drive shaft 17 via a dog clutch 33.
- a roller holder 34 is arranged in a rotationally fixed manner.
- the roller holder 34 carries a plurality of rollers 35 which are engaged with a cam surface formed on the end face of the cam plate 32.
- the cam disk 32 is pressed onto the rollers 35 in the axial direction by means of a plate spring 36, which is supported on the pump body 12. If the drive shaft 17 rotates, the rotational movement is transmitted to the pump piston 20 via the dog clutch 33 and the cam disk 32. At the same time, the pump piston 20 is set in a reciprocating movement via the cam disk 32 and the rollers 35.
- the membrane accumulator 23 has a membrane 37 which separates a fuel storage chamber 38 from a pressure chamber 39. In the fuel storage space 38, the one
- Fuel inlet 40 is connected, the inclined channel 24 of the connection between the pump working chamber 22 and the diaphragm accumulator 23 opens.
- the fuel storage chamber 38 is connected to a leakage oil groove 42 on the pump piston 20 via a connecting bore 41 penetrating the pump body 12 and the pump cylinder 19.
- a throttle 50 is formed in the connecting bore 41.
- the leakage oil groove 42 is formed as an annular groove on the piston section close to the engine compartment 13.
- the leakage oil groove 42 is connected to a fuel return 44 via a further connection bore 43 which penetrates the pump cylinder 19 and the pump body 12.
- the pressure chamber 39 of the diaphragm accumulator 23 can be connected to the ambient air, or - as shown in the drawing - can be connected to the engine compartment 13 via a lubricating oil hole 45 in the pump body 19.
- a check valve 46 or 47 is arranged both on the lubricating oil inflow -14 and on the fuel inflow 40, and the lubricating oil drain 15 is provided with a pressure limiter 48.
- the pressure limiter 48 By means of the pressure limiter 48, the pressure level in the engine compartment 13 is set to approximately the same pressure level as that prevailing in the fuel storage space 38. Limitation of the lubricating oil flow is achieved by means of a throttle 49 in the lubricating oil inflow 14.
- the pump piston 20 is set in a rotating and back-and-forth movement by the drive shaft 17.
- the pump piston 20 carries out a suction stroke when the volume of the pump work chamber 22 increases, when it moves downward and penetrates deeper into the engine compartment 13, and a compression or pressure stroke when the volume of the pump work chamber 22 decreases, when it moves upwards , so again moved out of the engine compartment 13.
- the switching valve 21 is opened, so that fuel from the fuel storage space 38 of the membrane accumulator 23 via the opened connection 24, 25 into the
- the pump piston 20 has rotated so far that at the end of the suction stroke the connection between relief bore 28 and filling bore 30 is interrupted.
- the pump piston 20 now begins to move upward, the distributor bore 27 communicating with a distributor channel leading to an injection valve.
- the fuel which is under injection pressure in the pump working chamber 22 is conveyed via the axial blind bore 26 and the distributor bore 27 to the associated injection valve and is injected there into the combustion chamber of the cylinder.
- the pressure acting radially on the pump piston 20 via the distributor bore 27 is opposed by the same pressure acting radially on the pump piston 20 via the relief bores 28, 29.
- the diaphragm accumulator 23 serves to prevent brief pressure drops during the suction stroke as a result of the large filling volume flowing out into the pump working space 22. If - as shown in the drawing - the pressure chamber 39 of the diaphragm accumulator 23 is connected to the engine compartment 13, the merabran accumulator 23 can also be used to improve the filling of the pump working chamber 22. During the suction stroke, the pump piston 20 penetrates deeper into the engine compartment 13 and causes one here
- the pressure surge occurring in the engine compartment 13 acts in the pressure chamber 39 of the diaphragm accumulator 23 on the diaphragm 37 and brings about a brief pressure increase in the fuel storage chamber 38. This pressure increase improves and accelerates the filling of the pump work chamber 22 with fuel.
- An optimal effect is obtained when the lubricating oil pressure in the engine compartment 13 is approximately equal to the fuel pressure usually prevailing in the fuel storage space 38 of the membrane accumulator 23. If the lubricating oil pressure is too high, the diaphragm 37 is biased in the wrong direction and the effect of the pump piston 20 immersed in the lubricating oil volume is greatly reduced.
- the fuel storage space 38 of the diaphragm accumulator 23 By connecting the fuel storage space 38 of the diaphragm accumulator 23 to the fuel return 44, the fuel storage space 38 is flushed in a targeted manner and additional heat is dissipated. As a result, the fuel is essentially kept at a constant temperature level, which increases the reliability and reproducibility of the fuel filling of the pump work chamber 22. A restriction of the fuel outflow is achieved by means of the throttle 50.
- the invention is not limited to the described embodiment of a fuel injection pump.
- the relief bore 28 can be used for additional filling of the pump work chamber 22 with fuel bypassing the electromagnetic switching valve 21.
- the filling bores 30 would then have to be designed accordingly.
Landscapes
- Engineering & Computer Science (AREA)
- Chemical & Material Sciences (AREA)
- Combustion & Propulsion (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Fuel-Injection Apparatus (AREA)
- Reciprocating Pumps (AREA)
Description
Claims
Applications Claiming Priority (3)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
DE3928612 | 1989-08-30 | ||
DE3928612A DE3928612A1 (de) | 1989-08-30 | 1989-08-30 | Kraftstoffverteilereinspritzpumpe fuer brennkraftmaschinen |
PCT/DE1990/000576 WO1991003639A1 (de) | 1989-08-30 | 1990-07-26 | Kraftstoffverteilereinspritzpumpe für brennkraftmaschinen |
Publications (2)
Publication Number | Publication Date |
---|---|
EP0489740A1 true EP0489740A1 (de) | 1992-06-17 |
EP0489740B1 EP0489740B1 (de) | 1994-04-13 |
Family
ID=6388143
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
EP90910549A Expired - Lifetime EP0489740B1 (de) | 1989-08-30 | 1990-07-26 | Kraftstoffverteilereinspritzpumpe für brennkraftmaschinen |
Country Status (6)
Country | Link |
---|---|
US (1) | US5207201A (de) |
EP (1) | EP0489740B1 (de) |
JP (1) | JPH05500697A (de) |
KR (1) | KR0167112B1 (de) |
DE (2) | DE3928612A1 (de) |
WO (1) | WO1991003639A1 (de) |
Families Citing this family (15)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
DE4315646A1 (de) * | 1993-05-11 | 1994-11-17 | Bosch Gmbh Robert | Kraftstoffeinspritzpumpe für Brennkraftmaschinen |
JP3567485B2 (ja) | 1994-05-13 | 2004-09-22 | 株式会社デンソー | 燃料噴射ポンプ |
US6257499B1 (en) | 1994-06-06 | 2001-07-10 | Oded E. Sturman | High speed fuel injector |
US6161770A (en) | 1994-06-06 | 2000-12-19 | Sturman; Oded E. | Hydraulically driven springless fuel injector |
US5471959A (en) * | 1994-08-31 | 1995-12-05 | Sturman; Oded E. | Pump control module |
US6148778A (en) | 1995-05-17 | 2000-11-21 | Sturman Industries, Inc. | Air-fuel module adapted for an internal combustion engine |
DE19531811A1 (de) * | 1995-08-30 | 1997-03-06 | Bosch Gmbh Robert | Kraftstoffeinspritzpumpe |
DE19542952A1 (de) * | 1995-11-18 | 1997-05-22 | Bosch Gmbh Robert | Kraftstoffeinspritzpumpe für Brennkraftmaschinen |
DE19543116A1 (de) * | 1995-11-18 | 1997-05-22 | Bosch Gmbh Robert | Kraftstoffeinspritzpumpe für Brennkraftmaschinen |
US6085991A (en) | 1998-05-14 | 2000-07-11 | Sturman; Oded E. | Intensified fuel injector having a lateral drain passage |
DE10156429A1 (de) * | 2001-11-16 | 2003-06-12 | Bosch Gmbh Robert | Hochdruckkraftstoffpumpe mit entlüftetem Membranspeicher |
US6668797B2 (en) * | 2002-05-13 | 2003-12-30 | Advanced Vehicle Technologies | Fuel injection pump system |
US9285040B2 (en) | 2013-10-10 | 2016-03-15 | PSI Pressure Systems Corp. | High pressure fluid system |
USD749692S1 (en) | 2014-10-08 | 2016-02-16 | PSI Pressure Systems Corp. | Nozzle |
JP6411313B2 (ja) * | 2015-11-26 | 2018-10-24 | ヤンマー株式会社 | 燃料噴射ポンプ |
Family Cites Families (14)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
GB468958A (en) * | 1936-01-15 | 1937-07-15 | John Forster Alcock | Improvements in fuel injection pumps for internal combustion engines |
US2582535A (en) * | 1948-04-14 | 1952-01-15 | Preeision Mecanique Soc | Fuel injection pump |
DE3017276A1 (de) * | 1980-05-06 | 1981-11-12 | Robert Bosch Gmbh, 7000 Stuttgart | Kraftstoffeinspritzpumpe fuer brennkraftmaschinen |
DE3049366A1 (de) * | 1980-12-29 | 1982-07-29 | Spica S.p.A., Livorno | Kraftstoffverteiler-einspritzpumpe fuer verbrennungsmotoren |
US4485789A (en) * | 1981-07-31 | 1984-12-04 | The Bendix Corporation | Fuel injector with inner chamber vacuum |
JPS5912131A (ja) * | 1982-07-13 | 1984-01-21 | Nippon Denso Co Ltd | 燃料噴射ポンプの噴射率制御装置 |
US4412519A (en) * | 1982-09-13 | 1983-11-01 | General Motors Corporation | Diesel fuel distributor type injection pump |
DE3310049A1 (de) * | 1983-03-19 | 1984-09-20 | Robert Bosch Gmbh, 7000 Stuttgart | Kraftstoffeinspritzeinrichtung zur einspritzung einer aus mindestens zwei komponenten bestehenden kraftstoffmischung |
JPH0212299Y2 (de) * | 1984-12-28 | 1990-04-06 | ||
JPS623133A (ja) * | 1985-06-28 | 1987-01-09 | Nippon Soken Inc | 内燃機関の燃料噴射制御装置 |
DE3719831A1 (de) * | 1987-06-13 | 1988-12-22 | Bosch Gmbh Robert | Kraftstoffeinspritzpumpe |
DE3722264A1 (de) * | 1987-07-06 | 1989-01-19 | Bosch Gmbh Robert | Kraftstoffeinspritzanlage fuer brennkraftmaschinen |
DE3722265A1 (de) * | 1987-07-06 | 1989-01-19 | Bosch Gmbh Robert | Kraftstoffeinspritzpumpe |
US5000668A (en) * | 1988-04-27 | 1991-03-19 | Diesel Kiki Co., Ltd. | Distribution-type fuel injection pump |
-
1989
- 1989-08-30 DE DE3928612A patent/DE3928612A1/de not_active Withdrawn
-
1990
- 1990-07-26 DE DE59005382T patent/DE59005382D1/de not_active Expired - Fee Related
- 1990-07-26 US US07/836,262 patent/US5207201A/en not_active Expired - Fee Related
- 1990-07-26 JP JP2510262A patent/JPH05500697A/ja active Pending
- 1990-07-26 EP EP90910549A patent/EP0489740B1/de not_active Expired - Lifetime
- 1990-07-26 KR KR1019910701924A patent/KR0167112B1/ko not_active IP Right Cessation
- 1990-07-26 WO PCT/DE1990/000576 patent/WO1991003639A1/de active IP Right Grant
Non-Patent Citations (1)
Title |
---|
See references of WO9103639A1 * |
Also Published As
Publication number | Publication date |
---|---|
KR920702750A (ko) | 1992-10-06 |
WO1991003639A1 (de) | 1991-03-21 |
US5207201A (en) | 1993-05-04 |
EP0489740B1 (de) | 1994-04-13 |
DE3928612A1 (de) | 1991-03-07 |
KR0167112B1 (ko) | 1998-12-15 |
JPH05500697A (ja) | 1993-02-12 |
DE59005382D1 (de) | 1994-05-19 |
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