EP0419612A1 - Kraftstoffeinspritzpumpe für brennkraftmaschinen. - Google Patents
Kraftstoffeinspritzpumpe für brennkraftmaschinen.Info
- Publication number
- EP0419612A1 EP0419612A1 EP19900904766 EP90904766A EP0419612A1 EP 0419612 A1 EP0419612 A1 EP 0419612A1 EP 19900904766 EP19900904766 EP 19900904766 EP 90904766 A EP90904766 A EP 90904766A EP 0419612 A1 EP0419612 A1 EP 0419612A1
- Authority
- EP
- European Patent Office
- Prior art keywords
- pressure
- chamber
- fuel injection
- valve
- 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
Links
- 239000000446 fuel Substances 0.000 title claims abstract description 31
- 238000002347 injection Methods 0.000 title claims abstract description 29
- 239000007924 injection Substances 0.000 title claims abstract description 29
- 238000002485 combustion reaction Methods 0.000 title claims abstract description 13
- 230000001419 dependent effect Effects 0.000 claims description 3
- 238000006073 displacement reaction Methods 0.000 abstract description 2
- 238000010792 warming Methods 0.000 abstract 1
- 239000007921 spray Substances 0.000 description 6
- 238000011084 recovery Methods 0.000 description 2
- 239000000498 cooling water Substances 0.000 description 1
- 230000003111 delayed effect Effects 0.000 description 1
- 238000011161 development Methods 0.000 description 1
- 230000018109 developmental process Effects 0.000 description 1
- 230000000630 rising effect Effects 0.000 description 1
Classifications
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02D—CONTROLLING COMBUSTION ENGINES
- F02D1/00—Controlling fuel-injection pumps, e.g. of high pressure injection type
- F02D1/16—Adjustment of injection timing
- F02D1/18—Adjustment of injection timing with non-mechanical means for transmitting control impulse; with amplification of control impulse
- F02D1/183—Adjustment of injection timing with non-mechanical means for transmitting control impulse; with amplification of control impulse hydraulic
-
- 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
- F02M41/128—Varying injection timing by angular adjustment of the face-cam or the rollers support
Definitions
- the invention relates to a fuel injection pump according to the preamble of the main claim.
- a fuel injection pump according to the preamble of the main claim.
- Such is known from DE-OS 3148 214.
- the pressure valve provided there in the relief load of the resetting space can be controlled depending on the temperature in such a way that it is closed when the internal combustion engine is cold started and is open at the latest when the internal combustion engine is at operating temperature.
- the pressure valve is designed as a check valve which can open at a maximum pressure and which is opened by a thermostatically controlled element. As long as the pressure valve is closed, the same pressure, which is determined by the delivery rate of the fuel feed pump, is established in the pressure chamber and in the resetting space, which pressure also acts on the spray adjustment device and adjusts it in the "early" direction.
- This special early adjustment is canceled at the end of the harmony phase by opening the pressure valve and then the pressure acting on the spray adjustment device is controlled in a known manner as a function of speed by the pressure control valve.
- the special early adjustment improves the cold start behavior and the running of the internal combustion engine in the warm-up phase. It is a disadvantage of the known device that on the pressure control valve when the fuel injection pump is at a standstill, a small remaining gap of the discharge throttle from the pressure chamber to the relief chamber remains open and when the fuel injection pump starts, the delivery pump delivery rate is then insufficient, the required pressure at low speeds in the start-up phase of the internal combustion engine or to generate the fuel injection pump in the pressure chamber or in the recovery room immediately in such a way that the special early adjustment for the cold start is achieved at the same time. It is only with increasing speed and delivery quantity of the feed pump that the desired pressure is delayed.
- the fuel injection pump according to the invention with the characterizing features of the main claim has the advantage that the drain throttle on the pressure control valve is closed quickly and safely during cold start, that the aforementioned pressure for the cold start early adjustment can be reached regularly.
- FIG. 1 shows a first exemplary embodiment of the fuel injection pump according to the invention in a schematic illustration
- FIG. 2 shows a second exemplary embodiment of the invention
- FIG Pressure curve in the pressure chamber in front of the pressure control valve or the control pressure effective at the spray adjustment device for various functional positions.
- a spray adjustment device 2 which has a spray adjustment piston 4 which is displaceable in a cylinder 3 and which is acted upon on one end face by a return spring 5 which is supported in a stationary manner on an end face of the cylinder 3 and on the other end of a spray adjuster working space 6 is limited in the cylinder 3.
- the injection adjuster working space 6 is connected via a throttle bore 7 in the injection adjustment piston to a suction space 9 in the interior of the fuel injection pump.
- the suction chamber 9 is supplied with fuel by a feed pump 10, which is driven synchronously with the fuel injection pump 1, via a pressure line 11, the feed pump taking the fuel from a fuel reservoir 13 via a suction line 12.
- a bypass line 15 is provided in parallel to the feed pump 10, in which a pressure control valve 16 is arranged.
- This has an adjustable wall in the form of a control piston 17, which slides tightly in a cylinder 18 and delimits on one side a pressure chamber 19 into which the bypass line 15 opens out from the pressure line 11.
- the control piston delimits a return space 20, in which a return spring 22 is arranged, which is supported on the one hand on the control piston 17 and on the other hand is supported on an adjustable stop 23.
- the reset space 20 is constantly connected to the pressure space 19 via a throttle 24.
- the reset space 20 is connected to the pressure via a relief line 26 Room 27 of a pressure valve 28 connected, which is designed as a pressure control valve in the form of a check valve, the valve closing member 29 can be pushed open by a temperature-dependent actuator 30.
- This actuator is, for example, a thermostat or an expansion element that is exposed to the cooling water of the internal combustion engine and thus detects the operating temperature of the internal combustion engine. Accordingly, the closing element 29 is pushed open by the actuator when the internal combustion engine is at operating temperature, and thus the relief line 26 is connected to a relief line part 26 leading further to the fuel supply 13 downstream of the valve closing element 29.
- a second pressure valve 33 is connected in parallel to the pressure valve 28 and lies in a bypass line 34 to the pressure valve 28.
- the second pressure valve 33 has a piston 37 which is tightly displaceable in a cylinder 36 and which delimits a pressure chamber 38 on the one side and a relieved space 39 on the other side, in which a return spring 40 which loads the piston 37 is arranged by means of an adjusting member 41 is adjustable.
- the pressure chamber 38 is constantly connected to the delivery side of the feed pump 10 and thus has the same pressure that prevails in the suction chamber 9 or in the pressure chamber 19. By this pressure, the piston 37 is displaceable against the return spring and comes in the course of
- the pressure in the pressure chamber 38 is always the same as in the pressure chamber 19 of the pressure control valve, which ultimately controls this pressure in conjunction with the delivery rate of delivery pump 10, which is driven synchronously with the speed of the fuel injection pump.
- the pressure control valve in the radial wall of the cylinder 18 has a discharge throttle 46 which is connected via a bypass line 15 to the suction line 12 of the feed pump 10 or via this to the relief chamber in the form of the fuel supply 13.
- the cross section of the discharge throttle is determined by the Position of the control piston 17 determined and controlled by its front edge. The position of the control piston is in turn determined by the pressure in the pressure chamber 19 and the force acting on it from the restoring chamber 20.
- This is essentially determined by return spring 22, the pretension of which is in turn determined by the adjustable stop 23.
- This has the shape of a stepped piston, the part 49 of which has a smaller diameter at the end of the reset space 20 and whose larger part 50 includes a working space 51 which is connected via a line 52 to the relief line 26 or to the reset space 20.
- the interior of the fuel injection pump is filled with fuel.
- the feed pump 10 is set in motion and generates a pressure in the
- Suction chamber 9 or pressure chamber 19 of the pressure control valve 16 This pressure propagates via the throttle 24 into the resetting chamber 20 and from there via the line 52 into the working chamber 51. This pressure quickly causes the adjustable stop to be displaced in the direction of the control piston 17, so that it is moved so that the discharge throttle 46 is initially securely closed. This provided that, according to the assumed case of a cold start the relief line 26 is closed by the pressure valve 28 and the bypass line 34 is closed by the second pressure valve 33. As a result, an effective control pressure, which could now be controlled via the pressure control valve 16, can build up very quickly in the interior of the fuel injection pump. Because of the existing pressure equalization between the recovery chamber 20 and the pressure chamber 19, however, the discharge throttle 46 remains closed, so that the pressure in the suction chamber 9 rises quickly.
- the pressure valve 28 When the internal combustion engine is at operating temperature, the pressure valve 28 is open from the start via the actuator 30, the adjustable stop 23 in its normal position which relieves the return spring 22 and the pressure control valve 16 in the normal function. Accordingly, there is a profile of the pressure in the suction chamber 9 as a function of the speed according to the approximately linearly increasing characteristic curve 64 in FIG. 3. Without the measure according to the invention, a pressure curve according to characteristic curve 65 with little pronounced steepness at the start of the speed would result for the cold start.
- FIG. 2 shows a variant of the embodiment according to FIG. 1.
- the work space 51 is connected to the pressure space 19 via a separate line 54, in which a throttle 55 is arranged.
- the pressure chamber 51 is also connected via a controllable pressure-maintaining valve 56 to the suction line 12 of the feed pump 10 or to the relief chamber 13.
- the throttle 55 takes over the decoupling function that the throttle 24 from FIG. 1 had as a connecting element to the working chamber 51.
- the controllable pressure-maintaining valve 56 functions in place of the pressure valve 28 or the second pressure valve 33. With the controllable pressure valve, the pressure in the working space 51 can now be controlled more precisely and taking into account specific parameters.
- the temperature is also the main parameter for this pressure control valve.
Landscapes
- Engineering & Computer Science (AREA)
- Chemical & Material Sciences (AREA)
- Combustion & Propulsion (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Fuel-Injection Apparatus (AREA)
- High-Pressure Fuel Injection Pump Control (AREA)
Description
Claims
Applications Claiming Priority (3)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
DE3912624A DE3912624A1 (de) | 1989-04-18 | 1989-04-18 | Kraftstoffeinspritzpumpe fuer brennkraftmaschinen |
DE3912624 | 1989-04-18 | ||
PCT/DE1990/000235 WO1990012957A1 (de) | 1989-04-18 | 1990-03-23 | Kraftstoffeinspritzpumpe für brennkraftmaschinen |
Publications (2)
Publication Number | Publication Date |
---|---|
EP0419612A1 true EP0419612A1 (de) | 1991-04-03 |
EP0419612B1 EP0419612B1 (de) | 1994-08-03 |
Family
ID=6378874
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
EP90904766A Expired - Lifetime EP0419612B1 (de) | 1989-04-18 | 1990-03-23 | Kraftstoffeinspritzpumpe für brennkraftmaschinen |
Country Status (5)
Country | Link |
---|---|
US (1) | US5085196A (de) |
EP (1) | EP0419612B1 (de) |
JP (1) | JP2895218B2 (de) |
DE (2) | DE3912624A1 (de) |
WO (1) | WO1990012957A1 (de) |
Families Citing this family (3)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
DE4117813A1 (de) * | 1991-05-31 | 1992-12-03 | Bosch Gmbh Robert | Kraftstoffeinspritzpumpe fuer brennkraftmaschinen |
US5462033A (en) * | 1992-04-09 | 1995-10-31 | Lucas Industries Public Limited Company | Fuel pumping apparatus |
DE19832842C1 (de) * | 1998-07-21 | 2000-02-17 | Bosch Gmbh Robert | Kraftstoff-Fördersystem zur Kraftstoffversorgung einer Brennkraftmaschine |
Family Cites Families (14)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
DE1932600C3 (de) * | 1969-06-27 | 1978-07-27 | Robert Bosch Gmbh, 7000 Stuttgart | Kraftstoffeinspritzanlage für selbstzündende Brennkraftmaschinen mit Änderung des Spritzbeginns |
DE2854422A1 (de) * | 1978-12-16 | 1980-07-03 | Bosch Gmbh Robert | Kraftstoffeinspritzanlage fuer diesel- brennkraftmaschinen, insbesondere fuer fahrzeug-dieselmotoren |
DE2925418A1 (de) * | 1979-06-23 | 1981-01-29 | Bosch Gmbh Robert | Kraftstoffeinspritzpumpe fuer brennkraftmaschinen |
DE2931938A1 (de) * | 1979-08-07 | 1981-02-26 | Bosch Gmbh Robert | Kraftstoffeinspritzpumpe fuer brennkraftmaschinen |
DE2931937A1 (de) * | 1979-08-07 | 1981-02-26 | Bosch Gmbh Robert | Kraftstoffeinspritzpumpe fuer brennkraftmaschinen |
DE3037730A1 (de) * | 1980-10-06 | 1982-05-19 | Robert Bosch Gmbh, 7000 Stuttgart | Kraftstoffeinspritzanlage fuer brennkraftmaschinen |
DE3138606A1 (de) * | 1981-09-29 | 1983-04-14 | Robert Bosch Gmbh, 7000 Stuttgart | Kraftstoffeinspritzpumpe fuer brennkraftmaschinen |
DE3138607A1 (de) * | 1981-09-29 | 1983-04-14 | Robert Bosch Gmbh, 7000 Stuttgart | Kraftstoffeinspritzpumpe fuer brennkraftmaschinen |
DE3211877A1 (de) * | 1982-03-31 | 1983-10-06 | Bosch Gmbh Robert | Kraftstoffeinspritzpumpe |
DE3410146A1 (de) * | 1984-03-20 | 1985-10-03 | Robert Bosch Gmbh, 7000 Stuttgart | Kraftstoffeinspritzpumpe fuer brennkraftmaschinen |
DE3517974A1 (de) * | 1985-05-18 | 1986-11-20 | Robert Bosch Gmbh, 7000 Stuttgart | Kraftstoffeinspritzpumpe fuer brennkraftmaschinen |
GB2178559A (en) * | 1985-07-26 | 1987-02-11 | Perkins Engines Group | Fuel injection pump |
DE3619325A1 (de) * | 1986-06-09 | 1987-12-10 | Bosch Gmbh Robert | Kraftstoffeinspritzpumpe fuer brennkraftmaschinen |
DE3822257A1 (de) * | 1988-07-01 | 1990-01-04 | Bosch Gmbh Robert | Kraftstoffeinspritzpumpe fuer brennkraftmaschinen |
-
1989
- 1989-04-18 DE DE3912624A patent/DE3912624A1/de not_active Withdrawn
-
1990
- 1990-03-23 US US07/623,928 patent/US5085196A/en not_active Expired - Fee Related
- 1990-03-23 EP EP90904766A patent/EP0419612B1/de not_active Expired - Lifetime
- 1990-03-23 DE DE59006681T patent/DE59006681D1/de not_active Expired - Fee Related
- 1990-03-23 WO PCT/DE1990/000235 patent/WO1990012957A1/de active IP Right Grant
- 1990-03-23 JP JP2504715A patent/JP2895218B2/ja not_active Expired - Fee Related
Non-Patent Citations (1)
Title |
---|
See references of WO9012957A1 * |
Also Published As
Publication number | Publication date |
---|---|
DE59006681D1 (de) | 1994-09-08 |
WO1990012957A1 (de) | 1990-11-01 |
DE3912624A1 (de) | 1990-10-25 |
US5085196A (en) | 1992-02-04 |
EP0419612B1 (de) | 1994-08-03 |
JPH03505477A (ja) | 1991-11-28 |
JP2895218B2 (ja) | 1999-05-24 |
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Legal Events
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