EP0454803A1 - Fuel-injection pump for internal-combustion engines. - Google Patents
Fuel-injection pump for internal-combustion engines.Info
- Publication number
- EP0454803A1 EP0454803A1 EP19900915747 EP90915747A EP0454803A1 EP 0454803 A1 EP0454803 A1 EP 0454803A1 EP 19900915747 EP19900915747 EP 19900915747 EP 90915747 A EP90915747 A EP 90915747A EP 0454803 A1 EP0454803 A1 EP 0454803A1
- Authority
- EP
- European Patent Office
- Prior art keywords
- throttle
- fuel
- fuel injection
- pump
- fuel supply
- 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
- 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
- F02M41/124—Throttling of fuel passages to or from the pumping chamber
-
- 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
- F02M41/126—Variably-timed valves controlling fuel passages valves being mechanically or electrically adjustable sleeves slidably mounted on rotary 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
- 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
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 known from DE-PS 30 13 368
- a series injection pump is provided with an electronic controller, to which the desired load is added via an accelerator pedal.
- a throttle controlling the suction bore to this cylinder is adjusted on each cylinder of the injection pump.
- This throttle With the help of this throttle, maintenance of the operation of the internal combustion engine is to be ensured in the event of a failure of the controller and it is to be reliably avoided that a permissible maximum speed is exceeded.
- This device has the disadvantage that the upstream throttle causes a loss of filling in the pump work spaces, which must be compensated for by the controller for normal operation. This requires a higher design effort such that the fuel injection pump must be designed for a higher output than it actually delivers.
- the fuel injection pump according to the invention with the characterizing features of the main claim has the advantage that the function of the fuel injection quantity control is in no way disturbed when the regulator is intact, and that on the other hand the adjustable throttle with the minimum constant flow cross-section which is also provided in the event of the regulator failing an idle operation and also a load operation as emergency operation mode enables.
- Advantageous developments of the solution according to the invention presented in claim 1 are given by the subclaims.
- control of the throttle element of the throttle is realized in accordance with claim 5, with which a speed-dependent and load-dependent mechanical control of the fuel injection pump can be carried out if the regulator fails.
- FIG. 1 shows a first embodiment in a fixed throttle bypassing a throttle in the fuel supply line
- FIG. 2 shows a variant of the exemplary embodiment according to FIG. 1 with a seat valve as a throttle
- FIG. 3 shows a second variant of the exemplary embodiment according to FIG 1 in a further development of FIG. 2 with a passage cross section forming the fixed throttle in the valve closing member of the seat valve
- FIG. 4 shows a third variant of the exemplary embodiment according to FIG. 1 with a fixed throttle integrated in a rotary slide valve in three functional positions
- FIG. 5 shows the second exemplary embodiment of FIG Invention with a speed-dependent adjustable throttle.
- FIG. 6 shows a third exemplary embodiment with a throttle body of the throttle provided with an oblique control edge
- FIG. 7 shows a fourth exemplary embodiment in a modification of that shown in FIG. 6 with a pressure-compensating annular groove.
- a cylinder bore 2 is provided in a pump housing 1 of a fuel injection pump, in which a pump piston 3 encloses a pump work chamber 4.
- the pump piston is driven in rotation by a cam disk 5, which runs on a roller ring 6 (shown in the drawing by 90 ⁇ in the drawing plane), by means not shown, and carries out a reciprocating pump movement during its rotary movement a suction stroke and a delivery stroke.
- the fuel supply to the pump work space takes place via a fuel supply line 8 which leads into the cylinder 2 from a fuel supply space 9 serving as a fuel supply source, its entry into the cylinder being controlled via longitudinal grooves 10 starting from the end face of the pump piston.
- the fuel supply space is located within the pump housing and is supplied with fuel by means of a fuel feed pump 12, which is usually driven synchronously with the pump piston.
- the fuel delivery pump is connected to a fuel reservoir 15 via a suction line 14.
- a pressure control valve 16 switches ge, the "pressure in the fuel supply chamber 9 is ge controlled by the on speed-dependent promotion of Kraft ⁇ material supply pump addition.
- die ⁇ ser pressure is preferably dependent on the rotational speed, with which the fuel injection pump is operated.
- the pump piston protrudes into the fuel supply chamber on the cam disc side and carries on this part of the pump piston an annular slide 18, with the upper edge of which, for example, the exit of a transverse bore 19 on the pump piston into the fuel supply chamber 9 can be controlled.
- a longitudinal bore 20 in the pump piston extends from the transverse bore 19 and acts as a relief channel with the pump work chamber 4 is in constant communication.
- a radial bore 21 branches off from the relief channel and opens into a distributor groove 22. When the pump piston rotates, it is connected to a fuel injection line 24 one after the other during its delivery stroke. These are arranged according to the number of cylinders to be supplied to the internal combustion engine on the circumference of the cylinder bore 2 in the working area of the distributor groove 22.
- the ring slide 18 is used to control the fuel injection quantity and is axially shifted on the pump piston by an electromagnetic signal box 25, the greater the amount of fuel delivered to one of the injection lines per pump stroke of the pump piston, the greater the ring slide 18 at the top dead center of the pump piston is moved there.
- the electromagnetic signal box as a control element for controlling the fuel injection quantity is controlled by an electrical control device 23, which emits a control signal to the signal box 25 in accordance with operating parameters.
- the speed of the internal combustion engine is recorded as one of the operating parameters via a speed sensor 26 which cooperates with a toothed disk 28 coupled to the drive shaft 27 of the fuel injection pump. This drive shaft also drives the cam disk 6.
- the set position of the electromagnetic signal box 25 is detected by a feedback sensor 29 and the position of the injection timing of the control is also detected using an injection timing indicator 30.
- this can be a sensor that detects the position of the roller ring 6, but it can also be other spray timing sensors such.
- B. needle lift or the like can be provided.
- a signal corresponding to the desired torque to be output by the internal combustion engine is input into the control device via an accelerator pedal 32.
- other parameters such as the temperature or the density of the air supplied to the combustion chambers of the internal combustion engine, can be taken into account when generating the fuel quantity signal to control the signal box.
- Such controls are generally known and therefore do not need to be described in more detail here.
- a spray adjustment piston 34 is also provided, which is displaceable in a working cylinder 35 and is coupled to the roller ring 6, on one side is loaded by a return spring 37 and on the other side a working space 38 in the Includes working cylinder which is connected to the fuel supply chamber 9 via a decoupling throttle 39.
- the injection adjusting piston With the pressure in the fuel supply chamber increasing with the speed, the injection adjusting piston is displaced against the force of the spring 37 and thereby rotates the roller ring 6 so that the piston stroke movement takes place at an earlier angle of rotation of the injection pump drive shaft 27.
- a throttle 40 is arranged in the fuel supply line 8 in the form of a rotary slide valve with a through bore 41.
- This throttle can be actuated by the external lever 42 at the same time as the accelerator pedal 32 and controls the cross section of the fuel supply line. Downstream of this throttle, an electromagnetically actuated shut-off valve 44 can be provided in the fuel supply line 8 immediately before it flows into the cylinder 2 and can completely prevent the fuel supply to the pump work chamber 4 for switching off the internal combustion engine. This valve is also controlled by the control device 23 when, for. B. the power supply to the control device is interrupted by an ignition switch.
- a fixed throttle 46 is arranged in a bypass line 45, which determines the minimum passage cross-section from the fuel supply chamber 9 to the cylinder bore 2 or to the pump work chamber 4.
- a correspondingly actuatable seat valve 140 with a fixed throttle 46 according to FIG. 2, likewise parallel to it, or a seat valve 240 according to FIG. 3 can be provided, in which the fixed throttle as a bore 48 through the closing member 49 of the seat valve 240 is realized.
- the adjustable throttle is designed and is actuated by the accelerator pedal in such a way that even with the smallest accelerator pedal movements, the passage cross section of the fuel supply line 8 is opened very quickly, so that the functionality of the electrical control device is not restricted and the fuel injection quantity is unaffected by the adjustable throttle is controlled by the ring slide 18. Above all, this can be carried out particularly effectively if a conical seat valve 140 or 240 according to the explanations in FIGS. 2 and 3 is used.
- the adjustable throttle takes over the control of the fuel injection quantity in the manner of a suction throttle control.
- the adjustable throttle is now also adjusted as a function of the accelerator pedal 32 and changes the inflow cross section to the pump work space.
- the minimum inflow cross-section is determined by the fixed throttle 46, which must be of such a minimum that the full idling load absorption and the fuel supply for starting the internal combustion engine are guaranteed.
- the flow rate related to the individual delivery stroke of the pump piston drops in a ratio of 1 / n. Because the friction power of the motor increases with the speed, an equilibrium will be established at a corresponding speed between the amount of fuel supplied, the drive power and the resistances. Even if the signal box 25 were set to full fuel injection quantity, the internal combustion engine could be prevented from going through, since the driver takes back the accelerator pedal 32 to influence the drive power, the through bore 41 of the adjustable throttle 40 is closed and the fuel flow to the pump workspace is determined by the fixed throttle.
- the equilibrium ratio given above which can correspond to an idling speed or a medium low speed, is established.
- the fixed throttle can also be arranged in a rotary slide valve 50, as shown in three positions in FIG.
- the rotary slide valve represents the adjustable throttle, which corresponds to the adjustable throttle 40 from FIG. 1, with a through bore 41.
- a transverse channel 52 branches off from this and is designed as a throttle bore.
- the through-bore 41 has a cross-sectional widening 53 such that the inlet 54 is still connected to the inlet-side fuel supply line 8 in a rotary position of the rotary slide valve, in which the outlet 55 of the through-bore 41 is closed, but it is Cross channel 52 is connected to the continuing fuel supply line 8. In this second position of FIG.
- the fixed throttle is in the form of the transverse channel 52 in series with the through bore 55.
- a simple throttle valve Device can be used, as shown in Figure 5.
- a longitudinal slide 57 is provided as a throttle body of the throttle, which has an annular groove 58 on its circumference and can be moved tightly in a blind bore 59, which is open towards the fuel supply space.
- the end face 60 of the longitudinal slide 57 is thus acted upon by the speed-dependent pressure in the fuel supply space and can be displaced against a return spring 61 acting on its other end face.
- This displacement path is limited by an adjustable stop 63, which in turn is actuated by the accelerator pedal 32 in accordance with the control of the rotary valve 40 from FIG. 1.
- the longitudinal slide 57 is displaced against the pressure in the fuel supply space and the annular groove 58 increasingly overlaps the fuel supply line 8, which is preferably supplied with fuel by a constant pressure source.
- a variable cross-section can thus be controlled mechanically and, with the stop 63 adjusted in the direction of the smallest load, quantity control can be achieved via the equilibrium between the return spring 61 and the force acting on the longitudinal slide on the fuel supply space side.
- the return spring 61 can take over the function of an idling spring which controls the passage cross section in the fuel supply line 8 on the annular groove 58.
- the fuel injection pump is constructed in the same way as that of the exemplary embodiment according to FIG. 1.
- an additional stop can also be used to set a residual passage cross-section on the ring slide 58 and also make it possible to close the passage guideline of the fuel supply line 8 completely by manual actuation .
- FIG. 6 shows a modified embodiment of the exemplary embodiment according to FIG. 5.
- a cylindrical throttle body 66 of the throttle which is tightly displaceable in a guide cylinder 65, is provided, which at one end into a piston 67 with a larger diameter and at its other end into passes a piston 68 with a smaller diameter.
- the piston with a larger diameter slides tightly in a cylinder 69, which connects to the guide cylinder 65 and is located opposite via an inlet opening 70 in connection with the control pressure source, the fuel supply chamber 9, which is under speed-dependent pressure.
- the space 71 enclosed by the piston 67 in the cylinder 69 on the side opposite the inlet opening 70 is relieved of pressure via a relief line 72 or leak line.
- the shoulder 76 formed at the transition between the cylindrical throttle body 66 and the piston 68 with a smaller diameter runs obliquely, so that an oblique control edge 77 is formed, through which an inlet opening 78 of the fuel supply line 8 opening into the guide cylinder 65 can be controlled.
- the guide cylinder 65 is closed on the end face and the fuel supply line 8 leads from the part of the guide cylinder enclosed by the shoulder 76 to the pump working chamber of the fuel injection pump in an unlockable manner.
- the piston 68 which is smaller in diameter, is guided tightly through the end face 79 of the guide cylinder 65 and is loaded on the end face there by a return spring 80 corresponding to the return spring 61, such that the throttle body 66 by means of the piston 67 depends on the speed-dependent pressure of the suction chamber 9 is displaceable against the force of the return spring 80 and thus controls the inlet cross section of the inlet opening 78 with its oblique control edge 77.
- the throttle body 66 can be changed in the rotational position by means of a lever 81, the lever 81 corresponding to the Accelerator pedal position can be changed in the direction of rotation.
- the inlet opening 78 is thus fully opened or completely closed according to an earlier or later path.
- the speed which is noticeable in the speed-dependent pressure of the fuel supply space, at which the fuel supply is regulated can also be changed, or the throttle throttling the cross section of the fuel supply line 8 can be adjusted depending on the load.
- FIG. 7 A variant of the embodiment according to FIG. 6 is shown in FIG. 7. This differs from FIG. 6 in that the piston 67 with a larger diameter adjoining the cylindrical throttle body 66 is dispensed with, so that here the cylindrical throttle body 86 with its one A pressure chamber 88 delimits the end face in the guide cylinder 87 and is in turn connected to the fuel supply chamber 9 via the inlet opening 70. Furthermore, the cylindrical throttle body 86 has an annular groove 90, the boundary wall of which faces the inlet opening 70 and runs obliquely to the longitudinal axis of the throttle body, forming an oblique control edge 91.
- the fuel supply line 8 leads from the annular groove 90 to the pump work space and cannot open, and the fuel supply line opens 8 controlled via an inlet opening 92 through the oblique control edge 91 into the annular groove 90.
- the cylindrical throttle body is guided in a manner similar to the embodiment according to FIG. 6 via a piston 93 with a smaller diameter, the piston 93 passing through the end wall 94 of the guide cylinder 87 leads to the outside, there has the lever 81 for rotating the throttle body 86 and is acted upon by the return spring 80 against the fuel pressure in the pressure chamber 88.
- This configuration has the advantage over the preceding one that the throttle body 86 is force-balanced with respect to the annular groove 90 or the force acting on it on the control edge side.
- the guide cylinder 87 is relieved of pressure via a leak line, not shown here.
- the device described makes it possible to bring the safety precautions in the control unit to a low level with increased security against the internal combustion engine going through.
- the fuel metering is no longer dependent solely on the function of the control device and the signal box.
- the embodiment according to the invention can also be used in another type of electrical regulation or control of the fuel injection quantity. This z. B. in fuel injection pumps, the pump work rough is opened or closed via an electrically controlled valve during the pump piston delivery stroke and with the closing the duration and the time of high-pressure fuel generation by the pump piston and thus the injection is determined.
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, dans laquelle il est prévu, pour la commande du débit de carburant, un dispositif de régulation électrique (23) commandant un organe de réglage électrique (25) qui, de son côté, actionne l'élément (18) déterminant le débit d'injection du carburant. L'alimentation en carburant du volume moteur de la pompe s'effectue par l'intermédiaire d'un conduit d'alimentation en carburant (8), dans lequel est montée une soupape d'étranglement réglable (40). Celle-ci est actionnée suivant la position d'une pédale de gaz (32), mais elle commande toutefois une section de passage du conduit d'alimentation (8) toujours plus grande que celle correspondant à la quantité dosée de carburant traversant le dispositif de régulation (23). Une section minimale de passage est déterminée par un étranglement fixe (46). Ce dispositif permet de disposer d'un mode de fonctionnement de secours en cas de panne de la commande électrique du débit d'injection de carburant, sans que le dispositif de secours perturbe la quantité dosée de carburant traversant le dispositif de régulation. L'étranglement fixe (46) empêche notamment qu'un emballement du moteur se produise involontairement de la part du conducteur, en cas de panne du dispositif de régulation.A fuel injection pump for internal combustion engines is described, in which there is provided, for the control of the fuel flow, an electrical regulating device (23) controlling an electrical regulating member (25) which, of its own side, actuates the element (18) determining the fuel injection rate. The engine volume of the pump is supplied with fuel via a fuel supply duct (8), in which an adjustable throttle valve (40) is mounted. This is actuated according to the position of a gas pedal (32), but it nevertheless controls a section of passage of the supply duct (8) always greater than that corresponding to the metered quantity of fuel passing through the device. regulation (23). A minimum passage section is determined by a fixed constriction (46). This device makes it possible to have an emergency operating mode in the event of failure of the electrical control of the fuel injection flow rate, without the emergency device disturbing the metered quantity of fuel passing through the regulating device. The fixed throttle (46) prevents in particular that a runaway of the engine occurs involuntarily on the part of the driver, in the event of failure of the regulating device.
Description
Claims
Applications Claiming Priority (2)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
DE3937709A DE3937709A1 (en) | 1989-11-13 | 1989-11-13 | FUEL INJECTION PUMP FOR INTERNAL COMBUSTION ENGINES |
DE3937709 | 1989-11-13 |
Publications (2)
Publication Number | Publication Date |
---|---|
EP0454803A1 true EP0454803A1 (en) | 1991-11-06 |
EP0454803B1 EP0454803B1 (en) | 1993-05-05 |
Family
ID=6393425
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
EP90915747A Expired - Lifetime EP0454803B1 (en) | 1989-11-13 | 1990-10-24 | Fuel-injection pump for internal-combustion engines |
Country Status (5)
Country | Link |
---|---|
US (1) | US5220894A (en) |
EP (1) | EP0454803B1 (en) |
JP (1) | JPH04503101A (en) |
DE (2) | DE3937709A1 (en) |
WO (1) | WO1991007585A1 (en) |
Families Citing this family (4)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US5701873A (en) * | 1993-11-08 | 1997-12-30 | Eidgenoessische Technische Hochschule Laboratorium Fuer Verbrennungsmotoren Und Verbrennungstechnik | Control device for a filling-ratio adjusting pump |
DE4344865A1 (en) * | 1993-12-29 | 1995-07-06 | Bosch Gmbh Robert | Fuel injection pump |
DE19631655C2 (en) * | 1996-08-05 | 2003-03-27 | Hatz Motoren | Engine shutdown for an internal combustion engine |
DE19948149A1 (en) * | 1999-10-07 | 2001-04-12 | Volkswagen Ag | Fuel delivery system and method for operating the fuel delivery system |
Family Cites Families (14)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
DE1058790B (en) * | 1958-03-26 | 1959-06-04 | Bosch Gmbh Robert | Fuel injection pump for multi-cylinder internal combustion engines |
DE1143674B (en) * | 1961-06-16 | 1963-02-14 | Bosch Gmbh Robert | Fuel injection pump |
FR1452638A (en) * | 1965-06-01 | 1966-04-15 | Bosch Gmbh Robert | Improvements to reciprocating fuel injection pumps allowing fuel overflow at start-up |
FR1528311A (en) * | 1966-06-28 | 1968-06-07 | Bosch Gmbh Robert | Fuel injection pump for internal combustion engines |
DE3004460A1 (en) * | 1980-02-07 | 1981-09-10 | Robert Bosch Gmbh, 7000 Stuttgart | FUEL INJECTION PUMP FOR INTERNAL COMBUSTION ENGINES |
DE3013368A1 (en) * | 1980-04-05 | 1981-10-15 | Daimler-Benz Ag, 7000 Stuttgart | Electronic fuel control system for diesel engine - has throttle reducing fuel when injection pump controller fails |
DE3017275A1 (en) * | 1980-05-06 | 1981-11-12 | Robert Bosch Gmbh, 7000 Stuttgart | FUEL INJECTION PUMP FOR SELF-IGNITIONING INTERNAL COMBUSTION ENGINES |
DE3049366A1 (en) * | 1980-12-29 | 1982-07-29 | Spica S.p.A., Livorno | FUEL DISTRIBUTOR INJECTION PUMP FOR COMBUSTION ENGINES |
GB2109058B (en) * | 1981-11-11 | 1985-02-20 | Lucas Ind Plc | Liquid fuel pumping apparatus |
JPS58149566U (en) * | 1982-03-31 | 1983-10-07 | 株式会社デンソー | distribution type fuel injection pump |
GB8331246D0 (en) * | 1983-11-23 | 1983-12-29 | Lucas Ind Plc | Liquid fuel injection pumping apparatus |
GB8401626D0 (en) * | 1984-01-21 | 1984-02-22 | Lucas Ind Plc | Liquid fuel injection pumping apparatus |
JPS60162267U (en) * | 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 | distribution type fuel injection pump |
DE3711744A1 (en) * | 1987-04-07 | 1988-10-27 | Bosch Gmbh Robert | METHOD AND DEVICE FOR CONTROLLING THE FUEL INJECTION AMOUNT |
-
1989
- 1989-11-13 DE DE3937709A patent/DE3937709A1/en not_active Withdrawn
-
1990
- 1990-10-24 JP JP2514611A patent/JPH04503101A/en active Pending
- 1990-10-24 EP EP90915747A patent/EP0454803B1/en not_active Expired - Lifetime
- 1990-10-24 DE DE9090915747T patent/DE59001368D1/en not_active Expired - Fee Related
- 1990-10-24 US US07/700,125 patent/US5220894A/en not_active Expired - Fee Related
- 1990-10-24 WO PCT/DE1990/000801 patent/WO1991007585A1/en active IP Right Grant
Non-Patent Citations (1)
Title |
---|
See references of WO9107585A1 * |
Also Published As
Publication number | Publication date |
---|---|
EP0454803B1 (en) | 1993-05-05 |
US5220894A (en) | 1993-06-22 |
DE59001368D1 (en) | 1993-06-09 |
WO1991007585A1 (en) | 1991-05-30 |
JPH04503101A (en) | 1992-06-04 |
DE3937709A1 (en) | 1991-05-16 |
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