EP0302904B1 - Kraftstoffeinspritzpumpe für eine brennkraftmaschine - Google Patents

Kraftstoffeinspritzpumpe für eine brennkraftmaschine Download PDF

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Publication number: EP0302904B1
Authority: EP; European Patent Office
Prior art keywords: valve element; pump piston; fuel; piston; fuel injection
Prior art date: 1987-01-30
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.): Expired - Lifetime

Application number

EP88900804A

Other languages

German (de)

English (en)

French (fr)

Other versions

EP0302904A1 (de

Inventor

Peter Fuchs

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.)

MAN B&W Diesel AS

Original Assignee

Nova Werke AG

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.)

1987-01-30

Filing date

1988-01-25

Publication date

1991-05-08

1988-01-25 Application filed by Nova Werke AG filed Critical Nova Werke AG

1988-01-25 Priority to AT88900804T priority Critical patent/ATE63367T1/de

1989-02-15 Publication of EP0302904A1 publication Critical patent/EP0302904A1/de

1991-05-08 Application granted granted Critical

1991-05-08 Publication of EP0302904B1 publication Critical patent/EP0302904B1/de

2008-01-25 Anticipated expiration legal-status Critical

Status Expired - Lifetime legal-status Critical Current

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Classifications

- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
- 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
- F02M59/30—Varying fuel delivery in quantity or timing with variable-length-stroke pistons
- 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
- F02M59/361—Valves being actuated mechanically
- 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
- F02M59/46—Valves
- 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
- F02M2200/00—Details of fuel-injection apparatus, not otherwise provided for
- F02M2200/30—Fuel-injection apparatus having mechanical parts, the movement of which is damped

Definitions

the invention relates to a fuel injection pump for an internal combustion engine with a pump piston guided in a cylinder, the stroke of which is adjustable, a valve arrangement arranged in the axis extension of the pump piston above the cylinder chamber and in front of the injection line, with a valve body which has its lower end in the cylinder chamber protrudes and cooperates with it at the top dead center of the pump piston, the valve arrangement opening or closing a connection between the cylinder space and a return line and an actuating device for the piston stroke.
a fuel injection pump of this type is known from German Offenlegungsschrift No. 31 00 725 A1.
This publication describes in particular in connection with FIG. 7 a fuel injection pump which has an overflow valve actuated by the pump piston.
a fuel chamber is arranged above the cylinder space and is connected to the cylinder space via a connecting channel.
the overflow valve is arranged parallel to the fuel channel and closes a passage from the fuel chamber into a return line to the fuel feed system.
a valve lifter connected to the valve is in the upper area of the cylinder chamber and is in contact with the top of the pump piston.
the valve with the valve tappet is held against the valve seat by a spring ie pressed in the direction of the upper region of the cylinder space.
a connection bore which leads into the injection line.
the pump piston is driven by appropriate devices, as also described in this publication. In the course of the stroke movement of the pump piston, the fuel is compressed in the cylinder space and pressed through the connecting bore into the fuel space and from here into the injection line.
the injection nozzles are released in a known manner, and the injection process into the cylinders of the internal combustion engine begins.
the end face of the pump piston touches the end of the valve stem and presses on the overflow valve. This clears the connection hole between the fuel chamber and the return flow line, and the pressure in the cylinder chamber of the fuel chamber and the injection line is immediately reduced. As a result of the reduction in pressure, the injection nozzle is also closed and the injection process is stopped.
a valve actuated by the pump piston which is equipped with hydraulic damping to increase the service life.
the end of the valve assigned to the pump piston is conical, and the cylinder space has no connecting line to the overflow space.
an increased pressure is to be created in the remaining cylinder space, which causes a displacement across the conical valve end face of the valve.
the damping effect of this arrangement is difficult to control and adjust. If the pressure in the cylinder chamber is relieved, the piston and valve hit each other with full force, which leads to unbearable damage and malfunctions.
the application shown here cannot be used for high-pressure systems because the acting forces are not reduced.
a first hydraulic damping device is arranged at the lower end of the valve body and a second hydraulic damping device is arranged in the region of the upper end of the valve body, each of the two damping devices has a pressure chamber filled with fuel, a displacement body and a gap space, the valve body has a core cavity for the passage of fuel from the cylinder space into the injection line and its upper end is guided into the area of the injection line in the pump housing and is supported there in a guide bore.
a second hydraulic damping device is arranged on the one-piece valve body in the upper region, which ensures that the valve body and so that the pump piston cannot shoot upwards due to the high acting forces.
the first and the second hydraulic damping device each have a pressure chamber filled with fuel, a displacement body and a gap space.
the fuel is displaced from the pressure chamber by means of the displacement body via the gap space.
the valve body is guided in a cavity, the lower end of which adjoins the cylinder chamber and the upper end of which is the injection line. This enables the symmetrical arrangement of the valve body, cavities surrounding the valve body and feed lines around the axis of the injection pump.
a preferred embodiment of the invention is characterized in that, in the first hydraulic damping device, a circular cavity arranged in the head part of the pump piston and open towards the valve body forms the pressure chamber, the lower end of the valve body is immersed in the cavity at the top dead center of the pump piston and forms the displacement body , the diameter of this cavity is slightly larger than the diameter of the lower end of the valve body, and between the outer surface of the lower end of the valve body and the outer surface of the cavity, the gap is formed.
the ratio of the annular cross-sectional area of the gap space to the cross-sectional area of the pump piston is preferably at most 1: 500 and at least 1: 1000.
the ratio of the diameter of the lower end of the valve body to the diameter of the pump piston is at most 1: 1, 2 and minimum 1: 2.5.
the diameter of the pump piston is essentially determined by the desired maximum injection pressure and the maximum possible movement length of the stroke of the pump piston.
the diameter of the lower end of the valve body, or of the displacement body results from the permissible surface pressure between the valve body end surface and the base surface of the cavity in Head part of the pump piston at the residual force acting before top dead center.
a preferred embodiment of the invention consists in that the lower end of the valve body has a graduated diameter in the area of the penetration length into the cavity, the largest diameter in this area determining the gap space. This embodiment enables a simpler manufacture of the damping device and a precise adaptation to the operating conditions.
a further preferred embodiment of the invention consists in that in the second hydraulic damping device the pressure chamber is arranged around a partial area of the valve body, the guide bore, into which the upper end of the valve body is guided, adjoins this pressure chamber and a piston surface is arranged in this pressure chamber on the valve body and the gap is formed between the outer surface of the upper end of the valve body and the outer surface of the guide bore.
the ratio of the annular cross-sectional area of the gap to the cross-sectional area of the pump piston is a maximum of 1: 600 and a minimum of 1: 1100.
the ratio of the diameter of the upper end of the valve body to the diameter of the pump piston is a maximum of 1: 1.5 and a minimum of 1: 3 of the valve body in the direction of the injection line, the fuel, which is located in the pressure chamber around a partial area of the valve body, is compressed by the piston surface arranged on the valve body.
the pressure increase in the fuel in this pressure chamber causes the fuel to flow into the injection line via the gap between the outer surface of the upper end of the valve body and the outer surface of the guide bore
Pressure build-up in the pressure chamber initially acts on the valve body like a spring and then, as a result of the outflow via the gap space, reduces the accelerations and forces acting on the valve body until equilibrium is established.
the course of the damping can be precisely predetermined by the appropriate choice of the diameter and the cross-sectional area of the gap and with the aid of known calculation methods.
the damping device has a self-regulating effect in certain areas, since when the forces and accelerations acting on the valve body are increased, higher counterforces also occur in the pressure chamber and the damping takes a correspondingly different course.
This arrangement of the damping device thus makes it possible to change the operating states of the fuel injection pump and to avoid impermissible force and acceleration processes in the area of the pump piston and the valve body and corresponding damage.
Another advantage is that the fuel itself can be used as damping means and no additional pressure means are necessary.
the core cavity arranged in the valve body is open at the upper end of the valve body, at the lower end of the valve body via side bores with the cylinder space, and in the region of the beginning of the guide bore via side bores with the pressure space.
a preferred embodiment of the invention is characterized in that the core cavity arranged in the valve body is open at the upper end and at the lower end of the valve body in the direction of the axis and is connected to the pressure chamber via side bores in the region of the beginning of the guide bore, a pin in the cavity of the pump piston protrudes beyond the base and this pin fits into the core cavity at the lower end of the valve body.
the continuous core cavity enables an optimal flow for the fuel flow. All axial and radial forces on the valve body can be compensated, so that no asymmetrical loads occur.
the closure of the core cavity by the pin on the pump piston in the area of the top dead center results in additional damping and prevents fuel from flowing into the fuel line to the nozzle.
a further preferred embodiment of the invention is characterized in that the valve body is enclosed in a partial area by an annular space in which the bores of the fuel supply line and the fuel discharge line open, in this annular space a piston ring surface is arranged on the valve body and at the lower end of the annular space between the Valve body and the cylinder liner an annular valve seat is formed.
valve body During the suction process, ie the downward movement of the pump piston, the valve body is kept in an equilibrium state by the piston ring surface arranged in this annular space, or by the pressure of the fuel supply system acting on this annular surface and the compression spring arranged in the pressure space in the upper region of the valve body.
the suction negative pressure generated in the cylinder chamber acts on the pressure chamber in the upper area via the core cavity in the valve body and causes the pressure to be too low Inflow of fuel into the cylinder chamber an additional opening of the valve seat.
the construction of the valve arrangement is considerably simplified by the combination of the suction valve and the overflow valve in one valve seat, and there is also the additional advantage of the symmetrical arrangement around the pump axis.
a further improvement of the fuel injection pump can be achieved in that the pump piston, the valve body and the guide bore are enclosed by a one-piece cylinder liner and this cylinder liner is only attached to the pump housing at the upper end in the direction of the pump axis.
This one-piece design of the cylinder liner with only one-sided support brings significant advantages in that thermal expansions of the liner do not lead to the bracing thereof and the liner itself is not mechanically clamped in the axial direction. As a result, deformations of the cylinder space due to possible compressive forces acting on the cylinder liner are avoided. This in turn leads to less susceptibility to faults in the course of the movement of the pump piston in the cylinder space.
the cylinder liner is at least partially enclosed by a casing of the housing, this housing casing has longitudinal bores which are connected to the fuel supply lines and fuel discharge lines and are filled with fuel in the operating state, and the lower end of the cylinder liner ends in an unpressurized leakage space in the Casing of the housing.
the housing jacket and the pump cylinder can be heated uniformly over the entire sealing length via the fuel circulating in these longitudinal bores, and the thermal load on the jacket and the cylinder liner can thus be significantly reduced.
the cylindrical contact surfaces between the cylinder liner and the casing shell form a metallic one Seal with a sealing gap, the lower end of which opens into an unpressurized leakage space. This has the advantage that no further seals, for example in the form of rubber rings, are necessary for the sealing between the cylinder liner and the housing jacket. This arrangement also enables substantially better control of the overflow pressures within the pump housing.
An improvement in the drive of the pump piston results from the fact that an additional piston is arranged at the lower end of the pump piston and this additional piston is part of a pneumatic or hydraulic spring which acts against the drive stroke of the pump piston. Furthermore, an actuating element of the drive and control device lies loosely against the lower end of the pump piston.
the drive and control device for the pump piston is known and can be designed, for example, in accordance with FIG. 5 of German Offenlegungsschrift 31 00 725. However, it is also possible to carry out the drive mechanically, hydraulically or in another type of combination.
the actuating element lying loosely on the pump piston pushes the pump piston upwards during the stroke movement.
the additional piston is also pushed upwards and a hydraulic or pneumatic pressure medium is compressed in a storage space.
this compressed pressure medium causes the pump piston to return and thus has the advantage that no positive mechanical coupling is necessary between the drive and control device and the pump piston.
the actuating element of the drive and control device can move independently of the latter in the region of the bottom dead center of the pump piston and any deviations in the course of movement can be absorbed.
a further improvement in the setting of the stroke movement can be achieved in that a relief valve with a connection is located in the injection line after the valve body to the fuel circuit.
the pump piston Before starting up the injection pump, the pump piston is brought to the top dead center since this ensures a clearly defined starting position for the pump piston.
the relief valve is opened and the fuel displaced by the pump piston can flow back into the fuel circuit.
the stroke of the pump piston is now always set from top dead center downwards via the drive and control device. The movements of the pump piston are always based on a precisely defined position.
the fuel injection pump shown in Figure 1 shows an injection pump for a diesel engine, which generates injection pressures in the order of 2500 bar.
the injection pump consists of a housing 3 with a housing flange 5.
a cylinder liner 2 is installed in the housing 3, in which the cylinder space 10 is arranged.
a pump piston 1 is guided, which is connected at its lower end to an actuating element 19 of a device which controls the drive and the stroke setting of the pump piston 1 is used.
This device consists of a known mechanical and / or hydraulic drive and actuating device, for example according to German Offenlegungsschrift 31 00 725, and is not shown in more detail in FIG. 1.
the fuel is fed to the injection pump via fuel supply lines 8 and excess fuel is carried away via the fuel discharge lines 9.
the fuel compressed and delivered in the cylinder space 10 by the pump piston 1 is guided through a core cavity 20 in a valve body 4 to the injection line 7 and from here to the injection nozzles on the internal combustion engine.
a unit of the injection pump shown is available for each cylinder of the internal combustion engine.
the valve body 4 is arranged in a cavity 14 in the cylinder liner 2, which extends from the upper end of the cylinder space 10 to the beginning of the injection line 7.
the lower end 11 of the valve body 4 protrudes into the cylinder space 10 and touches the head part 13 of the pump piston 1 at the top dead center.
the upper end 12 of the valve body 4 is guided in an intermediate part 21 with a guide bore 22.
the valve body 4 is mounted in a sliding guide 23 of the cylinder liner 2.
a pressure chamber 24 is located between the slide guide 23 and the intermediate part 21.
the valve body 4 has a piston surface 25 in the region of the pressure chamber 24, pressure prevailing in the pressure chamber 24 pushing the valve body 4 downward in the direction of the pump piston 1.
a compression spring 26 is installed in the pressure chamber 24 between the piston surface 25 and the end surface of the intermediate part 21.
a fuel ring channel 28 is arranged around the valve body 4, in which the bores 29 and 30 open.
the fuel channel 28 is through a valve seat 27 sealed against the cylinder space 10.
This valve seat 27 enables fuel to be sucked into the cylinder space 10 when the pump piston 1 moves downward, specifically from the fuel feed line 8 via the bore 29, the fuel channel 28 and the annular space 31.
the valve seat 27 is open, the cylinder space 10 Excess fuel flows through the annular space 31 into the fuel channel 28 and then through the bore 30 into the fuel discharge line 9.
the valve body 4 with the valve seat 27 thus simultaneously serves as an intake and overflow valve.
the fuel is conveyed from the cylinder space 10 through holes 32 into the core cavity 20 and from there through the injection line 7 to the injection nozzles.
pressure is built up in the pressure chamber 24 via side bores 33 and the valve seat 27 is firmly closed by acting on the piston surface 25 and the resulting differential force.
the fuel supply line 8 is guided into an annular channel 34 in the housing 3, which is connected to longitudinal bores 35.
These longitudinal bores 35 are distributed around the entire jacket of the housing 3 and open into a second annular channel 36, which establishes the connection to the fuel discharge line 9.
the fuel flowing through these longitudinal bores 35 during pump operation temperates the jacket of the housing 3 and ensures a uniform heat distribution along the entire sealing length of the pump piston 1 and the reduction of the thermal stresses in the injection pump.
the cylinder liner 2 has a fastening and sealing flange 37 at its upper end.
This flange 37 is clamped between a support surface 38 on the housing 3 and the housing flange 5.
the attachment is carried out using attachment means, not shown, for example screws, which are arranged in the region of several axes 39.
the sealing between the mounting flange 37, the bearing surface 38 of the housing 3 and the housing flange 5 takes place by pressing the contact surfaces together with a correspondingly high contact pressure.
the fuel pump is metallically sealed from the outside and can also withstand very high pressure surges in the channel 36 when the valve seat 27 is opened, for example at 2500 bar.
the cylinder liner 2 is inserted into the bore 40 of the housing 3 in the axial direction without additional support.
a known sealing arrangement 6 via which leaking fuel is collected and discharged into the leak line 41.
the seal 6 serves to separate the leakage space 54 and a further cylinder space 42 in the lower region of the housing 3. It is obvious that the cylinder liner in this arrangement does not have any additional forces apart from the forces caused by the pump piston 1 and the pressure build-up in the cylinder space 10 Is subjected to clamping forces, which could lead to deformation of the cylinder chamber 10.
the cylinder liner 2 can expand freely in the direction of the seal 6.
the cylinder liner 2 is completely symmetrical with respect to the pump axis 43, which likewise prevents the occurrence of stress deformations.
This arrangement means that no plastic sealing rings are necessary between the housing 3 and the cylinder liner 2.
the pressure surges which occur in the annular channel 28 when the fuel overflows at the delivery end can be influenced by backflow, which prevents a drop in the pressure in the cavitation area.
the lower end of the pump piston 1 is connected to an additional piston 44 which is guided in the cylinder space 42.
the cylinder space 42 is filled with air and connected to a compressed air supply system or a compressed air reservoir in a known but not shown manner. If the pump piston 1 is moved upward with the additional piston 44, the air in the cylinder space 42 is slightly compressed and acts after the top dead center has been exceeded of the pump piston 1 as a recoil spring.
the actuating element 19 of the lifting and adjusting device, which drives the pump piston 1 bears against the lower surface 45 of the additional piston 44.
the drive can be mechanical, hydraulic or in a combined form, but it is essential that the stroke of the pump piston 1 is measured from top dead center down. This creates a well-known and consistent basis for stroke dimensioning.
a relief valve 46 is arranged in the housing flange 5, via which fuel from the cylinder space 10 via the core cavity 20, the beginning of the injection line 7 and the bores 47 and 48 can be derived into the leak line 41.
the relief valve 46 is actuated via known control elements 49.
FIG. 1 and FIG. 2 show the hydraulic damping devices formed both at the lower end 11 and at the upper end 12 of the valve body 4.
FIG. 2 shows the pump piston 1 at top dead center, the valve seat 27 being open. In contrast to this, the valve seat 27 is closed in FIG. 1, ie the valve body 4 is in its lowest position, and the pump piston 1 is shown during an upward lifting movement or conveying movement.
the first damping device is formed between the lower end 11 of the valve body 4 and the head part 13 of the pump piston 1.
the head part 13 of the pump piston 1 there is a cavity 15 with a circular cross section, which is open towards the lower end 11 of the valve body 4.
this cavity 15 is slightly larger than the diameter of the lower end 11 of the valve body 4, so that the lower end 11 of the valve body 4 can penetrate into the cavity 15. Since the cylinder space 10 is filled with fuel, there is also fuel in the cavity 15 when the pump piston 1 moves upward. That in the cavity 15 penetrating the pump piston 1 lower end 11 of the valve body 4 displaces this fuel through the annular gap 18 existing between the lateral surfaces. This dampens the relative movement between the pump piston 1 and the valve body 4 before the end surface 16 of the lower end 11 of the valve body 4 the base surface 17 hits the pump piston 1 in the cavity 15. Without damping, the lower end 11 of the valve body 4 is immediately damaged and destroyed as a result of the high impulse forces.
the lower end 11 of the valve body 4 has a diameter of 20 mm.
the cavity 15 in the head part 13 of the pump piston 1 is dimensioned in such a way that a gap of approximately 0.025 mm is formed in the annular gap 18.
the width of the gap space 18 can be adapted to the speed of the pump piston 1 and to the maximum pressure in the cylinder space 10. To optimize the depth of penetration or the length of the gap 18 is changed in the axial direction.
the second damping device at the upper end 12 of the valve body 4 comprises the intermediate part 21 and the guide bore 22 as well as the pressure chamber 24 with the associated piston surface 25 on the valve body 4.
a annular gap space 50 is formed, the gap width being approximately 0.02 mm.
valve body 4 As soon as the pump piston 1 or the base surface 17 rests on the head part 13 on the end face 16 of the valve body 4, the valve body 4 is pushed upwards. As a result, the openings of the side bores 33 are pushed and closed into the guide bore 22, and an increased pressure builds up in the pressure chamber 24 due to the displacement of the piston surface 25. This increased pressure acts against the movement of the valve body 4 and prevents it from shooting upwards. If the gap space 50 is dimensioned correctly, enough fuel flows out of the pressure space 24 that the valve body 4 and the pump piston 1 can be moved into the position of the top dead center with the desired speed and damping.
valve seat 27 was also opened and the injection pressure prevailing in the cylinder space 10 as well as in the core cavity 20 and the injection line 7 was relieved via the annular space 31 into the bore 30 and thus the fuel discharge line 9.
the entire system is thus only at the top dead center of the pump piston under the delivery pressure of the fuel supply system.
fuel is sucked into the cylinder space 10 via the valve seat 27.
a further piston surface 51 which is located in the upper region of the annular channel 28, is arranged on the valve body 4.
the delivery pressure prevailing in the annular channel 28 acts on this piston surface 51 and keeps the valve seat 27 open.
FIG 3 shows essentially the same arrangement as Figure 2, and the mode of operation is similar.
the valve body 4 here has a continuous core cavity 55 which is open at the two end regions 11 and 12 of the valve body 4 in the direction of the pump axis 43.
the head part 13 of the pump piston 1 is also designed differently in that a cylindrical pin 52 is arranged in the center of the cavity 15. This gives the cavity 15 in the pump piston 1 an annular base 53.
the foremost part of the lower end 11 of the valve body 4 has a smaller diameter than in the region of the gap space 18.
the pin 52 penetrates into the End of the core cavity 55 and closes it, whereby the damping of the movement via the gap 18 begins. Since a higher pressure is generated in the pressure chamber 24 than in the core cavity 55 and the injection line 7, the damping function is retained via the upper gap space 50.

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Engineering & Computer Science (AREA)
Chemical & Material Sciences (AREA)
Combustion & Propulsion (AREA)
Mechanical Engineering (AREA)
General Engineering & Computer Science (AREA)
Fuel-Injection Apparatus (AREA)
Filling Or Discharging Of Gas Storage Vessels (AREA)
Measuring Or Testing Involving Enzymes Or Micro-Organisms (AREA)
Superstructure Of Vehicle (AREA)

EP88900804A 1987-01-30 1988-01-25 Kraftstoffeinspritzpumpe für eine brennkraftmaschine Expired - Lifetime EP0302904B1 (de)

Priority Applications (1)

Application Number	Priority Date	Filing Date	Title
AT88900804T ATE63367T1 (de)	1987-01-30	1988-01-25	Kraftstoffeinspritzpumpe fuer eine brennkraftmaschine.

Applications Claiming Priority (2)

Application Number	Priority Date	Filing Date	Title
CH330/87		1987-01-30
CH330/87A CH672168A5 (ja)	1987-01-30	1987-01-30

Publications (2)

Publication Number	Publication Date
EP0302904A1 EP0302904A1 (de)	1989-02-15
EP0302904B1 true EP0302904B1 (de)	1991-05-08

Family

ID=4184560

Family Applications (1)

Application Number	Title	Priority Date	Filing Date
EP88900804A Expired - Lifetime EP0302904B1 (de)	1987-01-30	1988-01-25	Kraftstoffeinspritzpumpe für eine brennkraftmaschine

Country Status (11)

Country	Link
US (1)	US4986728A (ja)
EP (1)	EP0302904B1 (ja)
JP (1)	JPH01502044A (ja)
KR (1)	KR950003759B1 (ja)
CN (1)	CN1011525B (ja)
AT (1)	ATE63367T1 (ja)
CH (1)	CH672168A5 (ja)
DE (1)	DE3862708D1 (ja)
FI (1)	FI884481A0 (ja)
PL (1)	PL157661B1 (ja)
WO (1)	WO1988005863A1 (ja)

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US6158419A (en) *	1999-03-10	2000-12-12	Diesel Technology Company	Control valve assembly for pumps and injectors
US6089470A (en) *	1999-03-10	2000-07-18	Diesel Technology Company	Control valve assembly for pumps and injectors
US6450778B1 (en)	2000-12-07	2002-09-17	Diesel Technology Company	Pump system with high pressure restriction
US6655602B2 (en)	2001-09-24	2003-12-02	Caterpillar Inc	Fuel injector having a hydraulically actuated control valve and hydraulic system using same
JP3814245B2 (ja) *	2002-11-21	2006-08-23	ヤンマー株式会社	燃料噴射ポンプ
AU2003209344A1 (en) *	2003-01-24	2004-08-23	Robert Bosch Gmbh	Pump system with variable restriction
DE102005061886A1 (de) *	2005-12-23	2007-07-05	Robert Bosch Gmbh	Hochdruckpumpe, insbesondere für eine Kraftstoffeinspritzeinrichtung einer Brennkraftmaschine
FR2895919B1 (fr) *	2006-01-11	2008-03-14	Pulssar Technologies Sarl	Dispositif de pompage.
JP5478051B2 (ja) *	2008-10-30	2014-04-23	日立オートモティブシステムズ株式会社	高圧燃料供給ポンプ
CN102325987B (zh) *	2009-02-20	2015-04-01	日立汽车***株式会社	高压燃料供给泵及用于该泵的排出阀单元
DE102010064219A1 (de) *	2010-12-27	2012-06-28	Robert Bosch Gmbh	Druckregelanordnung eines Kraftstoffeinspritzsystems mit einem druckseitig von einer Pumpe angeordneten Ventil
ITMI20130500A1 (it) *	2013-04-02	2014-10-03	Bosch Gmbh Robert	Gruppo di pompaggio per alimentare combustibile, preferibilmente gasolio, ad un motore a combustione interna
CN206487579U (zh) *	2017-01-18	2017-09-12	江苏易实精密科技股份有限公司	一种柴油高压燃油喷射器导向套
US10544770B2 (en)	2017-06-29	2020-01-28	Woodward, Inc.	Mecha-hydraulic actuated inlet control valve

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DE655171C (de) *		1938-01-10	Liselotte Elze	Kolbenpumpe
US2449382A (en) *	1945-10-22	1948-09-14	Raul Pateras Pescara	Fuel injection device
DE863573C (de) *	1951-11-25	1953-01-19	Otto Natter	Einspritzpumpe fuer Brennkraftmaschinen
DE2348865A1 (de) *	1973-09-28	1975-04-10	Maschf Augsburg Nuernberg Ag	Vorrichtung zur brennstoffeinspritzung
DE3100725A1 (de) *	1980-12-16	1982-07-01	Gebrüder Sulzer AG, 8401 Winterthur	"einrichtung zur gesteuerten foerderung des brennstoffs in einer brennkraftmaschine"
DE3523536A1 (de) *	1984-09-14	1986-03-27	Robert Bosch Gmbh, 7000 Stuttgart	Elektrisch gesteuerte kraftstoffeinspritzpumpe fuer brennkraftmaschinen
IT1182446B (it) *	1985-02-15	1987-10-05	Weber Spa Azienda Altegna	Pompa di iniezione del combustibile per motori a ciclo diesel per autoveicoli con regolazione della portata e dell anticipo di iniezione asservita alla pressione di alimentazione

1987
- 1987-01-30 CH CH330/87A patent/CH672168A5/de not_active IP Right Cessation
1988
- 1988-01-25 AT AT88900804T patent/ATE63367T1/de not_active IP Right Cessation
- 1988-01-25 US US07/269,734 patent/US4986728A/en not_active Expired - Fee Related
- 1988-01-25 KR KR1019880701200A patent/KR950003759B1/ko not_active IP Right Cessation
- 1988-01-25 WO PCT/CH1988/000014 patent/WO1988005863A1/de active IP Right Grant
- 1988-01-25 EP EP88900804A patent/EP0302904B1/de not_active Expired - Lifetime
- 1988-01-25 DE DE8888900804T patent/DE3862708D1/de not_active Expired - Fee Related
- 1988-01-25 JP JP63500982A patent/JPH01502044A/ja active Pending
- 1988-01-29 PL PL1988270369A patent/PL157661B1/pl unknown
- 1988-01-29 CN CN88100522A patent/CN1011525B/zh not_active Expired
- 1988-09-29 FI FI884481A patent/FI884481A0/fi not_active IP Right Cessation

Also Published As

Publication number	Publication date
JPH01502044A (ja)	1989-07-13
FI884481A (fi)	1988-09-29
CN1011525B (zh)	1991-02-06
CN88100522A (zh)	1988-11-23
US4986728A (en)	1991-01-22
PL270369A1 (en)	1988-09-29
WO1988005863A1 (en)	1988-08-11
ATE63367T1 (de)	1991-05-15
PL157661B1 (pl)	1992-06-30
CH672168A5 (ja)	1989-10-31
KR950003759B1 (ko)	1995-04-18
EP0302904A1 (de)	1989-02-15
KR890700751A (ko)	1989-04-27
FI884481A0 (fi)	1988-09-29
DE3862708D1 (de)	1991-06-13

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