EP0657642B1 - Fuel injection device for internal combustion engines - Google Patents

Fuel injection device for internal combustion engines Download PDF

Info

Publication number
EP0657642B1
EP0657642B1 EP19940113010 EP94113010A EP0657642B1 EP 0657642 B1 EP0657642 B1 EP 0657642B1 EP 19940113010 EP19940113010 EP 19940113010 EP 94113010 A EP94113010 A EP 94113010A EP 0657642 B1 EP0657642 B1 EP 0657642B1
Authority
EP
European Patent Office
Prior art keywords
valve
pressure
space
high
injection
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.)
Expired - Lifetime
Application number
EP19940113010
Other languages
German (de)
French (fr)
Other versions
EP0657642A3 (en
EP0657642A2 (en
Inventor
Jaroslaw Dipl.-Ing. Hlousek
Peter Dipl.-Ing. Müller
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Robert Bosch GmbH
Original Assignee
Robert Bosch GmbH
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Priority to DE19934341543 priority Critical patent/DE4341543A1/en
Priority to DE4341543 priority
Application filed by Robert Bosch GmbH filed Critical Robert Bosch GmbH
Publication of EP0657642A2 publication Critical patent/EP0657642A2/en
Publication of EP0657642A3 publication Critical patent/EP0657642A3/en
Application granted granted Critical
Publication of EP0657642B1 publication Critical patent/EP0657642B1/en
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

Links

Images

Classifications

    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02MSUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M63/00Other 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
    • F02M63/0003Fuel-injection apparatus having a cyclically-operated valve for connecting a pressure source, e.g. constant pressure pump or accumulator, to an injection valve held closed mechanically, e.g. by springs, and automatically opened by fuel pressure
    • F02M63/0007Fuel-injection apparatus having a cyclically-operated valve for connecting a pressure source, e.g. constant pressure pump or accumulator, to an injection valve held closed mechanically, e.g. by springs, and automatically opened by fuel pressure using electrically actuated valves
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02BINTERNAL-COMBUSTION PISTON ENGINES; COMBUSTION ENGINES IN GENERAL
    • F02B3/00Engines characterised by air compression and subsequent fuel addition
    • F02B3/06Engines characterised by air compression and subsequent fuel addition with compression ignition

Description

State of the art

The invention relates to a fuel injection device for Internal combustion engines according to the preamble of claim 1. At such a fuel injection device known from DE-OS 37 00 687 a high pressure fuel pump delivers fuel from a Low-pressure room in a high-pressure plenum that is connected to high-pressure lines with the individual, in the combustion chamber of the to be supplied Internal combustion engine projecting injection valves is connected, wherein this common pressure storage system by a pressure control device is kept at a certain pressure. To control the Injection times and injection quantities at the injection valves is on These each have an electrically controlled control valve in the high pressure lines used that with its opening and closing the High-pressure fuel injection on the injection valve controls.

It is in the known fuel injection device on everyone Injection valve another pressure storage space provided by the common pressure storage system is filled and in addition to that of High-pressure line discharging high-pressure line also with the Injector is connected. By dividing the storage volume on each injection valve to two pressure chambers, which are separated by a Line of a certain length can be connected there Connection with a throttled outflow of fuel from a pressure chamber acting on the valve member of the injection valve Injection course the requirements of the respective internal combustion engine can be optimally adapted, in particular a slow rise in pressure at the beginning and a high pressure increase at the end of the injection is achievable. The directly from the common high-pressure collection room The amount of fuel supplied to the injector is only as control means for controlling the stroke movement of the valve member of the injector used while the injection quantity completely removed from the respective smaller pressure storage space becomes.

From the document FR-A-2 449 795 there is also a fuel injection device known, in which the control valve on the injection valve the connection of the further pressure storage space with one, the valve member of the injection valve in the opening direction pressurizing pressure chamber during the injection valve during the injection breaks can close. This controls Control valve during the injection breaks on the injection valve to be supplied a connection of the pressure chamber of the injection valve with a relief chamber and thus relieves the pressure chamber of the injection valve member from the high one in the pressure storage space fuel pressure.

However, the known fuel injection device has the disadvantage that it is very expensive to construct and also for the defined limitation of the stroke movements of the valve member additional stroke stop surfaces are provided.

Advantages of the invention

The fuel injection device according to the invention with the characteristic Features of claim 1 contributes to simplification of the entire injector. This will be advantageous simply with a double seat valve electrically controlled control valve reached, the respective Stroke is formed by a valve seat and that the pressure application surfaces of the same size on the valve member in both stroke directions in the open and closed state is pressure balanced, so that the actuating forces of the valve member actuating solenoid valve only the force of a return spring have to overcome.

Another advantage is the through hole in the piston Valve element of the control valve reached, via which the under high Fuel under pressure during the injection breaks from the High pressure area within the control valve in a relief chamber flows out and via which a constant pressure equalization on both valve member faces, or the rooms adjacent to it. An injection pressure curve with a slight increase in pressure at the beginning and to achieve a high injection pressure at the end is the volume of the pressure storage spaces 5 assigned to the injection valves up to 20 times larger than the maximum injection quantity at the injection valve executed, the one at the injection valve at the start of injection reflected fuel pressure in the pressure reservoir for a pressure increase is used to a value above the system pressure. This Pressure increase can be done by dimensioning the high pressure line and a pressure valve in the inlet adjustable Adjust the afterflow into the pressure accumulator in such a way that towards the end of injection the highest fuel pressure is built up in the system. A flow restrictor inserted into the pressure connection of the pressure accumulator prevents the pressure fluctuations from propagating into the system.

Further advantages and advantageous configurations of the object the invention are the description, the drawing and the claims removable.

drawing

An embodiment of the fuel injection device according to the invention is shown in the drawing and is shown in the following Description explained in more detail.

FIG. 1 shows a schematic illustration of the fuel injection device with a longitudinal section through the control valve and the injection valve and Figure 2 shows the design of the valve seats and sealing surfaces of the control valve in an enlarged section from FIG. 1.

Description of the embodiments

In the fuel injection device shown in FIG. 1 is a high-pressure fuel pump 1 on the suction side via a fuel supply line 3 with a fuel-filled low-pressure chamber 5 and on the pressure side via a delivery line 7 with a high-pressure plenum 9 connected, the output of High-pressure fuel pump 1 from an electrical control unit 11 is controllable.

High-pressure lines 13 lead from the high-pressure collecting space 9 to the individual, protruding into the combustion chamber of the internal combustion engine to be supplied Injection valves 15, whereby to control the injection process one electric control valve 17 on each injection valve 15 is inserted into the respective high pressure line 13.

Furthermore, in each high-pressure line 13 there is between the high-pressure plenum 9 and control valve 17, a further pressure storage space 19 is provided, whose volume is about 5 to 20 times larger than the maximum Injection quantity at injection valve 15 per injection process is and the one via two parallel pressure connections with that to the high-pressure plenum 9 leading part of the high pressure line 13 is connected. Here has a first pressure connection 21 in the direction of the pressure storage space 19 opening pressure valve 23 and designed as a check valve a second pressure port 25 to a throttle point 27, wherein about the throttle 27 an uncontrolled backflow of fuel in the part of the high-pressure line 13 leading to the high-pressure collecting space 9 and influencing the pressure in the pressure storage spaces of the remaining injectors should be avoided while the pressure valve 23 enables rapid refilling of the pressure storage space 19. It can be about the design of the throttle 27 and Pressure valve 23 depending on the dimensioning of the high pressure line 13 the inflow and outflow quantity into the pressure storage space 19 adjust especially during high pressure injection, whereby Throttle 27 and pressure valve 23 also in a common pressure connection, can be arranged in series.

The control valve 17 is designed as a 3/2 way valve, the piston-shaped Valve member 29 from one to its one end face one between the housing 31 and a spring plate 33 on Valve member 29 supporting compression spring 35 acting electrical Actuating magnet 37 is actuated, the current supply from the control unit 11 is controlled. The valve member 29 has one on its shaft Ring web 39, the lower one facing away from the actuating magnet 37 Transition surface to the piston skirt is conical and there forms a first conical sealing surface 41 on the valve member 29, which with a conical valve seat 43 cooperates. This in Figure 2 enlarged conical valve seat 43 is by a conical diameter expansion of a, a guide piston part 45 on the valve member 29 receiving guide bore 49 within the housing 31 of the control valve 17 is formed. It is between that Limit valve member 29 on the side remote from the solenoid Guide piston part 45 and the conical valve sealing surface 41 a Annular groove 47 is provided on the valve member 29, which with the wall of the guide bore 49 forms a pressure chamber 51, which is from the guide piston part 45 and the conical valve sealing surface 41 on the ring web 39 limited and into a part of the pressure storage space 19 leading away the high pressure line 13 to the control valve 17 opens such that the Mouth during the lifting movement of the valve member 29 not through the Valve member 29 is closable.

The transition from the ring web 39 to the actuating magnet 37 Piston shaft takes place via a ring shoulder 53, the resulting one axially directed ring surface on the ring shoulder 53 a second flat Sealing surface 55 forms that with a surrounding a bore 57 Flat valve seat 59 on the axial end face of an intermediate piece 61 cooperates, the piston skirt through the bore 57 to Solenoid 37 continues and with its end in one Compression spring 35 of the valve member 29 receiving spring space 63 protrudes. The outer diameter of the bearing the flat axial sealing surface 55 Ring shoulder 53 on the ring web 39 is for a pressure equalization on open control valve 17 the same size as the diameter of the guide piston part 45.

The stroke movement of the valve member 29 is in each case by contact the sealing surfaces 41, 55 limited to one of the valve seats 43, 59. The ring web 39 is in one of the respective valve seats 43, 59 limited, an anteroom 65 forming an annular space from which a pressure line 67 to the injection valve 15 and a relief channel 69 lead away. This relief channel 69 is partially through a remaining annular gap between the piston skirt and the bore 57 formed in the intermediate piece 61, with its outer diameter formed smaller than the sealing surface 55 and so of this is lockable. The bore 57 opens into the as a return spring acting compression spring 35 of the valve member 29 receiving Spring chamber 63 and is, an axial through bore 71 in the valve member 29 intersecting transverse bores 73 with one of which Setting magnet 37 facing away from the end face of the guide piston 45 of the Valve member 29 connected relief space 75. This inside the relief bore 75 formed in the guide bore 49 axially in a direction away from the control magnet 37 in a spring chamber 77 of the injection valve 15, in which a valve member 79 of the injection valve 15 acting in the closing direction valve spring 81 is arranged and of which a return line 83 in discharges the low pressure chamber 5.

The valve member 79 of the injection valve 15 is known Way with a conical pressure shoulder 85, which in one with the pressure line 67 connected pressure chamber 87 protrudes such that the pressure in the pressure chamber 87 acts on the valve member 79 in the opening direction. An injection channel 89 also leads from the pressure chamber 87 along valve member 79 to one or more of the sealing surface at the tip of the valve member 79 controlled injection openings 91 of the injection valve 15 in the not shown Combustion chamber of the internal combustion engine to be supplied.

The fuel injection device according to the invention works in the following Wise.

The high-pressure fuel pump 1 delivers the fuel from the Low pressure chamber 5 in the high pressure collection chamber 9 and builds in this high fuel pressure, which is controlled by the high pressure pump 1 is adjustable. This high fuel pressure takes over the high pressure lines 13 into the pressure chamber 51 of the individual Control valves 17 on the injection valves 15 and fills also the respective pressure storage spaces 19 via the pressure valves 23.

In the idle state, that is, with the injector 15 closed Solenoid 37 on the control valve 17 is de-energized so that the Compression spring 35, the valve member 29 via the spring plate 33 with the conical Sealing surface 41 in contact with the conical valve seat 43 holds, so that the connection between the high fuel pressure Pressure chamber 51 and that constantly with the pressure line 67 to the injection valve 15 connected vestibule 65 closed and the connection from Anteroom 65 in the relief channel 69 is open.

If an injection is to take place at the injection valve 15, the Actuator 37 energizes and shifts the valve member 29 of the control valve 17 against the restoring force of the spring 35 to the system its flat valve sealing surface 55 to the flat valve seat 59 the connection of the anteroom 65 to the relief channel 69 is closed and opened to the pressure line 67, so that the High fuel pressure now from the pressure chamber 51 via the vestibule 65 and the Pressure line 67 continues to the pressure chamber 87 of the injection valve 15 and there about the lifting of the valve member 79 from its valve seat The injection takes place at the injection openings 91 in a known manner.

It can be in the pressure line 67 during the injection phase achieve a pressure increase above the system pressure in the following way. By moving the valve member 29, the pressure chamber 51 connected to the vestibule 65 and it sets a flow in the direction Cross bore 73 and through bore 71 up to the unpressurized Return line 83 a. This flow caused in Another consequence is a flow in the line connection from the pressure storage space 19 to the pressure chamber 51 and in line 13 between Pressure accumulator 19 and high pressure accumulator 9.

At the end of the opening stroke of the valve member 29 by contact the sealing surface 55 on the valve seat 59, the fuel flow in the direction Pressure line 67 directed. Due to the traffic jam effect in motion existing fuel flow there is a pressure increase. This pressure increase is due to a suitable choice of the influencing variables Line length, line diameter, storage volume, throttle cross-section etc. can be influenced.

In addition, due to the implementation of the flow energy Pressure increase of the injection pressure above the value of the system pressure achieve by the fuel pressure wave running to the injection valve 15 partly reflected at the injection valve, to the pressure accumulator 19 runs back and causes a pressure increase in this, which is caused by the flow energy of the high-pressure plenum 9 inflowing fuel and the dimensioning of the throttle 27, which prevents rapid pressure reduction, can be adjusted. This the increased fuel pressure then reaches the injection valve 15 again and increases its injection rate towards the end of the injection. Of the Injection course at the injection valve 15 can also be over the opening cross section on the valve member 29 (diameter / stroke), the volume of the vestibule 65 and the pressure line 67 and the volume of the Form the accumulator 19.

If the injection is to be ended, the actuating magnet 37 is activated again switched off and the compression spring 35 brings this even in the open Condition due to the ring shoulder 53 pressure-balanced valve member 29 of the control valve 17 again in contact with the conical valve seat 43. The opening cross section at the flat valve seat 59 is opened and the high pressure fuel relaxes via the relief channel 69, the spring chamber 63, the transverse and longitudinal bores 73, 71 in valve member 29 in the relief chamber 75, from where the fuel via the spring chamber 77 and the return line 83 flows into the low pressure chamber 5, so that the valve member 79 of the injection valve 15 is depressurized under Action of the valve spring 81 goes into the closed position and the valve member 29 is pressure balanced again. Here is the cross section of the relief channel 69 designed so that it has a rapid one hand Pressure drop in the pressure line 67 below the closing pressure of the Injector 15 ensures, but on the other hand, the outflow throttles from the pressure line 67 so that during the injection breaks a residual pressure remains in the pressure line 67 and the injection valve 15.

To influence the individual injection valves 15 with one another by the closed control valve 17 at the end of injection Avoiding a returning pressure wave is the volume of the pressure storage space 19 and the cross section of the throttle 27 in the return line serve pressure port 25 so that the Pressure peaks within the pressure storage space 19 and to the high-pressure collection space 9 are dismantled.

Claims (12)

  1. Fuel injection device for internal combustion engines, with a fuel high-pressure pump (1) which conveys fuel out of a low-pressure space (5) into a high-pressure collecting space (9) which is connected, via high-pressure conduits (13), to injection valves (15) which project into the combustion space of the internal combustion engine to be supplied and the opening and closing movement of which is controlled in each case by an electrically activated control valve (17) arranged in the high-pressure conduit (13) on the injection valve (15) and having a piston-shaped valve member (29), and with, on each injection valve (15), a further pressure accumulator space (19) which is integrated into the high-pressure conduit (13) between the high-pressure collecting space (9) and the injection valve (15), during the injection intermissions the control valve (17) on the injection valve (15) closing the connection of the further pressure accumulator space (19) to a pressure space (87) located within the injection valve (15) and acting on the valve member (79) of the injection valve (15) in the opening direction, the control valve (17) opening a connection of the pressure space (87) of the injection valve (15) to a relief space (75) during the injection intermissions of the injection valve (15), characterized in that the piston-shaped valve member (29) has an annular web (39), of which one surface of transition to the valve-member shank of smaller diameter forms a first valve sealing surface (41) cooperating with a valve seat (43) and of which the other transition to the valve-member shank of smaller diameter takes place via an annular shoulder (53) which has adjoining it, facing away from the annular web (39), a guide-piston part (45) spaced from the annular web (39) and of which the axial annular end surface facing away from the annular web (39) forms a second valve sealing surface (55) which co-operates with a valve seat (59) fixed relative to the housing.
  2. Fuel injection device according to Claim 1, characterized in that the stroke movement of the valve member (29) of the control valve (17) is limited in each case by the bearing of the valve sealing surfaces (41, 55) on one of the valve seats (43, 59).
  3. Fuel injection device according to Claim 1, characterized in that the outside diameter of the annular shoulder (53) carrying the flat valve sealing surface (55) is equal to the diameter of a guide piston (45) of the valve member (29) in a guide bore (49), the said guide piston adjoining an annular groove (47) located on the valve member (29) and emanating from the conical valve sealing surface (41), and the said guide piston, at the same time, delimiting a pressure space (51) formed between the wall of the guide bore (49) and the valve member (29) in the region of the annular groove (47).
  4. Fuel injection device according to Claim 3, characterized in that the annular web (39) is arranged in a pre-space (65) constantly connected to a pressure conduit (67) leading to the pressure space (87) of the injection valve (15).
  5. Fuel injection device according to Claim 4, characterized in that the pressure space (51) in the region of the annular groove (47) of the valve member (29) is constantly connected to a part of the high-pressure conduit (13) which leads away from the pressure accumulator space (19).
  6. Fuel injection device according to Claims 4 and 5, characterized in that the connection between the pre-space (65) and the pressure space (51) can be closed by the bearing of the conical sealing surface (41) of the valve member (29) on the conical valve seat (43).
  7. Fuel injection device according to Claim 4, characterized in that, by designing the valve-member shank adjoining the flat valve sealing surface (55) so as to have a smaller diameter than a bore (57) receiving the said shank, a relief duct (69) is formed which connects the pre-space (65) to the relief space (75) when the flat-seat valve is open.
  8. Fuel injection device according to Claim 7, characterized in that the piston-shaped valve member (29) of the control valve (17) has an axial passage bore (71) and, in the region of the relief duct (69), transverse bores (73) which lead radially away from the said passage bore and via which the fuel flowing away from the pressure conduit (67) and the pre-space (65) when the flat-seat valve is open passes from the relief duct (69) into the relief space (75).
  9. Fuel injection device according to Claim 1, characterized in that the control valve (17) is designed as a 3/2-way solenoid valve which is activated by means of an electric control unit (11).
  10. Fuel injection device according to Claim 1, characterized in that the accumulator volume of the pressure accumulator space (19) is about 5 to 20 times larger than the maximum injection quantity on the injection valve (15).
  11. Fuel injection device according to Claim 1, characterized in that the pressure accumulator space (19) is connected, via two parallel pressure connections, to that part of the high-pressure conduit (13) which leads to the high-pressure collecting space (9), of which pressure connections a first (21) has a pressure valve (23), preferably a non-return valve, opening in the direction of the pressure accumulator space (19) and a second (25) has a throttle point (27).
  12. Fuel injection device according to Claim 1, characterized in that the pressure accumulator space (19) is connected, via one pressure connection, to that part of the high-pressure conduit (13) which leads to the high-pressure collecting space (9), the said pressure connection having a pressure valve, preferably a non-return valve, opening in the direction of the pressure accumulator space (19) and a throttle point connected in series with the said valve.
EP19940113010 1993-12-07 1994-08-20 Fuel injection device for internal combustion engines Expired - Lifetime EP0657642B1 (en)

Priority Applications (2)

Application Number Priority Date Filing Date Title
DE19934341543 DE4341543A1 (en) 1993-12-07 1993-12-07 Fuel injection device for internal combustion engines
DE4341543 1993-12-07

Publications (3)

Publication Number Publication Date
EP0657642A2 EP0657642A2 (en) 1995-06-14
EP0657642A3 EP0657642A3 (en) 1995-12-06
EP0657642B1 true EP0657642B1 (en) 1999-01-13

Family

ID=6504295

Family Applications (1)

Application Number Title Priority Date Filing Date
EP19940113010 Expired - Lifetime EP0657642B1 (en) 1993-12-07 1994-08-20 Fuel injection device for internal combustion engines

Country Status (4)

Country Link
US (1) US5497750A (en)
EP (1) EP0657642B1 (en)
JP (1) JP3655938B2 (en)
DE (1) DE4341543A1 (en)

Families Citing this family (44)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US5669355A (en) * 1994-07-29 1997-09-23 Caterpillar Inc. Hydraulically-actuated fuel injector with direct control needle valve
US5687693A (en) 1994-07-29 1997-11-18 Caterpillar Inc. Hydraulically-actuated fuel injector with direct control needle valve
US5526791A (en) * 1995-06-07 1996-06-18 Diesel Technology Company High-pressure electromagnetic fuel injector
DE19701879A1 (en) 1997-01-21 1998-07-23 Bosch Gmbh Robert Fuel injection device for internal combustion engines
DE19712135C1 (en) 1997-03-22 1998-08-13 Mtu Friedrichshafen Gmbh Fuel injection system for internal combustion engine
DE19715234A1 (en) * 1997-04-12 1998-06-25 Daimler Benz Ag Valve for fuel injection system of internal combustion engine
DE19720913C1 (en) * 1997-05-16 1998-08-20 Mtu Friedrichshafen Gmbh Diesel engine fuel injection system with common controller reservoir
DE19732070C2 (en) * 1997-07-25 2001-02-01 Daimler Chrysler Ag Direct-injection fuel injector with solenoid valve control for a multi-cylinder internal combustion engine
DE19742073A1 (en) 1997-09-24 1999-03-25 Bosch Gmbh Robert Fuel injection arrangement for internal combustion engines
DE19748999C2 (en) * 1997-11-06 2002-11-07 Daimler Chrysler Ag Solenoid valve controlled injector for a storage system of a multi-cylinder internal combustion engine
DE19753072C2 (en) * 1997-11-29 1999-11-18 Bosch Gmbh Robert Fuel supply system for an internal combustion engine, in particular of a motor vehicle
US6026785A (en) * 1998-05-08 2000-02-22 Caterpillar Inc. Hydraulically-actuated fuel injector with hydraulically assisted closure of needle valve
US6364282B1 (en) 1998-12-04 2002-04-02 Caterpillar Inc. Hydraulically actuated fuel injector with seated pin actuator
DE19859175A1 (en) * 1998-12-21 2000-06-29 Siemens Ag Fuel supply system venting method for diesel engine common rail systems
DE19860678A1 (en) * 1998-12-29 2000-07-06 Bosch Gmbh Robert Fuel injection device for internal combustion engines
DE19910970A1 (en) * 1999-03-12 2000-09-28 Bosch Gmbh Robert Fuel injector
DE19919665A1 (en) * 1999-04-29 2000-11-02 Volkswagen Ag Fuel injector
DE19928906A1 (en) * 1999-06-24 2001-01-11 Bosch Gmbh Robert Common rail injector
DE19928846A1 (en) * 1999-06-24 2001-03-08 Bosch Gmbh Robert Common rail injector
DE19939428A1 (en) * 1999-08-20 2001-03-01 Bosch Gmbh Robert Method and device for performing a fuel injection
DE19942990A1 (en) 1999-09-09 2001-03-22 Bosch Gmbh Robert Common rail injector
DE19951554A1 (en) * 1999-10-26 2001-05-10 Bosch Gmbh Robert Fuel injector with integrated flow limitation
DE10032923A1 (en) * 2000-07-06 2002-01-24 Bosch Gmbh Robert Fuel injection device for internal combustion engines
DE10046829C2 (en) * 2000-09-20 2003-01-09 Orange Gmbh Control valve for injection injectors of internal combustion engines
DE10054991A1 (en) 2000-11-07 2002-05-29 Bosch Gmbh Robert Pressure controlled injector for injecting fuel with double valve
DE10055269B4 (en) * 2000-11-08 2005-10-27 Robert Bosch Gmbh Pressure-controlled injector with pressure boost
DE10055268A1 (en) 2000-11-08 2002-05-23 Bosch Gmbh Robert Pressure controlled injector of a high pressure accumulator injection system
DE10056165C2 (en) 2000-11-13 2003-06-12 Bosch Gmbh Robert Sammelraumbeaufschlagter injector with a cascade control arrangement
DE10059124B4 (en) 2000-11-29 2005-09-15 Robert Bosch Gmbh Pressure-controlled injector for injection systems with high-pressure collecting space
DE10059423A1 (en) 2000-11-30 2002-06-13 Bosch Gmbh Robert Device for conveying liquids, in particular fuel
DE10060811A1 (en) * 2000-12-07 2002-06-13 Bosch Gmbh Robert Fuel injection system for internal combustion engines
DE10060836C1 (en) * 2000-12-07 2002-07-25 Bosch Gmbh Robert Pressure-controlled CR injector with stepped opening and closing behavior
DE10105031A1 (en) * 2001-02-05 2002-08-14 Bosch Gmbh Robert Device for damping pressure pulsations in high-pressure injection systems
DE10114252C2 (en) * 2001-03-22 2003-01-30 Mtu Friedrichshafen Gmbh Method for injecting fuel into the combustion chambers of an internal combustion engine, and fuel injection system for such
DE10143423A1 (en) * 2001-09-05 2003-05-08 Bosch Gmbh Robert Fuel injection system with injector hydraulically decoupled from the supply line
DE10149868C1 (en) * 2001-10-10 2002-12-05 Orange Gmbh Fuel injector for diesel engine has fuel return line coupled to injection jet provided with high pressure region coupled to low pressure region via venting valve
DE10151955A1 (en) 2001-10-22 2003-05-08 Bosch Gmbh Robert Reduced-mass solenoid carrier
US7124746B2 (en) 2002-07-16 2006-10-24 Brocco Douglas S Method and apparatus for controlling a fuel injector
US7021565B2 (en) * 2004-02-10 2006-04-04 Caterpillar Inc. Pressure modulated common rail injector and system
EP1584815A1 (en) * 2004-04-05 2005-10-12 Tiby M. Martin Common rail fuel injector
CN101223352B (en) * 2005-07-18 2010-12-08 甘瑟-许德罗玛格股份公司 Accumulator injection system for an internal combustion engine
EP2188516B1 (en) * 2007-09-13 2011-10-26 Ganser-Hydromag AG Fuel injection device
US20110297125A1 (en) * 2010-06-03 2011-12-08 Caterpillar Inc. Reverse Flow Check Valve For Common Rail Fuel System
CH712276B1 (en) * 2016-03-18 2020-03-13 Ganser Hydromag Accumulator injection system for internal combustion engines.

Family Cites Families (11)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS51101628A (en) * 1975-01-24 1976-09-08 Diesel Kiki Co Denkishikikoatsufunshasochi
FR2449795B1 (en) * 1979-02-24 1986-11-28 Huber Motorenbau Inst Injection system for internal combustion engine
US4360163A (en) * 1981-01-19 1982-11-23 General Motors Corporation Electromagnetic diesel fuel injector
JPS5939963A (en) * 1982-08-27 1984-03-05 Nippon Denso Co Ltd Fuel injector
JPS6314186B2 (en) * 1982-08-31 1988-03-29 Yanmar Diesel Engine Co
USRE33270E (en) * 1982-09-16 1990-07-24 Bkm, Inc. Pressure-controlled fuel injection for internal combustion engines
JPH0525032B2 (en) * 1984-06-27 1993-04-09 Nippon Denso Co
DE3767260D1 (en) * 1986-09-25 1991-02-14 Ganser Hydromag Fuel injection valve.
JP2712760B2 (en) * 1990-05-29 1998-02-16 トヨタ自動車株式会社 Fuel injection valve
US5191867A (en) * 1991-10-11 1993-03-09 Caterpillar Inc. Hydraulically-actuated electronically-controlled unit injector fuel system having variable control of actuating fluid pressure
US5245970A (en) * 1992-09-04 1993-09-21 Navistar International Transportation Corp. Priming reservoir and volume compensation device for hydraulic unit injector fuel system

Also Published As

Publication number Publication date
DE4341543A1 (en) 1995-06-08
EP0657642A3 (en) 1995-12-06
JP3655938B2 (en) 2005-06-02
JPH07189849A (en) 1995-07-28
US5497750A (en) 1996-03-12
EP0657642A2 (en) 1995-06-14

Similar Documents

Publication Publication Date Title
EP1078160B1 (en) Fuel injection system
EP1485609B1 (en) Device for injecting fuel to stationary internal combustion engines
CA1228269A (en) Electromagnetic unit fuel injector
EP1520096B1 (en) Common rail injection system comprising a variable injector and booster device
EP1654456B1 (en) Fuel injection device for an internal combustion engine
JP3655938B2 (en) Fuel injection device for internal combustion engine
EP1612405B1 (en) An injection system for an internal-combustion engine
EP0925440B1 (en) Fuel injector
EP0931215B1 (en) Fuel injection device for internal combustion engines
US5456233A (en) Fuel injection arrangement for internal combustion engines
US7121264B2 (en) Adjustable pressure regulating valve for fuel injection systems
EP0779949B1 (en) Fuel injection device for internal combustion engines
EP0828936B1 (en) Injection valve
EP2050951B1 (en) Fuel injector
US6811103B2 (en) Directly controlled fuel injection device for a reciprocating internal combustion engine
DE69918902T2 (en) Fuel injector
DE60126380T2 (en) Fuel injection valve
EP0745184B1 (en) Process for reducing the fuel pressure in a fuel injection system
EP1125046B1 (en) Fuel injection system for an internal combustion engine with a pressure amplifier
JP3583784B2 (en) Hydraulic drive electronic fuel injection system
EP1780401B1 (en) Fuel injection device
US6076800A (en) Valve for controlling fluids
US6491017B1 (en) Combined stroke/pressure controlled fuel injection method and system for an internal combustion engine
EP0898650B1 (en) Fuel injection device for internal combustion engines
DE19519192C1 (en) Injector

Legal Events

Date Code Title Description
AK Designated contracting states:

Kind code of ref document: A2

Designated state(s): DE FR GB IT

AK Designated contracting states:

Kind code of ref document: A3

Designated state(s): DE FR GB IT

17P Request for examination filed

Effective date: 19960607

17Q First examination report

Effective date: 19971007

AK Designated contracting states:

Kind code of ref document: B1

Designated state(s): DE FR GB IT

REF Corresponds to:

Ref document number: 59407645

Country of ref document: DE

Date of ref document: 19990225

ET Fr: translation filed
ITF It: translation for a ep patent filed

Owner name: STUDIO JAUMANN P. & C. S.N.C.

GBT Gb: translation of ep patent filed (gb section 77(6)(a)/1977)

Effective date: 19990318

26N No opposition filed
REG Reference to a national code

Ref country code: GB

Ref legal event code: IF02

PGFP Postgrant: annual fees paid to national office

Ref country code: DE

Payment date: 20071024

Year of fee payment: 14

PGFP Postgrant: annual fees paid to national office

Ref country code: IT

Payment date: 20080826

Year of fee payment: 15

Ref country code: FR

Payment date: 20080818

Year of fee payment: 15

PGFP Postgrant: annual fees paid to national office

Ref country code: GB

Payment date: 20080822

Year of fee payment: 15

PG25 Lapsed in a contracting state announced via postgrant inform. from nat. office to epo

Ref country code: DE

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20090303

GBPC Gb: european patent ceased through non-payment of renewal fee

Effective date: 20090820

REG Reference to a national code

Ref country code: FR

Ref legal event code: ST

Effective date: 20100430

PG25 Lapsed in a contracting state announced via postgrant inform. from nat. office to epo

Ref country code: FR

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20090831

PG25 Lapsed in a contracting state announced via postgrant inform. from nat. office to epo

Ref country code: GB

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20090820

PG25 Lapsed in a contracting state announced via postgrant inform. from nat. office to epo

Ref country code: IT

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20090820