WO1995014857A1 - Kraftstoffeinspritzpumpe - Google Patents
Kraftstoffeinspritzpumpe Download PDFInfo
- Publication number
- WO1995014857A1 WO1995014857A1 PCT/DE1994/001369 DE9401369W WO9514857A1 WO 1995014857 A1 WO1995014857 A1 WO 1995014857A1 DE 9401369 W DE9401369 W DE 9401369W WO 9514857 A1 WO9514857 A1 WO 9514857A1
- Authority
- WO
- WIPO (PCT)
- Prior art keywords
- distributor
- fuel injection
- injection pump
- valve member
- pump according
- Prior art date
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
- F02M41/14—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 rotary distributor supporting pump 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
- 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
- F02M41/14—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 rotary distributor supporting pump pistons
- F02M41/1405—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 rotary distributor supporting pump pistons pistons being disposed radially with respect to rotation axis
- F02M41/1411—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 rotary distributor supporting pump pistons pistons being disposed radially with respect to rotation axis characterised by means for varying fuel delivery or injection timing
-
- 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
- F02M59/366—Valves being actuated electrically
Definitions
- the invention is based on a fuel injection pump of the distributor type according to the preamble of claim 1.
- Such a fuel injection pump is known from EP-A-0 524 132.
- the fuel injection pump there is a so-called radial piston pump, in which radially extending cylinder bores are provided in the rotatingly driven distributor, in which pump pistons are slidably arranged, which are attached to a fixed cam ring via roller tappets which connect the distributor in the region of the cylinder bores encloses on the circumference, support.
- the rotating driven distributor causes the expiry of the Roller tappet on the cam ring and thus a reciprocating movement of the pump pistons, which, on the other hand, enclose a pump working space due to their opposite end faces. This can be relieved to the relief chamber via the connecting channel and the valve controlled by the electromagnet.
- valve member of this valve is acted upon by a spring in the opening direction and can be moved in the closing direction by a plunger, the plunger being moved with an armature which is axially adjustable relative to the fixed poles of an electromagnet.
- an exact assignment of the electromagnet to the distributor is required.
- the axial position of the distributor is secured by a disk which engages in an annular groove.
- this type of attachment has the disadvantage that the axial fixation of the distributor is provided with a play which results from the tolerances of the components and an unimpeded rotational movement without additional play allowing the distributor to be clamped. Thermal expansion of the individual components with respect to one another must also be taken into account.
- this play means that the distance from the distributor or valve seat or valve member in its closed position to the magnet can be different at different operating points.
- This, in turn, is disadvantageous for the switching force applied by the solenoid valve and the switching speed and dynamics of the switching behavior of the magnet.
- the fuel injection pump according to the invention with the characterizing features of claim 1 has the advantage that the part of the core which forms the magnetic circuit of the electromagnet and which cooperates with the armature can be adjusted together with the distributor, with the result that the valve member is simultaneously the same adjusting anchor the working air gap between the anchor and this adjustable core remains the same size.
- the forces developed by the electromagnet for switching the valve and the dynamic switching behavior of this solenoid valve thus remain the same regardless of the dimensioning of the axial play of the distributor.
- the electromagnet is configured according to claim 2 in that the part of the core or magnetic pole of the electromagnet interacting with the armature is directly coupled to the end face of the distributor.
- such an electromagnet is designed as a plunger magnet according to claim 3.
- a preferred embodiment of the electromagnet in connection with the valve for controlling the connection between the pump work chamber and the relief chamber is the subject of patent claim 4. This results in a very high degree compact design with a secure and low leakage magnetic coupling of the individual core parts with each other and still achievable mobility of the one core part, which together with the armature forms the working air gap.
- the fact that the magnetic coupling of this core part to the side core takes place on the circumference is a relatively low magnetic flux density in the magnetic coupling area compared to the high magnetic flux density in the area of the working air gap between the armature that slides in the axial recess and the part of the second yoke that surrounds the central opening.
- the second yoke also serves as a system for a variable stop of the distributor by means of different spacer rings of different widths and at the same time for fixing a stop determining the opening stroke for the valve member according to claim 7 , which are designed to open inwards and also realize valves which are designed to open outwards.
- Opening outwards means that the outflowing fuel flow can flow out in the direction of the valve member moving outwards when opened.
- the outflowing fuel flows counter to the outward opening movement of the valve member into the interior of the axial bore and from there to a relief chamber.
- FIG. 1 shows the fuel injection pump according to the invention with an inward opening valve
- FIG. 2 shows the fuel injection pump according to the invention with an outward opening valve.
- FIG. 1 shows a section through part of a distributor injection pump in which the features essential to the invention are realized.
- a bushing 2 is inserted into a housing bore 3 in a housing 1 of the fuel injection pump, which in turn has a guide bore 5 in its interior, in which a distributor 7 is guided.
- This is driven in rotation via a coupling part 8 by a drive shaft of the distributor injection pump, not shown, and rotates synchronously with the speed of the associated internal combustion engine.
- the distributor At its end protruding from the socket on the drive side, the distributor has a collar 9 with which it runs against the end face 11 of a part of the socket 2 protruding into a suction chamber 12.
- the pump working space 15 is connected via a pressure channel 19, which runs inside the distributor, to a distributor groove 20 on the circumference of the distributor, which is initially designed as bores in the radial plane in which the distributor groove 20 is located, leading away from the guide bore 5
- Injection lines 21 can be connected, each of which leads to a fuel injection valve (not shown further here).
- a connecting channel 23 also leads from the distributor groove 20, which opens into a coaxial blind bore 24, graduated in diameter, in the region of an inner annular groove 25 made in this blind bore.
- This inner annular groove forms an annular shoulder 28 on its side facing away from the end face 26 on the other end of the distributor protruding from the bushing 2 and which carries a valve seat 29 facing the annular groove 25.
- the axial blind bore changes from a larger diameter to a smaller diameter, in which the annular shoulder 28 is initially followed by a first annular groove 30 and then interrupted by a web 31, a second annular groove 32.
- a second part 33 of the connecting channel 23 leads away and opens into a longitudinal groove in the lateral surface of the distributor 34, which in turn opens into an annular groove 35, which leads via a transverse bore 36 in the socket 2 and a further line 37 to a relief chamber, which in the present case is the suction chamber 12.
- a valve member 39 with a sealing fit is displaceably guided, which has an outer annular groove 40 in the area of the inner annular groove 25 of the axial bore, with which it merges with the inner annular groove 25 Annulus 41 forms. Furthermore, an annular shoulder 42 is formed by the outer annular groove on the valve member, the outer diameter of which projects beyond the annular shoulder 28 of the axial bore and has a sealing surface 43 facing the valve seat 29. Subsequently to the part of the axial bore at the passage in the area of the annular shoulder 28 which is smaller in diameter, the diameter of the valve member tapers and subsequently widens conically into a guide piston 45 which cooperates with the web 31. On the end face of the guide piston, a spring 46 engages, which is supported in the base 47 of the axial bore and acts on the valve member in such a way that it is inclined to lift off its annular shoulder 42 from the valve seat 29.
- the valve member 39 protrudes from the axial bore on the end face 26 of the distributor and, at this protruding end 49, has a neck 50 formed by a reduction in diameter, which subsequently merges into a head 51 on which a sleeve-shaped or as Perforated disc formed armature 52 is pressed or is firmly connected to the valve member.
- the armature can also be in one piece with the valve member.
- Both disks, the stop disk and the magnetic disk have an axial opening, the opening 56 in the stop disk 54 being smaller in diameter than the outer diameter of the part of the valve member 39 guided in the axial bore and a stop for the annular shoulder 57 forms at the transition of the valve member to the neck 50.
- the opening 58 in the magnetic disk 55 is, however, larger.
- the openings 56 and 58 both have the shape of a keyhole, such that the valve member with its largest diameter can be passed through the hole in the keyhole and then can be brought with its neck into its end position with respect to the stop disk and magnetic disk. Both discs are screwed onto the end face 26 of the distributor by means of common fastening screws 59.
- magnetic disk 55 and stop disk 54 only a single disk can be provided if both the magnetic and mechanical requirements are met.
- the stop disk and magnetic disk which protrude beyond the distributor diameter, rotate together with the distributor during operation of the fuel injection pump.
- the magnetic disk 55 represents part of a magnetic circuit or core of an electromagnet.
- the magnetic disk 55 is magnetically coupled on its circumferential end face via an air gap 64 to a sleeve-like side core 65 of the magnet 66.
- the circular cylindrical inner wall of the side core overlaps with the circular cylindrical contour of the magnetic disk 55, which thus forms a yoke.
- the sleeve-shaped side core 65 in turn merges via a first yoke 67 opposite this second yoke, the magnetic disk 55, into a sleeve-shaped main core 68 which has an axial, circular-cylindrical recess 69, into which the armature 52 slidably dips.
- the magnet coil 71 of the electromagnet is mounted in the annular space 70 formed between the sleeve-shaped side core and the main core 68 and has connections 72 and 73 leading through the first yoke 67.
- the coil is encapsulated and stands at a radial distance between the main core 68 and the side core 65.
- the annular space 70 is in this case via at least one transverse channel 75 in the wall of the main core and transverse channel 76 in the wall of the side core, both with the recess 69 and with one of the side core surrounding annular space 77, which is not shown here, is connected to the relief space 12, the suction space.
- the recess 69 is closed from the side of the first yoke 67 by a closure part 78, so that an interior closed by the armature 52 is formed in the recess 69, which, as mentioned, can be connected to the relief space via the transverse channels 75 and 76 is such that the armature can move freely in the main core and at the same time the solenoid with fuel is washed around, promoted by the pumping back and forth movement of the anchor during its work cycles.
- the magnetic core of the electromagnet thus consists of a fixed magnetic core with the main core that is hollow in plunger armature magnets, the first yoke 67 and the side yoke 65 and, in the particular embodiment according to the invention, now has a movable part, the second yoke in the form of the magnetic disk 55 which cooperates with the armature 52.
- the working air gap 80 is formed between the end face of the armature facing the end face of the distributor or the end face of the magnetic disk 55 and the magnetic disk, while the armature is magnetically coupled to the main core via a coupling air gap 81.
- the pump working chamber 15 When the internal combustion engine is operating, the pump working chamber 15 is filled with fuel via the pressure channel 19, the connecting channel 23 and, when the valve member 39 is open, via the second part 33 of the connecting channel and the transverse bore or the line 37, by the pump pistons 14 during the suction cycle following the cam track 18 are moved outwards so that the volume of the pump work space 15 increases with the absorption of fuel.
- the volume of the pump working space is reduced and the fuel is returned in the same way as long as the valve member is lifted off the valve seat 29.
- the valve member At the beginning of the high pressure generation, the valve member is brought into the closed position by the electromagnet so that it sits on the seat 29 with its sealing surface 43.
- the configuration according to the invention has the advantage that the axial securing of the distributor can be subject to play, which is also necessary for technical reasons or cannot be avoided. Nevertheless, the working air gap 80 does not change as a result of this play.
- the magnetic disk is always at a fixed distance from the seat 29 in the distributor and the armature 52 is also at a fixed distance from the seat 29 in the distributor when the valve member is seated on the seat 29.
- the working air gap 80 thus remains constant regardless of the position of the distributor.
- the armature plate 55 moves, which rotates together with the distributor within the inner diameter of the sleeve-shaped side core 65, but remains there magnetically coupled to the side core via the air gap 64.
- the shift does not result in any changes affecting the armature movement.
- a change in the immersion depth of the armature in the main core 68 due to the displacement of the distributor has no influence on the actuating force of the magnet and its dynamics.
- the scattering losses in the circumference of the magnetic disk 55, which arise due to the local air gap 64, are comparatively small, since the magnetic flux is distributed over a large passage area. which is very large in relation to the area in the area of the working air gap, so that there is a low magnetic flux density there.
- these magnetic losses can be considered with little effort when designing the magnet. It is essential that a constant actuating force of the magnet is maintained during operation and that no variations in the actuating dynamics occur.
- the armature is fixedly attached to the valve member, so that there is no mechanical wear due to striking parts, as is the case with other conventional designs for actuating a valve member.
- the one-piece design of the armature and valve member is also more manageable than a two-part design in which the valve member is actuated by a tappet which is placed on the valve member.
- the setting of the residual air gap in the working gap 80 can be solved in a simple manner, since a simple assignment of the pressed-on armature part 52 and magnetic disk with a flat surface is possible.
- valve member is configured somewhat differently and is designed as an outward opening valve.
- the only difference is the channel routing of the connecting channel and the design of the axial bore in which the valve member is received.
- the axial bore 124 is made with approximately the same diameter throughout.
- the valve member 139 again has an outer annular groove 140 which, together with the blind bore 124, forms an annular space 141.
- annular space is delimited on the side of the valve member facing away from the end face 126 of the distributor 107 by a guide piston 145, which is guided by the Rest of the blind bore according to Figure 1 arranged spring 46 acted on in the direction of movement of the valve member to the outside.
- the other side of the annulus is now covered by an annular shoulder
- the axial blind bore 124 merges into a recess 81 with a larger diameter and has a valve seat 129 at the transition to this recess 81. This works together with a sealing surface provided on the annular shoulder 142
- valve member In the intermediate region between the annular shoulder 142 and the guide piston 145, the valve member also has guide webs 82 which are supported on the wall of the axial bore 124 and which are formed from a collar which is provided with flats 83 for the passage of the fuel from the connecting channel 23 to the valve seat
- valve member 139 Adjacent to the ring shoulder 142, the valve member 139 in turn has the ring shoulder 57, with which its opening stroke is limited in contact with the stop disc 54.
- the valve member and the fuel injection pump with magnets 166 are then configured in the same way as in the previous exemplary embodiment.
- a connecting channel 85 extends transversely from the recess 81 to a relief space, into which a relief line 86 of the space 87 enclosed by the guide piston 145 also opens.
- the exemplary embodiment according to FIG. 2 works in the same way as the exemplary embodiment according to FIG. 1, except that there are different conditions in terms of flow and impulses, which bring advantages in one form or the other depending on the application.
- a securing ring 89 is inserted on the outer circumference of the distributor, between which and an end face 160 of the bushing 102 in turn spacers 61 and 62 are inserted.
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
Description
Claims
Priority Applications (4)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
DE59409881T DE59409881D1 (de) | 1993-11-24 | 1994-11-22 | Kraftstoffeinspritzpumpe |
ES95900649T ES2164754T3 (es) | 1993-11-24 | 1994-11-22 | Bomba de inyeccion de combustible. |
EP95900649A EP0708885B1 (de) | 1993-11-24 | 1994-11-22 | Kraftstoffeinspritzpumpe |
JP51474495A JP3442391B2 (ja) | 1993-11-24 | 1994-11-22 | 燃料噴射ポンプ |
Applications Claiming Priority (2)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
DE4339948A DE4339948A1 (de) | 1993-11-24 | 1993-11-24 | Kraftstoffeinspritzpumpe |
DEP4339948.7 | 1993-11-24 |
Publications (1)
Publication Number | Publication Date |
---|---|
WO1995014857A1 true WO1995014857A1 (de) | 1995-06-01 |
Family
ID=6503265
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
PCT/DE1994/001369 WO1995014857A1 (de) | 1993-11-24 | 1994-11-22 | Kraftstoffeinspritzpumpe |
Country Status (8)
Country | Link |
---|---|
US (1) | US5582153A (de) |
EP (1) | EP0708885B1 (de) |
JP (1) | JP3442391B2 (de) |
KR (1) | KR100373806B1 (de) |
CN (1) | CN1042968C (de) |
DE (2) | DE4339948A1 (de) |
ES (1) | ES2164754T3 (de) |
WO (1) | WO1995014857A1 (de) |
Cited By (1)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
WO2002042634A1 (de) * | 2000-11-23 | 2002-05-30 | Robert Bosch Gmbh | Magnetventilgesteuerte kraftstoffeinspritzpumpe für brennkraftmaschinen, insbesondere dieselmotoren |
Families Citing this family (16)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
DE4323683A1 (de) * | 1993-07-15 | 1995-01-19 | Bosch Gmbh Robert | Kraftstoffeinspritzpumpe |
DE19542952A1 (de) * | 1995-11-18 | 1997-05-22 | Bosch Gmbh Robert | Kraftstoffeinspritzpumpe für Brennkraftmaschinen |
DE19616084A1 (de) * | 1996-04-23 | 1997-10-30 | Bosch Gmbh Robert | Kraftstoffeinspritzvorrichtung |
DE19714812A1 (de) * | 1997-04-10 | 1998-10-15 | Bosch Gmbh Robert | Magnetspule |
EP0971375B1 (de) * | 1998-07-09 | 2003-05-07 | NOK Corporation | Solenoidantriebsvorrichtung |
JP3633388B2 (ja) * | 1999-08-04 | 2005-03-30 | トヨタ自動車株式会社 | 内燃機関の高圧燃料ポンプ制御装置 |
US6415769B1 (en) | 2000-04-24 | 2002-07-09 | Blue Chip Diesel Performance | Performance enhancing system for electronically controlled engines |
US6773240B2 (en) | 2002-01-28 | 2004-08-10 | Visteon Global Technologies, Inc. | Single piston dual chamber fuel pump |
US6807943B2 (en) | 2002-08-05 | 2004-10-26 | Husco International, Inc. | Motor vehicle fuel injection system with a high flow control valve |
US6793196B2 (en) | 2002-08-05 | 2004-09-21 | Husco International, Inc. | High flow control valve for motor vehicle fuel injection systems |
US6976640B2 (en) * | 2003-12-04 | 2005-12-20 | Kuo-Liang Chen | Air gun with a quick-releasing device |
EP1707797B1 (de) * | 2005-03-14 | 2007-08-22 | C.R.F. Società Consortile per Azioni | Verstellbares Dosierservoventil eines Einspritzventils |
WO2007129277A2 (en) * | 2006-05-10 | 2007-11-15 | Koninklijke Philips Electronics N. V. | A magnetic system |
US7900886B2 (en) * | 2008-04-18 | 2011-03-08 | Caterpillar Inc. | Valve assembly having a washer |
US8083206B2 (en) * | 2008-07-08 | 2011-12-27 | Caterpillar Inc. | Precision ground armature assembly for solenoid actuator and fuel injector using same |
JP4958023B2 (ja) * | 2010-01-18 | 2012-06-20 | 株式会社デンソー | 高圧ポンプ |
Citations (3)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JPS62276264A (ja) * | 1986-05-23 | 1987-12-01 | Nippon Denso Co Ltd | 燃料噴射ポンプの溢流用電磁弁及び噴射量調節方法 |
EP0524132A2 (de) * | 1991-07-16 | 1993-01-20 | Stanadyne Automotive Corp. | Brennstoffsystem für eine Rotationsverteilerbrennstoffeinspritzpumpe |
US5228844A (en) * | 1992-10-14 | 1993-07-20 | Stanadyne Automotive Corp. | Rotary distributor type fuel injection pump |
Family Cites Families (8)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
DE3412834A1 (de) * | 1984-04-05 | 1985-10-24 | Robert Bosch Gmbh, 7000 Stuttgart | Kraftstoffeinspritzpumpe |
DE3910793C2 (de) * | 1989-04-04 | 1996-05-23 | Kloeckner Humboldt Deutz Ag | Brennstoffeinspritzvorrichtung |
JPH02276264A (ja) * | 1989-04-18 | 1990-11-13 | Nec Corp | ヒートシンク付セラミックパッケージ |
US5215449A (en) * | 1991-12-05 | 1993-06-01 | Stanadyne Automotive Corp. | Distributor type fuel injection pump |
JPH0742644A (ja) * | 1992-10-29 | 1995-02-10 | Nippon Soken Inc | 電磁弁 |
US5265576A (en) * | 1993-01-08 | 1993-11-30 | Stanadyne Automotive Corp. | Calibration system for electrically controlled fuel injection pump |
US5345916A (en) * | 1993-02-25 | 1994-09-13 | General Motors Corporation | Controlled fuel injection rate for optimizing diesel engine operation |
US5425341A (en) * | 1994-07-15 | 1995-06-20 | General Motors Corporation | Fuel injection with pulse rate shaping cam |
-
1993
- 1993-11-24 DE DE4339948A patent/DE4339948A1/de not_active Withdrawn
-
1994
- 1994-11-22 DE DE59409881T patent/DE59409881D1/de not_active Expired - Lifetime
- 1994-11-22 EP EP95900649A patent/EP0708885B1/de not_active Expired - Lifetime
- 1994-11-22 KR KR1019950703032A patent/KR100373806B1/ko not_active IP Right Cessation
- 1994-11-22 CN CN94190997A patent/CN1042968C/zh not_active Expired - Fee Related
- 1994-11-22 ES ES95900649T patent/ES2164754T3/es not_active Expired - Lifetime
- 1994-11-22 WO PCT/DE1994/001369 patent/WO1995014857A1/de active IP Right Grant
- 1994-11-22 JP JP51474495A patent/JP3442391B2/ja not_active Expired - Lifetime
-
1995
- 1995-06-16 US US08/454,357 patent/US5582153A/en not_active Expired - Fee Related
Patent Citations (3)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JPS62276264A (ja) * | 1986-05-23 | 1987-12-01 | Nippon Denso Co Ltd | 燃料噴射ポンプの溢流用電磁弁及び噴射量調節方法 |
EP0524132A2 (de) * | 1991-07-16 | 1993-01-20 | Stanadyne Automotive Corp. | Brennstoffsystem für eine Rotationsverteilerbrennstoffeinspritzpumpe |
US5228844A (en) * | 1992-10-14 | 1993-07-20 | Stanadyne Automotive Corp. | Rotary distributor type fuel injection pump |
Non-Patent Citations (1)
Title |
---|
PATENT ABSTRACTS OF JAPAN vol. 12, no. 157 (M - 696) 13 May 1988 (1988-05-13) * |
Cited By (2)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
WO2002042634A1 (de) * | 2000-11-23 | 2002-05-30 | Robert Bosch Gmbh | Magnetventilgesteuerte kraftstoffeinspritzpumpe für brennkraftmaschinen, insbesondere dieselmotoren |
US6884041B2 (en) | 2000-11-23 | 2005-04-26 | Robert Bosch Gmbh | Electromagnetic valve-controlled fuel injection pump for internal combustion engines, especially diesel engines |
Also Published As
Publication number | Publication date |
---|---|
JP3442391B2 (ja) | 2003-09-02 |
EP0708885B1 (de) | 2001-09-26 |
US5582153A (en) | 1996-12-10 |
ES2164754T3 (es) | 2002-03-01 |
KR960700406A (ko) | 1996-01-20 |
EP0708885A1 (de) | 1996-05-01 |
CN1116869A (zh) | 1996-02-14 |
CN1042968C (zh) | 1999-04-14 |
DE4339948A1 (de) | 1995-06-01 |
KR100373806B1 (ko) | 2003-05-09 |
DE59409881D1 (de) | 2001-10-31 |
JPH08510816A (ja) | 1996-11-12 |
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