EP0906506A1 - Pompe d'injection de carburant pour moteur a combustion interne - Google Patents

Pompe d'injection de carburant pour moteur a combustion interne

Info

Publication number
EP0906506A1
EP0906506A1 EP98907857A EP98907857A EP0906506A1 EP 0906506 A1 EP0906506 A1 EP 0906506A1 EP 98907857 A EP98907857 A EP 98907857A EP 98907857 A EP98907857 A EP 98907857A EP 0906506 A1 EP0906506 A1 EP 0906506A1
Authority
EP
European Patent Office
Prior art keywords
pressure
groove
distributor
fuel injection
injection pump
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Granted
Application number
EP98907857A
Other languages
German (de)
English (en)
Other versions
EP0906506B1 (fr
Inventor
Karl-Friedrich Ruesseler
Bernhard Bonse
Wolfgang Braun
Dieter Junger
Joachim Kurz
Roland Gronenberg
Hubert Greif
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
Application filed by Robert Bosch GmbH filed Critical Robert Bosch GmbH
Publication of EP0906506A1 publication Critical patent/EP0906506A1/fr
Application granted granted Critical
Publication of EP0906506B1 publication Critical patent/EP0906506B1/fr
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

Links

Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M41/00—Fuel-injection apparatus with two or more injectors fed from a common pressure-source sequentially by means of a distributor
    • F02M41/08—Fuel-injection apparatus with two or more injectors fed from a common pressure-source sequentially by means of a distributor the distributor and pumping elements being combined
    • F02M41/10—Fuel-injection apparatus with two or more injectors fed from a common pressure-source sequentially by means of a distributor the distributor and pumping elements being combined pump pistons acting as the distributor
    • F02M41/12—Fuel-injection apparatus with two or more injectors fed from a common pressure-source sequentially by means of a distributor the distributor and pumping elements being combined pump pistons acting as the distributor the pistons rotating to act as the distributor
    • F02M41/123—Fuel-injection apparatus with two or more injectors fed from a common pressure-source sequentially by means of a distributor the distributor and pumping elements being combined pump pistons acting as the distributor the pistons rotating to act as the distributor characterised by means for varying fuel delivery or injection timing
    • F02M41/125—Variably-timed valves controlling fuel passages
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M41/00—Fuel-injection apparatus with two or more injectors fed from a common pressure-source sequentially by means of a distributor
    • F02M41/08—Fuel-injection apparatus with two or more injectors fed from a common pressure-source sequentially by means of a distributor the distributor and pumping elements being combined
    • F02M41/10—Fuel-injection apparatus with two or more injectors fed from a common pressure-source sequentially by means of a distributor the distributor and pumping elements being combined pump pistons acting as the distributor
    • F02M41/12—Fuel-injection apparatus with two or more injectors fed from a common pressure-source sequentially by means of a distributor the distributor and pumping elements being combined pump pistons acting as the distributor the pistons rotating to act as the distributor

Definitions

  • the invention relates to a fuel injection pump for internal combustion engines according to the preamble of claim 1.
  • a fuel injection pump of this type which has a pump piston which is driven back and forth in a housing bore and at the same time also rotates.
  • the outlet opening on the pump piston serves as a distributor opening, through which various pressure lines are successively supplied with high-pressure fuel.
  • a longitudinal groove is arranged approximately opposite the distributor opening in the lateral surface of the pump piston, which is in constant communication with the fuel supplied to the distributor opening under high pressure.
  • This configuration has the disadvantage that despite a force equalization that is achieved on the pump piston, the large-area grooves in the lateral surface of the moving part cause an interruption of a lubricating oil film, which lubricating oil film is the moving part, the pump piston and distributor at the same time Rotation in the housing bore.
  • the fuel injection pump according to the invention with the features of the characterizing part of patent claim 1 has the advantage over the fact that a compensation force which is independent of the rotational position of the moving part is generated by the pressure compensation surface according to the invention, since the pressure compensation surface remains constantly closed.
  • the pressure which arises in the area of the pressure compensation area and which is derived from the outlet pressure of the high-pressure source at the adjacent outlet opening can be set as desired by dimensioning the first and the second leakage path.
  • This configuration also has the advantage that, in the event of high pressure occurring in the area of the outlet opening, the size of the leakage sections, in particular their effective flow cross section, is influenced as a result of the intermittent high-pressure fuel injection due to the deformation of the moving part and the housing bore that an outflow cross section over the second leak section is reduced and an inflow cross section over the first leak section is enlarged.
  • the pressure in the area of the pressure equalization surface rises disproportionately with increasing high pressure. This tends to increase faster- de Pressure creates a correspondingly higher compensation force against the force that arises there in the area of the outlet opening when the high pressure rises.
  • the lateral force resulting from the sum of the forces therefore only increases slowly as the pressure level of the high-pressure source increases.
  • the compensating force reduces the deformation on the moving part and the housing bore that receives it.
  • These deformations are flattened portions of the circular cross section in the direction of an elliptical cross section in the moving part and bore widenings in the housing bore likewise with an elliptical cross section, the main axes of the respective cross sections being perpendicular to one another.
  • there are also fewer transverse contractions or transverse extensions transverse to the triggering deformation so that a smaller clearance between the moving part and the housing bore can be achieved in the basic dimensioning of these parts with respect to one another.
  • the second leakage path is substantially twice as long as the first leakage distance, which results in a favorable quantity balance of the high pressure fuel flowing in from the pressure compensation surface and fuel flowing out again from this pressure compensation surface to a relief space.
  • the pressure that arises in the area of the pressure compensation area can be set with the length of the leakage distances and the cross sections that arise.
  • the solution according to the invention is implemented in a distributor injection pump according to claim 3.
  • the pressure compensation surfaces are advantageously designed according to claim 4 as a longitudinal groove or a flattening or bevel surface extending in a longitudinal direction to the axis of the rotatingly moving part.
  • the length of this longitudinal groove advantageously allows the pressure field in the area of the pressure compensation area to be determined, and it is necessary to accommodate such a pressure compensation area in a manner which facilitates production and implementation between otherwise existing high-pressure-carrying grooves or pressure relief grooves in the area of the lateral surface of the moving part.
  • a further groove is provided according to claim 5, which mainly serves to set the desired gap length in areas of the lateral surface that are favorable for this setting.
  • the pressure compensation area can be relatively isolated from the high-pressure outlet opening and can still reach a desired proximity to this outlet opening via the further groove or groove-like flattening, in order to define the first leak path there.
  • a leak path length to a relief side can also be set accordingly via this continued groove.
  • the partial extension of the pressure compensation surface according to claim 5 is carried out essentially parallel to a radial plane to the axis of the moving part, which enables the pressure compensation surface if possible to accommodate in the peripheral area of the lateral surface, in which the outlet opening is also provided, taking into account that during the reciprocating movement of the pump piston, the pressure compensation grooves do not reach the area of relief openings coming from the housing bore.
  • the distributor opening is designed as a longitudinal groove, wherein the further groove, which leads away from the pressure compensation surface, is designed as a partial ring groove, which ends in the axial direction below or above the longitudinal distributor groove and defines the first leakage path there.
  • the second leakage path is formed by the pressure compensation surface and a channel, which also extends in the circumferential direction and is connected to a relief chamber of the fuel injection pump.
  • a plurality of pressure compensation surfaces are advantageously provided according to patent claims 11 and 12, wherein according to patent claim 13 the surface of the pressure compensation surface is advantageously larger than the surface of the outlet opening which is directly acted upon by the high pressure of the high-pressure fuel source.
  • FIG. 1 shows a fuel injection pump in section and shown in simplified form
  • FIG. 2 shows a distributor piston, in the view as used in the pump according to FIG. 1
  • FIG. 3 shows a section along line III - III through the distributor piston according to FIG. 2 4
  • FIG. 2 shows a development of the distributor piston according to FIG. 2 together with the associated inner wall of the housing bore with a representation of the pressure lines discharging from it in a first embodiment
  • FIG 5 shows a section through the pump piston along the line V - V from FIG this receiving housing part with housing bore
  • Figure 6 shows a second embodiment of the invention based on a development of the pump piston
  • Figure 7 shows a third embodiment of the invention, shown on a development of the pump piston
  • Figure 8 shows a fourth embodiment of the invention with an additional annular groove.
  • a fuel distributor injection pump of the reciprocating piston type Provided in a housing 1 of such a distributor injection pump is a cylinder sleeve 4 pressed into a pump head 3, in the axial bore 5 of which a distributor pump piston 6 is guided, which is set into a reciprocating and a rotating movement by a cam drive (not shown further).
  • the distributor pump piston changes a pump working space 8, which is enclosed by it in the cylinder sleeve 4 on the end face, in such a way that this space is increased during the downward stroke of the pump piston, which is also a suction stroke, and is reduced in accordance with a delivery stroke during the upward stroke of the pump piston with the delivery of fuel brought to high pressure from this pump work chamber 8.
  • the distributor pump piston has one of its
  • This distributor opening is preferably designed as a longitudinal groove.
  • the distributor opening in each case during the delivery stroke of the pump piston comes into connection with one of a plurality of pressure lines 14, each of which leads as an injection line to a fuel injection valve 15 and which is distributed along the circumference of the inner circumferential surface in accordance with the fuel injection valves to be supplied the axial bore 5 are arranged.
  • a delivery valve 17 is preferably provided in each pressure line, for example as a constant pressure valve or as a valve with a valve member which has a continuously open throttle connection between the fuel injection valve and the fuel injection pump.
  • a filling groove 18 is provided in the lateral surface 11 of the pump piston 6, which is connected via a longitudinal channel 19 in the distributor pump piston 6 to an annular groove 20 in the lateral surface of the distributor pump piston.
  • This annular groove is connected to a relief bore 22 in the cylinder sleeve, which opens into a pump suction chamber 24 of the fuel injection pump, which is supplied by a feed pump 25 sucking from a fuel tank 27, possibly with the interposition of a further pre-feed pump.
  • a pressure control valve 26 which is arranged parallel to the feed pump 25, the pressure in the pump suction chamber is set.
  • the part of the fuel not participating in the fuel injection is controlled with the aid of a solenoid valve 29, the valve member 30 of which creates a connecting bore 31 between the pump work chamber 8 and a suction channel 32 leading to the pump suction chamber 24 when it is lifted off the valve seat of the solenoid valve.
  • This connection serves on the one hand to fill the pump work space during the suction stroke of the pump piston and on the other hand, as already mentioned, to discharge the pump workspace over a certain, defined stroke of the pump piston. This can lie before the actual delivery-effective pump piston stroke to determine the start of fuel injection and also after the injection of a desired fuel injection quantity to determine the end of high-pressure injection.
  • the solenoid valve is controlled electrically by a control device 34.
  • FIG. 1 shows the known design of the distributor injection pump with a solenoid valve for controlling the injection quantity.
  • FIG. 2 shows the known design of the distributor injection pump with a solenoid valve for controlling the injection quantity.
  • FIG. 2 shows the distributor groove 12, the filling groove 18 and a pressure compensation surface 36 can be seen.
  • the distributor opening 12 and the filling groove are designed as longitudinal grooves.
  • the pressure compensation surface 36 is also designed like a longitudinal groove, for example in the form of a bevel.
  • This pressure compensation surface which lies approximately diametrically opposite the distributor groove 12, is connected to a partial annular groove 37 which extends to below the distributor groove 12.
  • the assignments of pressure compensation surface 36, distributor groove 12 and filling groove 18 are shown more clearly and the partial ring groove 37 can also be seen in broken lines.
  • the pressure compensation surface 36 can equally well be designed as a flattening produced in some other way.
  • the partial ring groove can also be designed as a ground joint. When it approaches the distributor opening 12, it delimits a first leakage distance 39 at a vertical distance from it.
  • the pressure compensation surface 36 which lies at a safe distance, which is greater than the length of the leakage path, below the radial plane determined by the lowest boundary of the pressure line 14 facing away from the pump work space. From this pressure-equalizing surface 36, which is designed as a bevel or flattened area, the part-ring groove 37 leads from its uppermost boundary on the side of the pump work space parallel to a radial plane of the distributor piston 6.
  • the part-ring groove ends in such a way that the part-ring groove and distributor opening 12 overlap in the axial direction , the first leakage path 39 being formed between the partial annular groove 37 and the lowermost boundary edge 40 of the distributor opening via the gap existing between the outer surface of the distributor pump piston and the outer surface of the axial bore 5.
  • the second leakage path 42 is formed by the vertical distance between the lower boundary edge 43 facing away from the pump working space 8 and the annular groove 20.
  • the filling groove 18 is also entered, which is in the intermediate area between the distributor opening 12 and the
  • Pressure compensation surface 36 is. Seen in the circumferential direction, this largely overlaps the distributor opening 12 in such a way that when the distributor pump piston 6 rotates, it can also come into connection with the individual orifices of the pressure lines 14.
  • the print Line 44 enclosing the same flat line 36 is a line of a currently identical high pressure, which prevails in the area between the lateral surface of the distributor pump piston 6 and the housing bore during the delivery stroke of the pump piston. It can be seen that in the case of high-pressure delivery, the vicinity of the distributor groove is still acted upon by the high pressure as far as into the gap between the lateral surface 11 and the housing bore.
  • this high pressure is reduced in the area of the filling groove 18 connected to the suction space 24 and also in the area of the orifices of the pressure lines 14 which are not involved in the high-pressure injection.
  • the pressure compensation area 36 can also be adjusted via the distance between the closest boundary edge Filling groove 18 or to one of the pressure lines 14, which have in the meantime been relieved of pressure
  • Leakage path as a second leakage path 42 a or 42 b can be formed as an alternative or in addition.
  • the distributor opening is acted upon intermittently by the high pressure from the pump work space.
  • the distributor opening is connected to one of the orifices 14 of the pressure lines for delivery to the fuel injection valve 15.
  • the distributor pump piston 6 and the cylinder sleeve 4 are acted upon strongly by the high pressure present at the distributor groove 12. This state is shown exaggerated in the section according to FIG. 5, the section through the filling groove 18 being avoided for better illustration. 5 shows the distributor groove 12 and the flattening of the pressure compensation surface 36 as well as the dashed line of the partial annular groove 37 which opens into the pressure compensation surface 36 and begins below the distributor groove 12, but is not touched by the latter.
  • the cross-section of a possible leakage path here in particular the cross-section of the second leakage path 42, is also considerably reduced, which has the consequence that a relatively large amount of fuel under high pressure enters the partial ring groove over the first leakage path in the region of the increased distance 47 37 can drain and reaches the pressure compensation surface 36.
  • the second leakage path 42 Because of the missing or reduced outflow there via the second leakage path 42, there is a significant pressure increase there, which is higher than would be the case with a completely identical geometric game in the size of the normal game. This pressure increase causes a high counterforce on the distributor pump piston, which counteracts the resulting force from the pressurization in the region of the distributor opening 12.
  • the compensation forces that are generated by the pressure compensation surface dynamically adapt to the respective pressure level.
  • the normal play between the distributor pump piston and the axial bore 5 receiving it can be kept smaller than without the force compensation according to the invention. This results in less leakage loss during the entire operation of the distributor injection pump and thus a higher efficiency of the pump and the possibility of also generating higher injection pressures.
  • the distribution of forces ensures that with this gap, which can be reduced in this way, an excessive contact of the surfaces of the parts moving with respect to one another is avoided and the risk of seizure is controlled.
  • the arrangement according to the invention means that the pressure equal to the first leakage path to the distributor groove 12 and the second leakage path 42 to the annular groove 20, a quite high surface area is available, which carries the distributor pump piston 6 within the axial bore 5 and which additionally loses the leakage losses over this great length between the end face 9 and the annular groove 20 Keeps the low pressure side small.
  • This and the dynamic pressure equalization which adapts to the pressure curve in the pump work space, lead to a safe construction with low leakage loss and high operational safety.
  • FIG. 6 shows an alternative embodiment to FIG. 4 of the pump piston, again in the form of an outer surface development.
  • Deviations from the exemplary embodiment according to FIG. 4 are provided here instead of two pressure compensation surfaces 36a and 36b, which are now symmetrical to the filling groove 18, which in turn lies diametrically opposite the distributor groove 12.
  • These two pressure compensation surfaces 36a and 36b are in turn connected to one another by a partial annular groove 37 'in such a way that this partial annular groove describes almost 360 °, with the exception of the area into which the filling groove 18, viewed in the circumferential direction, overlaps with the pressure equalizing surfaces 36a and 36b .
  • the first leakage path 39 is in turn formed by the vertical distance between the partial annular groove 37 and the lower edge 40 of the distributor groove 12 and the second leakage distance in turn between the lower boundary edge 43 of the pressure compensation surface 36a or 36b and the annular groove 20.
  • the pressure compensation surfaces are preferably 120 ° each rotated to the distributor groove 12. In addition to this position of the second leakage path, it would also be possible to form a leakage path between the pressure compensation surfaces 36a or 36b and the filling groove 18.
  • FIG. 7 shows a third exemplary embodiment, which in turn is based on the exemplary embodiment according to FIG. 4 leans on.
  • a pressure field delimitation surface 136b is provided, which are now continuously connected to one another by an annular channel 137.
  • the second leakage path 42 is in turn formed between the lower boundary 43 of the one pressure compensation surface 136a and the annular groove 20.
  • the first leakage path 139 now lies between the upper boundary edge of the pressure field boundary surface 136b and the lower boundary edge 40 of the distributor opening 12.
  • the pressure field boundary surface 136b is aligned with the distributor opening 12, ie the common center line forms a surface line of the outer surface 11 of the distributor pump piston.
  • a compensation force is generated by the pressure compensation surface 136a, while the pressure field limitation surface 136b serves primarily to supply the compensation pressure, but also to limit the distributor groove pressure field and thus the lateral force.
  • FIG. 8 shows a fourth exemplary embodiment, which in turn is based on the exemplary embodiment according to FIG. 6.
  • two filling bores 118a and 118b are provided there, which take over the filling function.
  • the arrangement of the filling bores 118a and 118b are selected such that they come into overlap with one of the injection lines 14 during a full working cycle (suction / conveying).
  • the filling bores should preferably be arranged at 90 ° to the distributor groove.
  • the second leak gap 142 is between the lower boundary edges 43 of the pressure compensation surfaces 36a and 36b and an additional annular groove running around the circumferential surface of the distributor pump piston
  • the third leakage path 49 is essentially 2.5 times larger than the second leakage path.

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

La présente invention porte sur une pompe d'injection de carburant doté d'un piston de pompe distributrice (6) placé dans un alésage prévu dans l'enceinte. La surface du corps de pompe présente une rainure distributrice (12), une rainure de remplissage (18) reliée à une chambre de décompression et une surface de compensation de pression. Celle-ci forme, en direction de la rainure distributrice (12), un premier trajet de fuite (39) et, en direction d'une rainure annulaire (20), un second trajet de fuite (42), en sorte que la surface de compensation de pression, qui reste autrement toujours fermée par la paroi intérieure (5) de l'alésage, assure une alimentation en carburant haute pression sur le premier trajet de fuite (20) en direction de la surface de compensation de pression (36), celle-ci étant à son tour déchargée sur le second trajet de fuite (42) en direction de la rainure annulaire (20). Du fait que la surface de compensation de pression (36) se trouve à l'extrémité opposée de la rainure distributrice, il s'opère un très bon équilibrage des forces s'exerçant sur le piston de la pompe distributrice pendant la phase de refoulement à haute pression, tandis que l'alimentation en pression par les trajets de fuite susmentionnés permet d'adapter ces forces de compensation au niveau de pression respectif et à la charge du piston de la pompe distributrice.
EP98907857A 1997-04-04 1998-01-24 Pompe d'injection de carburant pour moteur a combustion interne Expired - Lifetime EP0906506B1 (fr)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
DE19713868 1997-04-04
DE19713868A DE19713868A1 (de) 1997-04-04 1997-04-04 Kraftstoffeinspritzpumpe für Brennkraftmaschinen
PCT/DE1998/000217 WO1998045592A1 (fr) 1997-04-04 1998-01-24 Pompe d'injection de carburant pour moteur a combustion interne

Publications (2)

Publication Number Publication Date
EP0906506A1 true EP0906506A1 (fr) 1999-04-07
EP0906506B1 EP0906506B1 (fr) 2002-05-08

Family

ID=7825401

Family Applications (1)

Application Number Title Priority Date Filing Date
EP98907857A Expired - Lifetime EP0906506B1 (fr) 1997-04-04 1998-01-24 Pompe d'injection de carburant pour moteur a combustion interne

Country Status (8)

Country Link
US (1) US6152708A (fr)
EP (1) EP0906506B1 (fr)
JP (1) JP2000512362A (fr)
KR (1) KR20000016237A (fr)
CN (1) CN1084841C (fr)
CZ (1) CZ358698A3 (fr)
DE (2) DE19713868A1 (fr)
WO (1) WO1998045592A1 (fr)

Families Citing this family (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US6773240B2 (en) 2002-01-28 2004-08-10 Visteon Global Technologies, Inc. Single piston dual chamber fuel pump
ITBO20040322A1 (it) * 2004-05-20 2004-08-20 Magneti Marelli Powertrain Spa Metodo ed impianto per l'iniezione diretta di carburante in un motore a combustione interna
GB0715982D0 (en) * 2007-08-15 2007-09-26 Itw Ltd Check valve
CN105697205B (zh) * 2016-01-28 2018-06-22 山东康达精密机械制造有限公司 一种直列分配式电控喷油泵用高压燃油分配装置

Family Cites Families (13)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE2353737A1 (de) * 1973-10-26 1975-05-07 Bosch Gmbh Robert Kraftstoffeinspritzpumpe fuer brennkraftmaschinen
DE2449332C2 (de) * 1974-10-17 1986-08-07 Robert Bosch Gmbh, 7000 Stuttgart Kraftstoffverteilereinspritzpumpe für Brennkraftmaschinen
US4537170A (en) * 1984-02-28 1985-08-27 Diesel Kiki Co., Ltd. Distribution type fuel injection pump
US4528965A (en) * 1984-03-27 1985-07-16 Caterpillar Tractor Co. Rotor balancing for distribution valve
DE3424883A1 (de) * 1984-07-06 1986-02-06 Robert Bosch Gmbh, 7000 Stuttgart Kraftstoffeinspritzpumpe fuer brennkraftmaschinen
JPS61112771A (ja) * 1984-11-06 1986-05-30 Nissan Motor Co Ltd 分配型燃料噴射ポンプ
DE3524241A1 (de) * 1985-07-06 1987-01-08 Bosch Gmbh Robert Kraftstoffeinspritzpumpe fuer brennkraftmaschinen
DE3612068A1 (de) * 1986-04-10 1987-10-15 Bosch Gmbh Robert Kraftstoffeinspritzpumpe fuer brennkraftmaschinen mit abgasrueckfuehrung
DE3644583A1 (de) * 1986-12-27 1988-07-07 Bosch Gmbh Robert Kraftstoffeinspritzpumpe fuer brennkraftmaschinen
DE3722151A1 (de) * 1987-07-04 1989-01-12 Bosch Gmbh Robert Kraftstoffeinspritzpumpe
DE3819996A1 (de) * 1988-06-11 1989-12-14 Bosch Gmbh Robert Hydraulische steuereinrichtung insbesondere fuer kraftstoffeinspritzanlagen von brennkraftmaschinen
DE3943297A1 (de) * 1989-12-29 1991-07-04 Bosch Gmbh Robert Kraftstoffeinspritzpumpe
JP3041210B2 (ja) * 1994-12-28 2000-05-15 トヨタ自動車株式会社 分配型燃料噴射ポンプ

Non-Patent Citations (1)

* Cited by examiner, † Cited by third party
Title
See references of WO9845592A1 *

Also Published As

Publication number Publication date
CN1222952A (zh) 1999-07-14
JP2000512362A (ja) 2000-09-19
KR20000016237A (ko) 2000-03-25
DE19713868A1 (de) 1998-10-08
CZ358698A3 (cs) 1999-03-17
US6152708A (en) 2000-11-28
CN1084841C (zh) 2002-05-15
DE59804032D1 (de) 2002-06-13
WO1998045592A1 (fr) 1998-10-15
EP0906506B1 (fr) 2002-05-08

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