EP0708885B1 - Kraftstoffeinspritzpumpe - Google Patents

Kraftstoffeinspritzpumpe Download PDF

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Publication number
EP0708885B1
EP0708885B1 EP95900649A EP95900649A EP0708885B1 EP 0708885 B1 EP0708885 B1 EP 0708885B1 EP 95900649 A EP95900649 A EP 95900649A EP 95900649 A EP95900649 A EP 95900649A EP 0708885 B1 EP0708885 B1 EP 0708885B1
Authority
EP
European Patent Office
Prior art keywords
distributor
valve member
fuel injection
injection pump
pump according
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
EP95900649A
Other languages
German (de)
English (en)
French (fr)
Other versions
EP0708885A1 (de
Inventor
Andreas Dutt
Burkhard Veldten
Nestor Rodriguez-Amaya
Walter Fuchs
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
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 EP0708885A1 publication Critical patent/EP0708885A1/de
Application granted granted Critical
Publication of EP0708885B1 publication Critical patent/EP0708885B1/de
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • 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 relates to a fuel injection pump Distribution type according to the preamble of claim 1.
  • Such a fuel injection pump is through EP-A-0 524 132 known.
  • the fuel injection pump there it is a so-called radial piston pump, in which radially running in the rotating driven distributor Cylinder bores are provided in which pump pistons can be moved are arranged, which are on a roller tappet fixed cam ring, which the distributor in the area of Support the cylinder bores around the circumference.
  • the rotatably driven distributor causes the expiration of the Roller tappet on the cam ring and thus a back and forth Movement of the pump pistons, on the other hand by their opposite sides of a pump work room lock in. This is over the connection channel and that of the solenoid controlled valve to the relief space relieved.
  • the valve member of this valve is in the known Execution loaded by a spring in the opening direction and movable by a plunger in the closing direction, the Tappet with a relative to the fixed poles of an electromagnet axially adjustable armature is moved. For one exact dimensioning requires an exact assignment of the electromagnet to the distributor.
  • the axial position of the distributor is in the known embodiment by a Ring groove engaging disc secured. This type of attachment has the disadvantage, however, that the axial fixation of the Distributor is provided with a game that results from the tolerances the components and an unimpeded rotational movement without Clamping the distributor allows additional play. There are also thermal expansions of the individual components to consider each other.
  • this game has Consequence that the distance from the distributor or valve seat or valve member in its closed position to the magnet to different Operating points can be different. This means on the other hand, that a working air gap provided on the electromagnet different between armature and magnetic pole gets big. This in turn is disadvantageous to that of the solenoid valve applied shifting force and shifting speed and Dynamics of the switching behavior of the magnet. It result from these deviations different switching times of the High pressure injection phase determining valve and thus different Fuel injection quantities and injection start times deviating from a desired injection quantity for the respective Operating point.
  • the fuel injection pump according to the invention with the characteristic Features of claim 1 has the advantage in that the part of the the magnetic circuit of the core forming the electromagnet is adjustable with the distributor with the success that with itself the working air gap adjusts the valve member at the same time between the anchor and this adjustable core remains the same size. This also leaves those of the electromagnet Forces and forces developed for switching the valve the dynamic switching behavior of this solenoid valve independently on the dimensioning of the axial play of the distributor equal.
  • the electromagnet designed according to claim 2 by the with the anchor cooperating part of the core or magnetic pole of the electromagnet is directly coupled to the face of the distributor.
  • a preferred embodiment of the electromagnet in connection with the valve to control the connection between the pump work space and relief space is the subject of Claim 4.
  • the magnetic coupling of this core part to the side core A relatively low magnetic flux density has occurred on the circumference present in the magnetic coupling area compared to the high one Magnetic flux density in the area of the working air gap between the Anchor that slides in the axial recess and that central breakthrough surrounding part of the second yoke.
  • Air gaps between this second yoke and the side core as well as between the outer circumference of the anchor and the wall of the Recess in the central core contribute little to a magnetic one Flow loss at and can be considered a quasi-constant variable be taken into account when dimensioning the electromagnet. It is essential that the technical Properties of the electromagnet even with a shift of the distributor do not change.
  • the second yoke at the same time as an attachment for one different spacer rings of different widths variable Stop the distributor and at the same time to fix the Opening stroke determining stop for the valve member according to Claim 7.
  • Opening outwards means that the draining Fuel flow in the direction of the outward opening can flow moving valve member.
  • the outflowing fuel flows against the outgoing Opening movement of the valve member inside the axial Hole and from there to a relief room. This fuel flow causes a different opening dynamic than that of the outward opening valve.
  • FIG. 1 shows the fuel injection pump according to the invention with an inward opening valve and figure 2 the fuel injection pump according to the invention with a outside opening valve.
  • FIG. 1 shows a section through part of a Distributor injection pump in which the essential to the invention Features are realized. It is in a housing 1 Fuel injection pump a socket 2 in a housing bore 3rd used, which in turn has a guide bore inside 5, in which a distributor 7 is guided. This will via a coupling part 8 of a not shown Drive shaft of the distributor injection pump driven in rotation and runs synchronously with the speed of the associated internal combustion engine around. On its drive side protruding from the socket At the end of the distributor has a collar 9 with which it to the end face 11 of a part projecting into a suction chamber 12 socket 2 starts up.
  • the pump work space 15 is via a pressure channel 19 which is in the Runs inside the distributor, with a distributor groove 20 Circumference of the manifold connected with in the radial plane, in which is the distributor groove 20, leading away from the guide bore 5 injection lines initially designed as bores 21 is connectable, each of which is not further here lead shown fuel injector.
  • a second part 33 of the connecting channel 23 leads away from the annular groove and opens into a longitudinal groove in the lateral surface of the distributor 34, which in turn opens into an annular groove 35, which has a Cross bore 36 in the socket 2 and a further line 37 leads to a relief space, which in the present case is the Suction chamber 12 is.
  • a valve member 39 with a tight fit is slidable performed that in the area of the inner annular groove 25 of the axial Bore has an outer annular groove 40, with which it together with the inner annular groove 25 forms an annular space 41.
  • an annular shoulder 42 through the outer annular groove on the valve member formed with the outer diameter of the annular shoulder 28th protrudes beyond the axial bore and one points towards the valve seat 29 has a sealing surface 43.
  • the diameter smaller part of the axial bore at the passage in the The area of the annular shoulder 28 tapers the diameter of the Valve member and subsequently widens conically a guide piston 45 which cooperates with the web 31.
  • a spring 46 On the end of the guide piston engages a spring 46 which is based in the bottom 47 of the axial bore and the valve member so loaded that it is inclined with its ring shoulder 42 lift off valve seat 29.
  • the valve member 39 protrudes from the axial bore on the end face 26 of the distributor and has outstanding on this End 49 formed by a diameter reduction a neck 50 which subsequently merges into a head 51 the a sleeve-shaped or designed as a perforated disc anchor 52 is pressed or is firmly connected to the valve member.
  • the armature can also be in one piece with the valve member.
  • Breakthroughs 56 and 58 both have the shape of a keyhole, such that the valve member with its largest diameter through the Hole of the keyhole can be done and then with its neck in its end position in relation to the stop disc and Magnetic disk can be brought. Both panes are through common fastening screws 59 on the end face 26 of the Screwed on distributor. Instead of magnetic disc 55 and stop disc 54 can be adhered to both magnetic as well as mechanical requirements just a single disc be provided.
  • washers 61 and 62 are washers 61 and 62 as spacers interposed in such a way that with these spacers axial movement play of the distributor between its system with the collar 9 on the front side 11 of the socket 2 and the system the stop washer 54 via the spacer rings on the bushing 2 can be adjusted.
  • the stop disc and the diameter of the distributor Magnetic disk rotate when the fuel injection pump is in operation together with the distributor.
  • the magnetic disc provides 55 a part of a magnetic circuit or core of a Electromagnets.
  • the magnetic disk 55 is on its circumferential face via an air gap 64 with a sleeve-like Side core 65 of magnet 66 is magnetically coupled.
  • the circular cylindrical inner wall of the side core overlaps with the circular cylindrical contour of the magnetic disk 55, which is therefore a Yoke forms.
  • the sleeve-shaped side core 65 in turn merges one opposite this second yoke, the magnetic disk 55 first yoke 67 over into a sleeve-shaped Main core 68, which has an axial, circular cylindrical recess 69 has, in which the armature 52 slidably dips.
  • Annulus 70 is the solenoid 71 of the electromagnet mounted and has 67 leading connections through the first yoke 72 and 73 on.
  • the coil is potted and is radial Distance between main core 68 and side core 65.
  • the annulus 70 is 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 a surrounding the side core Annulus 77 connected, which is not shown here, with the relief chamber 12, the suction chamber is connected.
  • the Recess 69 is through from the side of the first yoke 67 a closure part 78 closed, so that in the Recess 69 on the other hand closed by the armature 52 Interior that forms, as I said, over the Cross channels 75 and 76 can be connected to the relief space such that the armature is axially free in the main core can move and at the same time the solenoid with fuel is washed around, promoted by the pumping back and forth movement the anchor during its work cycles.
  • the magnetic core of the electromagnet consists of one a fixed magnetic core with the usual plunger magnet hollow core, the first yoke 67 and the side yoke 65 and has in the particular invention Design now a moving part, the second yoke in Shape of the magnetic disk 55, which cooperates with the armature 52.
  • the second yoke in Shape of the magnetic disk 55, which cooperates with the armature 52.
  • the pump piston 14 of the cam track 18th effected inward stroke of the pump piston 14 reduces the Pump workspace in its volume and the fuel is on conveyed back the same way as long as the valve member from the valve seat 29 is lifted off.
  • the valve member by the electromagnet in the closed position brought so that it with its sealing surface 43 on the seat 29th sits on.
  • the configuration according to the invention has the advantage that the axial securing of the distributor can be backlash, what is also necessary for technical reasons or not avoided can be. Nevertheless, the game changes Working air gap 80 not.
  • the magnetic disc is always in the fixed distance to the seat 29 in the distributor and the anchor 52 also at a fixed distance from the seat 29 in the distributor at on the Seat 29 seated valve member.
  • the working air gap thus remains 80 constant regardless of the position of the distributor.
  • Corresponding a slight displacement of the distributor moves the anchor plate 55, which rotates together with the distributor within the inner diameter of the sleeve-shaped side core 65, but remains there magnetically over the air gap 64 with the Coupled side core. The shift results here no changes affecting anchor movement.
  • the anchor on the Valve member is attached so that there is no mechanical wear due to impact parts, as is the case with the usual Constructions for actuating a valve member is the case.
  • the setting of the residual air gap at working gap 80 is easier Solvable way, because a simple assignment of pressed Anchor part 52 and magnetic disc with flat surface possible is.
  • valve member slightly different designed and 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 with approximately continuous same diameter.
  • the connecting member 23 in turn has the valve member 139 an outer ring groove 140, which together with the blind bore 124 forms an annular space 141.
  • This annulus is limited to the from the end face 126 of the distributor 107 facing away from the Valve member by a guide piston 145 which is in the Rest of the blind bore arranged according to FIG.
  • valve member 139 Adjacent to the ring shoulder 142, the valve member 139 in turn has the annular shoulder 57 with which it is used to limit its opening stroke in System comes to the stop plate 54. Then that's it Valve element and the fuel injection pump with magnet 166 designed the same as in the previous embodiment.
  • a connecting channel 85 extends transversely from the recess 81 a relief room, in which also a relief line 86 of the space 87 enclosed by the guide piston 145 flows.
  • the embodiment works according to the figure 2 in the same way as the exemplary embodiment according to FIG. 1, only that flow and impulse different conditions prevail, depending on the application advantages in one or in the other form.
  • a locking ring 89 used between and one end face 160 of the socket 102 in turn spacers 61 and 62 inserted are.

Landscapes

  • Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Fuel-Injection Apparatus (AREA)
EP95900649A 1993-11-24 1994-11-22 Kraftstoffeinspritzpumpe Expired - Lifetime EP0708885B1 (de)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
DE4339948 1993-11-24
DE4339948A DE4339948A1 (de) 1993-11-24 1993-11-24 Kraftstoffeinspritzpumpe
PCT/DE1994/001369 WO1995014857A1 (de) 1993-11-24 1994-11-22 Kraftstoffeinspritzpumpe

Publications (2)

Publication Number Publication Date
EP0708885A1 EP0708885A1 (de) 1996-05-01
EP0708885B1 true EP0708885B1 (de) 2001-09-26

Family

ID=6503265

Family Applications (1)

Application Number Title Priority Date Filing Date
EP95900649A Expired - Lifetime EP0708885B1 (de) 1993-11-24 1994-11-22 Kraftstoffeinspritzpumpe

Country Status (8)

Country Link
US (1) US5582153A (es)
EP (1) EP0708885B1 (es)
JP (1) JP3442391B2 (es)
KR (1) KR100373806B1 (es)
CN (1) CN1042968C (es)
DE (2) DE4339948A1 (es)
ES (1) ES2164754T3 (es)
WO (1) WO1995014857A1 (es)

Families Citing this family (17)

* Cited by examiner, † Cited by third party
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
DE69907576T2 (de) * 1998-07-09 2004-04-08 Kabushiki Kaisha Toyota Jidoshokki, Kariya 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
DE10058011A1 (de) * 2000-11-23 2002-05-29 Bosch Gmbh Robert Magnetventilgesteuerte Kraftstoffeinspritzpumpe für Brennkraftmaschinen, insbesondere Dieselmotoren
US6773240B2 (en) 2002-01-28 2004-08-10 Visteon Global Technologies, Inc. Single piston dual chamber fuel pump
US6793196B2 (en) 2002-08-05 2004-09-21 Husco International, Inc. High flow control valve for motor vehicle fuel injection systems
US6807943B2 (en) 2002-08-05 2004-10-26 Husco International, Inc. Motor vehicle fuel injection system with a high flow control valve
US6976640B2 (en) * 2003-12-04 2005-12-20 Kuo-Liang Chen Air gun with a quick-releasing device
EP1707797B1 (en) * 2005-03-14 2007-08-22 C.R.F. Società Consortile per Azioni Adjustable metering servovalve for a fuel injector
US8486718B2 (en) * 2006-05-10 2013-07-16 Koninklijke Philips N.V. 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

Family Cites Families (11)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE3412834A1 (de) * 1984-04-05 1985-10-24 Robert Bosch Gmbh, 7000 Stuttgart Kraftstoffeinspritzpumpe
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
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
US5215060A (en) * 1991-07-16 1993-06-01 Stanadyne Automotive Corp. Fuel system for rotary distributor fuel injection pump
US5215449A (en) * 1991-12-05 1993-06-01 Stanadyne Automotive Corp. Distributor type fuel injection pump
US5228844A (en) * 1992-10-14 1993-07-20 Stanadyne Automotive Corp. Rotary 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

Also Published As

Publication number Publication date
KR960700406A (ko) 1996-01-20
DE4339948A1 (de) 1995-06-01
JPH08510816A (ja) 1996-11-12
CN1116869A (zh) 1996-02-14
KR100373806B1 (ko) 2003-05-09
DE59409881D1 (de) 2001-10-31
WO1995014857A1 (de) 1995-06-01
ES2164754T3 (es) 2002-03-01
EP0708885A1 (de) 1996-05-01
CN1042968C (zh) 1999-04-14
US5582153A (en) 1996-12-10
JP3442391B2 (ja) 2003-09-02

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