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EP0664854B1 - Kraftstoffeinspritzvorrichtung für brennkraftmaschinen - Google Patents

Kraftstoffeinspritzvorrichtung für brennkraftmaschinen Download PDF

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Publication number
EP0664854B1
EP0664854B1 EP94918280A EP94918280A EP0664854B1 EP 0664854 B1 EP0664854 B1 EP 0664854B1 EP 94918280 A EP94918280 A EP 94918280A EP 94918280 A EP94918280 A EP 94918280A EP 0664854 B1 EP0664854 B1 EP 0664854B1
Authority
EP
European Patent Office
Prior art keywords
injection device
fuel injection
valve member
valve
space
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
EP94918280A
Other languages
German (de)
English (en)
French (fr)
Other versions
EP0664854A1 (de
Inventor
Eugen Drummer
Maximilian Kronberger
Helmut Sattmann
Herbert Strahberger
Gerhard Weisz
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 EP0664854A1 publication Critical patent/EP0664854A1/de
Application granted granted Critical
Publication of EP0664854B1 publication Critical patent/EP0664854B1/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
    • 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
    • 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
    • F02M57/00—Fuel-injectors combined or associated with other devices
    • F02M57/02—Injectors structurally combined with fuel-injection pumps
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M59/00—Pumps specially adapted for fuel-injection and not provided for in groups F02M39/00 -F02M57/00, e.g. rotary cylinder-block type of pumps
    • F02M59/44—Details, components parts, or accessories not provided for in, or of interest apart from, the apparatus of groups F02M59/02 - F02M59/42; Pumps having transducers, e.g. to measure displacement of pump rack or piston
    • F02M59/46—Valves
    • F02M59/466—Electrically operated valves, e.g. using electromagnetic or piezoelectric operating means

Definitions

  • the fuel injection device according to the invention with the has characteristic features of claim 1 in contrast, the advantage that the high pressure volume is significant is reduced and at the same time a more compact design of the fuel injection device is achieved.
  • the design according to claim 2 has the advantage that the volume the fuel channel between the pump cylinder and valve seat can also be kept very small. If the valve as Gate valve with a piston valve according to claim 5 trained, this volume is further reduced. According to The configurations according to claim 4 result for the permanent connection between the fuel channel and Pump workspace only slight enlargements of the Cylinder space that is intended for the pump work space. According to claims 6 to 8, there is a safe Guiding the valve member of the solenoid valve at the same time low harmful high pressure dead volume within the Fuel channel.
  • FIG. 1 shows a longitudinal section through a pump cylinder and injector of the fuel injector a first embodiment
  • Figure 2 shows a section perpendicular to the plane of the representation of Figure 1 along the Line II-II
  • Figure 3 is a partial section through the fuel injection device in the longitudinal direction of the pump piston and in one rotated by 90 ° with respect to the illustration in FIG. 1 Level along the line III-III of Figure 2 and Figure 4 a Longitudinal section analogous to Figure 1 with a modified embodiment of the electrically controlled valve.
  • a pump housing 1 shown in section which has a cylindrical nozzle 3rd has a tappet bore 2, in the open from its Side a roller plunger 4 slidably immersed, the outside carries a roller 5 on which a not shown rocker arm actuated by a camshaft of the internal combustion engine attacks.
  • the roller tappet includes one inside Compression spring 6, which is on the one hand at the bottom of the recess supports the neck and on the other hand via a spring plate 7 supported on the roller tappet 4.
  • a pump piston 8 held in a Cylinder bore 11 in the form of a socket in the roller tappet 4 and the nozzle 3 enclosed spring chamber 9 projecting pump cylinder 10 dips.
  • Pump work space 13 which is also closer in Figure 3 is shown.
  • Pressure line 15 continues to an injection valve that with his Housing 16 by means of a union nut 17 on the pump housing is attached.
  • the pressure line runs in the injector housing further to the injector nozzle space, not shown, which is carried out in a known manner.
  • the valve needle of the injector is from an injector closing spring 18 loaded in the closing direction, which in a spring chamber 19 of the Injector housing is housed and attached to one adjustable spring plate 20 supports on the other hand.
  • the fuel channel runs advantageously transverse to the axis of the cylinder bore 11, preferably lies the axis of the fuel channel 22 in a radial plane to the axis of the cylinder bore 11.
  • the fuel channel is as Through bore through the pump housing 1 executed as that can be seen in FIGS. 1 and 2, one exit the fuel channel through a closure part, here e.g. a Cover 24 is closed, which is also an equalization space 25 includes, in which the fuel channel 22 opens.
  • the blind bore forming the control chamber 26 merges into a Larger diameter hole to form a receiving opening 48, in which a magnetic core 35 with a magnetic coil 36 Electromagnet 34 of the solenoid valve 31 is inserted and there is held by a magnetic housing 37 encompassing both. Between magnetic housing 37 and magnetic core 35 with magnetic coil 36 a second compensation space 38 is included, which over Compensating holes 39 in the pump housing directly with the Compensation chamber 25 on the other side of the fuel channel 22 connected is.
  • An armature disk 41 is arranged in the second compensation chamber 38, that with the end face of the magnetic core 35 in known Way works together.
  • the armature disk is driven by a return spring 44, which is supported on the magnet housing 37 in the direction Magnetic core applied. Closes on the armature disk 41 the armature tappet 47 on the solenoid valve 31, which is actuated by a axial bore is guided in the magnetic core 35 and on it other side comes to rest on the valve member 30.
  • the valve member is on its side facing away from the anchor plunger acted upon by a compression spring 49, which is located on the cover 24 supports and thus the valve member in a frictional connection with the anchor plunger. Under the action of both springs 49 and 41, the valve member in when the magnet is not energized Opening direction moves, so that the fuel channel 22 to the control chamber 26 is open.
  • the magnet housing is cylindrical and slidable held in a cup-shaped insert 42 which on its one side facing the fuel injector a passage opening 43 for guiding the cylindrical Has magnet housing and is provided there with sealants and on his other, facing away from the injector Side, has an outer flange 57 which adjoins Parts of a cylinder head wall 45 of the internal combustion engine below Interposition of a sealant comes to the system and is attached there and with his to the fuel injector pointing part through a corresponding opening in this cylinder head wall is passed through.
  • the valve member 30 of the solenoid valve 31 consists of an in the fuel channel 22 projecting first part 50 and one in the Control chamber 26 protruding second part 51.
  • the first part 50 closes towards the compensation chamber 25 with a piston 52 which the compensation space of one between this piston 52 and a guide piston 53 lying annular groove 54 by the injection pressure is applied, separates.
  • the guide piston points Passage cross-sections 55, which the annular groove 54 with a annular space lying between guide piston 53 and sealing surface 29 56 connect.
  • the conical sealing surface 29 is located on an enlarged cylindrical part 58 of the second part 51 of the valve member, on the end face of which Anchor plunger 47 comes to rest.
  • the cylindrical part 58 further immerses in a guide bore 59 in an intermediate washer 60 a, between the control chamber 26 and magnetic core 35, the control chamber 26 is arranged to close. Under the influence the cylindrical part 58 thus arrives at the spring 49 not energized electromagnet to rest on the face of the Magnetic core, which also determines the stroke of the valve member Stop is. Due to the thickness of the washer this stop can be adjusted and thus the opening cross-section of the valve.
  • the annular groove 54 on the valve member lies in the area of the part of the fuel passage 22 that intersects the cylinder bore 11 and is thus constantly connected to the cylinder bore 11.
  • the diameter expansion can be used as an annular groove or annular recess be formed or it is also up to the front side 64 of the cylinder bore leading in the area of the overlap longitudinal groove of the fuel channel with the cylinder bore.
  • connection between cylinder bore and fuel channel 22 be established, which is ultimately the connection through a breakthrough with the help of an erosion process, which in particular also for processing sharp-edged cross-section transitions applied can be achieved so that geometrically seen no overlap of the cross sections of the Bore of the fuel channel 22 with the recess or cylinder bore 11 is present.
  • the connection made in this way is but equate to an overlap.
  • the pump work space can also be used be connected to a storage valve 64.
  • This is the spring plate 20 connected to a piston part 66 via a plunger 65, which is tightly displaceable in a bore 67 and from Pump work chamber pressure against the force of the injector spring is applied.
  • the delivery stroke of the pump piston part of the fuel delivered by a Evasion movement of the piston part 66 are included for reduction the pressure build-up at the start of delivery of the fuel injector.
  • the removal of Fuel the closing of the solenoid valve that begins when Pressure build-up in the pump workspace is a force component in Direction of opening with the valve still open.
  • valve described above is located between the pump work space 13 and control room 26 only a very small one Space burdened by high fuel injection pressure and which essentially consists of the volume of the annular groove 54 and the Annulus 56 exists. This way you get a higher one hydraulic efficiency and more precise control of the Fuel injection quantity and the fuel injection timing, there is a loss of control time for the refilling of high pressure loads Rooms and their relief is reduced.
  • valve member 30 is hydraulic of both Pages about the compensation room 25 and the second compensation room 38 and the control chamber 26 pressure-balanced. These compensation rooms are caused by leakage losses e.g. between the cylindrical Part 58 and the washer 60 supplied with fuel. Because the cylindrical part 58 in diameter is larger than the diameter of the fuel channel Valve member as soon as there is pressure delivery stroke of the pump piston is opened by the high pressure in the opening direction in addition to the force of the spring 46, which is a short Opening time results.
  • FIG. 4 An alternative embodiment to the execution Figures 1 to 3 represents a simplification, is in the Figure 4 shown.
  • the electromagnet on the side facing away from the sealing surface Arranged end of the valve member.
  • Injector housing of fuel channel 22 as Through hole executed by the pump housing 1 and stands in the same way with the cylinder bore 11 or Pump work space 13 in connection.
  • the fuel channel 22 opens into a control chamber 126 which via a fuel inlet bore 133 with a low-pressure fuel chamber to supply the pump work space 10 with Fuel or connected to its discharge.
  • the control room 126 is on the exit of the fuel channel 22 opposite side delimited by an intermediate disk 160, that of a tightly sealing the pump housing to the outside Closure part 69 is held in the pump housing.
  • the intermediate disc has a guide bore 159 which via a groove 70 in the end face of the closure part 69 a compensating bore 139 is connected in the pump housing and over this with a first compensation space 125, in which the Fuel channel 22 opens at its other end.
  • the valve member 130 of this embodiment is a piston configured, arranged in the fuel channel 22 tightly sliding and an annular groove 154 analogous to the annular groove 54 of FIG. 1 has that constantly over a connection cross section 71, the either by penetrating the fuel channel and pump cylinder or its diameter extension 62 or by erosive Establishing this connection has arisen with the pump work room 13 or the cylinder bore 11 is connected.
  • the part of the valve member protruding into the first compensation chamber 125 130 carries an armature 141 which is connected to the magnetic core 135 of the electromagnet 134 now arranged on this side cooperates.
  • the magnetic core with magnetic coil 136 is from enclosed a magnet housing 137 that the housing with the first Compensation room 125 closes to the outside.
  • a return spring 149 is used that the valve member 130 towards its open position acted upon and against the excitation of the electromagnet 134 the valve member via the armature 141 in its Is brought into the closed position.
  • the spring chamber 9 is in the socket 3 completely enclosed by the roller tappet 4 and only one Throttle opening 68 can be relieved.
  • this throttle bore will in the course of the pressure stroke of the pump piston by the in the Socket 3 immersed part of the roller tappet 4 closed, so that the fuel injection pump against the cam drive End of the pump piston delivery stroke in a now closed Spring chamber 9 a restoring pressure is built up, the Operation of the return spring 6 supports.
  • This will in particular the tendency of the roller tappet or rocker arm to lift off from the driving cam towards the end of the delivery stroke prevented because in this area a higher resetting Power works.
  • the maximum pressure between roller and cam due to the flattening course the cam elevation curve of the drive cam towards the end of the stroke not increased.

Landscapes

  • Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Electromagnetism (AREA)
  • Fuel-Injection Apparatus (AREA)
EP94918280A 1993-07-07 1994-06-18 Kraftstoffeinspritzvorrichtung für brennkraftmaschinen Expired - Lifetime EP0664854B1 (de)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
DE4322546 1993-07-07
DE4322546A DE4322546A1 (de) 1993-07-07 1993-07-07 Kraftstoffeinspritzvorrichtung für Brennkraftmaschinen
PCT/DE1994/000693 WO1995002123A1 (de) 1993-07-07 1994-06-18 Kraftstoffeinspritzvorrichtung für brennkraftmaschinen

Publications (2)

Publication Number Publication Date
EP0664854A1 EP0664854A1 (de) 1995-08-02
EP0664854B1 true EP0664854B1 (de) 1998-04-08

Family

ID=6492129

Family Applications (1)

Application Number Title Priority Date Filing Date
EP94918280A Expired - Lifetime EP0664854B1 (de) 1993-07-07 1994-06-18 Kraftstoffeinspritzvorrichtung für brennkraftmaschinen

Country Status (8)

Country Link
US (2) US5606953A (ko)
EP (1) EP0664854B1 (ko)
JP (1) JP3539959B2 (ko)
KR (1) KR100340742B1 (ko)
CN (1) CN1049952C (ko)
DE (2) DE4322546A1 (ko)
RU (1) RU2120055C1 (ko)
WO (1) WO1995002123A1 (ko)

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* Cited by examiner, † Cited by third party
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IT1306317B1 (it) * 1998-07-16 2001-06-04 Magneti Marelli Spa Dispositivo di pompaggio ad alta pressione
DE19837333A1 (de) * 1998-08-18 2000-02-24 Bosch Gmbh Robert Steuereinheit zur Steuerung des Druckaufbaus in einer Pumpeneinheit
DE19923422C2 (de) * 1999-05-21 2003-05-08 Bosch Gmbh Robert Elektronisches Einspritzsystem
DE19963568A1 (de) * 1999-12-29 2001-07-05 Bosch Gmbh Robert Brennstoffeinspritzventil
DE10031570C2 (de) * 2000-06-29 2002-09-26 Bosch Gmbh Robert Leckage reduzierter Hochdruckinjektor
US6450778B1 (en) 2000-12-07 2002-09-17 Diesel Technology Company Pump system with high pressure restriction
DE602005009644D1 (de) * 2004-12-17 2008-10-23 Denso Corp Magnetventil, durchflussregelndes Ventil, Kraftstoffhochdruckpumpe und Einspritzpumpe
GB201011092D0 (en) 2010-07-01 2010-08-18 Lucite Int Uk Ltd A catalyst system and a process for the production of ethylenically unsaturated carboxylic acids or esters
EP2538067B1 (en) * 2011-06-20 2014-10-08 Delphi International Operations Luxembourg S.à r.l. Assembly for an electrically operated valve
US9989026B2 (en) * 2012-02-17 2018-06-05 Ford Global Technologies, Llc Fuel pump with quiet rotating suction valve
WO2016129618A1 (ja) * 2015-02-12 2016-08-18 古河電気工業株式会社 半導体レーザ素子およびレーザ光照射装置
US10330065B2 (en) * 2016-03-07 2019-06-25 Stanadyne Llc Direct magnetically controlled inlet valve for fuel pump
WO2019131049A1 (ja) * 2017-12-26 2019-07-04 日立オートモティブシステムズ株式会社 燃料供給ポンプ

Citations (1)

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WO1992010666A1 (en) * 1990-12-11 1992-06-25 Lucas Industries Public Limited Company Fuel pump

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WO1992010666A1 (en) * 1990-12-11 1992-06-25 Lucas Industries Public Limited Company Fuel pump

Also Published As

Publication number Publication date
WO1995002123A1 (de) 1995-01-19
RU95108382A (ru) 1997-01-10
US5709195A (en) 1998-01-20
RU2120055C1 (ru) 1998-10-10
DE59405637D1 (de) 1998-05-14
CN1112370A (zh) 1995-11-22
CN1049952C (zh) 2000-03-01
JPH08501368A (ja) 1996-02-13
US5606953A (en) 1997-03-04
JP3539959B2 (ja) 2004-07-07
KR100340742B1 (ko) 2002-10-31
DE4322546A1 (de) 1995-01-12
EP0664854A1 (de) 1995-08-02
KR950703121A (ko) 1995-08-23

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