EP2354526A2 - Injecteur de carburant - Google Patents

Injecteur de carburant Download PDF

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Publication number
EP2354526A2
EP2354526A2 EP11150091A EP11150091A EP2354526A2 EP 2354526 A2 EP2354526 A2 EP 2354526A2 EP 11150091 A EP11150091 A EP 11150091A EP 11150091 A EP11150091 A EP 11150091A EP 2354526 A2 EP2354526 A2 EP 2354526A2
Authority
EP
European Patent Office
Prior art keywords
valve
bore
fuel injector
valve member
chamber
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
EP11150091A
Other languages
German (de)
English (en)
Other versions
EP2354526A3 (fr
EP2354526B1 (fr
Inventor
Hans Brekle
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 EP2354526A2 publication Critical patent/EP2354526A2/fr
Publication of EP2354526A3 publication Critical patent/EP2354526A3/fr
Application granted granted Critical
Publication of EP2354526B1 publication Critical patent/EP2354526B1/fr
Not-in-force legal-status Critical Current
Anticipated expiration legal-status Critical

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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
    • F02M63/00—Other fuel-injection apparatus having pertinent characteristics not provided for in groups F02M39/00 - F02M57/00 or F02M67/00; Details, component parts, or accessories of fuel-injection apparatus, not provided for in, or of interest apart from, the apparatus of groups F02M39/00 - F02M61/00 or F02M67/00; Combination of fuel pump with other devices, e.g. lubricating oil pump
    • F02M63/0012—Valves
    • F02M63/0031—Valves characterized by the type of valves, e.g. special valve member details, valve seat details, valve housing details
    • 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
    • F02M47/00—Fuel-injection apparatus operated cyclically with fuel-injection valves actuated by fluid pressure
    • F02M47/02—Fuel-injection apparatus operated cyclically with fuel-injection valves actuated by fluid pressure of accumulator-injector type, i.e. having fuel pressure of accumulator tending to open, and fuel pressure in other chamber tending to close, injection valves and having means for periodically releasing that closing pressure
    • F02M47/027—Electrically actuated valves draining the chamber to release the closing pressure
    • 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
    • F02M63/00—Other fuel-injection apparatus having pertinent characteristics not provided for in groups F02M39/00 - F02M57/00 or F02M67/00; Details, component parts, or accessories of fuel-injection apparatus, not provided for in, or of interest apart from, the apparatus of groups F02M39/00 - F02M61/00 or F02M67/00; Combination of fuel pump with other devices, e.g. lubricating oil pump
    • F02M63/0012—Valves
    • F02M63/0031—Valves characterized by the type of valves, e.g. special valve member details, valve seat details, valve housing details
    • F02M63/0033—Lift valves, i.e. having a valve member that moves perpendicularly to the plane of the valve seat
    • F02M63/0035—Poppet valves, i.e. having a mushroom-shaped valve member that moves perpendicularly to the plane of the valve seat
    • 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
    • F02M63/00—Other fuel-injection apparatus having pertinent characteristics not provided for in groups F02M39/00 - F02M57/00 or F02M67/00; Details, component parts, or accessories of fuel-injection apparatus, not provided for in, or of interest apart from, the apparatus of groups F02M39/00 - F02M61/00 or F02M67/00; Combination of fuel pump with other devices, e.g. lubricating oil pump
    • F02M63/0012—Valves
    • F02M63/0031—Valves characterized by the type of valves, e.g. special valve member details, valve seat details, valve housing details
    • F02M63/0045—Three-way valves
    • 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
    • F02M63/00—Other fuel-injection apparatus having pertinent characteristics not provided for in groups F02M39/00 - F02M57/00 or F02M67/00; Details, component parts, or accessories of fuel-injection apparatus, not provided for in, or of interest apart from, the apparatus of groups F02M39/00 - F02M61/00 or F02M67/00; Combination of fuel pump with other devices, e.g. lubricating oil pump
    • F02M63/0012—Valves
    • F02M63/007—Details not provided for in, or of interest apart from, the apparatus of the groups F02M63/0014 - F02M63/0059
    • F02M63/0078—Valve member details, e.g. special shape, hollow or fuel passages in the valve member

Definitions

  • the invention relates to a fuel injector for a fuel injection system, in particular a common rail injection system, having the features of the preamble of claim 1.
  • a fuel injector comprises a control valve for controlling a hubbeweglichen nozzle needle, on the lifting movement at least one injection port is releasable or closable.
  • the control valve comprises a valve chamber for receiving a liftable valve member having a valve seat cooperating with a valve cone, wherein the valve space is bounded by a throttle plate, in the at least one first bore for connecting the valve chamber with a control chamber and a second bore for connecting the Valve space are formed with a high pressure passage.
  • the fuel injector described herein has a double-switching control valve with a valve body guided in a housing of the control valve so that wear on a poppet of the valve body and on a first valve seat in the housing of the control valve is reduced.
  • the valve body receiving the valve chamber is further connected via a first bore serving as a drain with a control chamber and via a serving as a bypass second bore with an inlet channel.
  • fuel in a first closed position of the valve body, fuel can flow into the control chamber via the bypass and the drainage channel in order to bring about rapid closing of the nozzle needle.
  • the object of the present invention is to effect, while maintaining the overall height, a further relief of the control valve in the region of its valve seat.
  • the fuel injector should be simple, preferably using the most known components, and thus inexpensive to produce.
  • a bypass function should be retained.
  • the proposed to solve the problem fuel injector has a control valve with a valve member, which is inventively traversed by an axially extending bore, in which a bolt is accommodated play.
  • the hydraulic force can be significantly reduced in the region of the valve seat, since the rail pressure no longer acts on the entire valve seat surface, but only on the reduced around the bore or bolt cross-sectional area.
  • the load on the valve seat can be reduced in this way to 65% and below. This in turn means that the rail pressure can be further increased.
  • the fuel injector can therefore be used at system pressures well above 2,000 bar. To implement the measure, it only requires less constructive changes, which essentially affect the valve member itself.
  • the bolt has the same length in the axial direction as the valve member.
  • the valve member passing through the axially extending bore is thus completely closed by the bolt.
  • the bolt has a smaller length in the axial direction than the valve member.
  • the bolt is formed integrally with the throttle plate, i. that the bolt and the throttle plate may be formed as a part or the bolt may be integrally connected to the throttle plate.
  • the bolt may be embedded in the throttle plate.
  • a frictional connection can be made for example via a press connection. The bolt is thus part of the throttle plate and thus fixed in position. The relative to the bolt slidably mounted valve member is guided by the pin or centered with respect to the valve seat. This also allows the load in the region of the valve seat can be reduced.
  • control valve is double-switching and formed on a valve seat facing away from the end of the valve member of the valve member of the control valve, a further sealing surface over which the second bore formed in the throttle plate is releasable or closable. Since the second bore formed in the throttle plate connects the valve chamber to the high-pressure passage, a bypass function is ensured via this second bore.
  • the further formed on the valve member sealing surface allows the release or closing of the bypass bore, wherein in a first closed position of the control valve, in which the valve cone of the valve member abuts the first valve seat, the bypass bore is released, and in a second closed position of the control valve, in which abuts the valve member with its further sealing surface on the throttle plate, the bypass hole is closed.
  • the control valve In the first closed position of the control valve can thus be supplied via the bypass bore under high pressure fuel from the high-pressure passage to the valve chamber, which then formed over a likewise formed in the throttle plate, as Drain serving bore is supplied to the control room. In this way, a faster filling of the control chamber with fuel under high pressure and thus a fast nozzle needle closing can be effected.
  • the second closed position of the control valve in which the valve chamber is connected to a low pressure chamber, the return flow can be reduced by closing the bypass bore.
  • the further sealing surface formed on the valve seat is preferably planar and / or annular and / or cooperates with a flat seat formed on the throttle plate. If a separate bolt is accommodated in the axially extending bore of the valve member, a sealing surface for closing or releasing the bypass bore can also be formed thereon. However, if the bolt is formed integrally with the throttle plate, only a ring formed on the valve member sealing surface is used to close or the release of the bypass. Accordingly, the bore serving as a bypass is to be guided within the throttle plate. This means that in one piece design of the bolt with the throttle plate, the bypass hole radially offset from the bolt opens into the valve chamber. In a separately formed bolt, the mouth region of the bypass bore can also be arranged coaxially to the bolt.
  • At least one throttle point is formed, which is further preferably formed as a coaxial or branching bore with a smaller flow cross-section than the second bore.
  • the formation and position of the throttle point depends in turn on whether the bolt is freely movable or designed as a position-fixed component of the throttle plate. If at least two throttle points are provided, at least one throttle point is formed as a branching bore, which opens radially offset from the bolt in the valve chamber. The formation of at least one throttle point improves the hydraulic design, since this acts to dampen.
  • the throttle point formed in the second bore is preferably arranged on the valve chamber side, ie in the mouth region of the second bore with the valve chamber. This simplifies the formation of the throttle point, as it is the top of the throttle plate is easily accessible.
  • the throttle point may also have been produced by means of laser drilling.
  • a compression spring for biasing the valve member relative to the valve seat is received in the valve chamber.
  • the compression spring is supported on the one hand on the valve cone of the valve member and on the other hand on the throttle plate. On the valve cone this is preferably a radially extending shoulder formed as a spring plate. The valve cone thus has a radial excess over a cylindrical portion of the valve member.
  • the compression spring ensures the installation of the valve member on the valve seat in the closed position of the control valve.
  • a piezoelectric actuator for actuating the control valve. High switching forces can be achieved by means of a piezo actuator or a plurality of piezo actuators combined to form a stack.
  • the Indian FIG. 1 shown known Kraftstoffinjektor has a control valve 1 for actuating a nozzle needle 2, which is axially displaceable in a nozzle body 23 is included.
  • the nozzle body 23 has a bore formed as a high-pressure channel 11, which connects a feed line 19 with at least one injection opening 23 (not shown) formed in the nozzle body 23.
  • the high-pressure fuel is thus supplied via the supply line 19 and the high-pressure passage 11 of the at least one injection nozzle.
  • the high-pressure channel 11 is delimited by means of a throttle plate 7, which is attached axially to the nozzle body 23. Between the throttle plate 7 and the nozzle needle 2, a control chamber 9 is further separated from the high-pressure passage 11 via a control sleeve 22.
  • the movement of the nozzle needle 2 is controllable. If the hydraulic pressure in the control chamber 9 increases, a closing force is exerted on the nozzle needle 2, so that the nozzle needle is transferred into its closed position. The closing process is supported by the pressure force of a closing spring 24. In contrast, falls off the hydraulic pressure in the control chamber 9, the nozzle needle 2 opens by lifting from their sealing seat. In order to cause the pressure increase or pressure drop in the control chamber 9, this is on the one hand via an opening formed in the throttle plate 7 and an inlet throttle 20 inlet bore 21 with the feed line 19 and on the other hand via a in the throttle plate. 7 trained and a drain throttle 25 having drain hole connected to a valve chamber 3 of the control valve.
  • the valve chamber 3 is in turn connectable to a low pressure chamber 18, via which the Abêtmenge can be fed to a return.
  • the connection of the valve chamber 3 with the low pressure chamber 18 is made via a corresponding switching position of the control valve 1.
  • a hydraulic connection is provided when a cooperating with a valve seat 5 valve cone 6 of a valve member 4 occupies a position lifted from the valve seat 5 position.
  • the poppet 6 of the valve member 4 seals against the valve seat 5 of the control valve 1
  • a hydraulic connection of the valve chamber 3 to the low-pressure chamber 18 is prevented.
  • a pressure increase in the control chamber 9 can be effected via the inlet bore 21 contained in the inlet throttle 20, which finally leads to the closing of the nozzle needle 2.
  • a bore 10 is provided in the throttle plate 7 further, which connects the valve chamber 3 with the high pressure passage 11 and thus serves as a bypass.
  • the valve member 4 is located with a further sealing surface 14 on a trained flat seat valve seat of the throttle plate 7, thereby closing the serving as a bypass bore 10.
  • fuel from the valve chamber 3 via the valve seat 5 in the low pressure space 18 outflow.
  • the bypass bore 10 is closed, the amount of fuel supplied via the low-pressure chamber 18 to a return line remains low.
  • the control valve 1 by operation of an actuator, such as a piezoelectric actuator (not shown) transferred.
  • a compression spring 17 ensures that the valve member 4 of the control valve 1 returns to its initial position, ie its first closed position.
  • FIG. 2 is an enlarged view of the valve member 4 of the fuel injector according to the Fig. 1 to be taken, which comprises a valve cone 6 cooperating with the valve seat 5. Furthermore, a further sealing surface 14 is formed on the valve cone 6 opposite end face of the valve member 4, which is engageable with the throttle plate 7 for closing the bore 10 serving as a bypass.
  • valve member 4 of a fuel injector according to the invention.
  • this valve member 4 has a cooperating with the valve seat 5 valve cone 6 and a further sealing surface 14 on the valve cone 6 opposite end face.
  • the valve member 4 has an axially extending bore 12 which completely penetrates the valve member 4.
  • the valve member 4 is thus designed as a hollow body.
  • a bolt 13 is received, which according to the embodiment of the FIG. 3 has the same length as the valve member 4.
  • the bolt 13 may also have a smaller length than the valve member 4.
  • a corresponding embodiment is in the FIG. 4 shown.
  • the bolt 13 is also integrally connected to the throttle plate 7 and thus fixed in position. Consequently, an axial guidance of the lifting valve member 4 is effected via the bolt 13.
  • throttle bodies 15, 16 are formed in the bore serving as a bore, which connect the bore 10 with the valve chamber 3.
  • Both throttle plates 15, 16 are formed as holes with a reduced flow cross-section relative to the bore 10, wherein the bores are guided such that they open radially offset from the bolt 13 in the valve chamber 3.
  • the release and closing of the throttle points 15, 16 and the bypass bore 10 is effected in the present case solely by the sleeve-like executed valve member 4.
  • an annular sealing surface 14 is formed on the valve cone 6 opposite end face of the valve member 4.
  • the relief caused by the fuel injector according to the invention of the control valve in the region of its valve seat is in the diagram of FIG. 5 shown graphically.
  • different diameters of the bolt 13 are plotted in millimeters, which in the present range from 0 to 1.2 mm.
  • the remaining load is plotted on the y-axis in percent.
  • the graph shows several graphs, each representing a specific seat diameter.
  • the seat diameter varies here between 1.33 mm (bottom graph) and 1.43 mm (top graph). Decisive for the degree of relief is therefore the area ratio between seat diameter and bolt diameter.

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  • Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Fluid Mechanics (AREA)
  • Fuel-Injection Apparatus (AREA)
EP20110150091 2010-01-28 2011-01-04 Injecteur de carburant Not-in-force EP2354526B1 (fr)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
DE201010001315 DE102010001315A1 (de) 2010-01-28 2010-01-28 Kraftstoffinjektor

Publications (3)

Publication Number Publication Date
EP2354526A2 true EP2354526A2 (fr) 2011-08-10
EP2354526A3 EP2354526A3 (fr) 2013-07-24
EP2354526B1 EP2354526B1 (fr) 2014-07-23

Family

ID=43903986

Family Applications (1)

Application Number Title Priority Date Filing Date
EP20110150091 Not-in-force EP2354526B1 (fr) 2010-01-28 2011-01-04 Injecteur de carburant

Country Status (2)

Country Link
EP (1) EP2354526B1 (fr)
DE (1) DE102010001315A1 (fr)

Cited By (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP2813698A1 (fr) * 2013-06-10 2014-12-17 Robert Bosch Gmbh Soupape d'injection de combustible
WO2016059079A1 (fr) * 2014-10-15 2016-04-21 Continental Automotive Gmbh Soupape d'injection de fluide dans une chambre de combustion d'un moteur à combustion interne
CN106593725A (zh) * 2017-01-18 2017-04-26 哈尔滨工程大学 谐振式电控喷油器
WO2018046204A1 (fr) * 2016-09-06 2018-03-15 Continental Automotive Gmbh Injecteur de fluide pour un véhicule automobile

Citations (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102004061800A1 (de) 2004-12-22 2006-07-06 Robert Bosch Gmbh Injektor eines Kraftstoffeinspritzsystems einer Brennkraftmaschine

Family Cites Families (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB9526522D0 (en) * 1995-12-23 1996-02-28 Lucas Ind Plc Valve arrangement
GB0215490D0 (en) * 2002-07-04 2002-08-14 Delphi Tech Inc Control valve arrangement
DE102008040637A1 (de) * 2008-07-23 2010-01-28 Robert Bosch Gmbh Kraftstoffeinspritzventileinrichtung

Patent Citations (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102004061800A1 (de) 2004-12-22 2006-07-06 Robert Bosch Gmbh Injektor eines Kraftstoffeinspritzsystems einer Brennkraftmaschine

Cited By (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP2813698A1 (fr) * 2013-06-10 2014-12-17 Robert Bosch Gmbh Soupape d'injection de combustible
WO2016059079A1 (fr) * 2014-10-15 2016-04-21 Continental Automotive Gmbh Soupape d'injection de fluide dans une chambre de combustion d'un moteur à combustion interne
WO2018046204A1 (fr) * 2016-09-06 2018-03-15 Continental Automotive Gmbh Injecteur de fluide pour un véhicule automobile
CN106593725A (zh) * 2017-01-18 2017-04-26 哈尔滨工程大学 谐振式电控喷油器

Also Published As

Publication number Publication date
EP2354526A3 (fr) 2013-07-24
EP2354526B1 (fr) 2014-07-23
DE102010001315A1 (de) 2011-08-18

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