EP1990532A1 - Injecteur de carburant pour un moteur à combustion interne comprenant un système d'injection à rampe commune - Google Patents

Injecteur de carburant pour un moteur à combustion interne comprenant un système d'injection à rampe commune Download PDF

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Publication number
EP1990532A1
EP1990532A1 EP08103421A EP08103421A EP1990532A1 EP 1990532 A1 EP1990532 A1 EP 1990532A1 EP 08103421 A EP08103421 A EP 08103421A EP 08103421 A EP08103421 A EP 08103421A EP 1990532 A1 EP1990532 A1 EP 1990532A1
Authority
EP
European Patent Office
Prior art keywords
closing piston
valve element
fuel injector
closing
fluid path
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.)
Withdrawn
Application number
EP08103421A
Other languages
German (de)
English (en)
Inventor
Hans-Christoph Magel
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 EP1990532A1 publication Critical patent/EP1990532A1/fr
Withdrawn legal-status Critical Current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
    • 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
    • F02M61/00—Fuel-injectors not provided for in groups F02M39/00 - F02M57/00 or F02M67/00
    • F02M61/04—Fuel-injectors not provided for in groups F02M39/00 - F02M57/00 or F02M67/00 having valves, e.g. having a plurality of valves in series
    • F02M61/10—Other injectors with elongated valve bodies, i.e. of needle-valve type
    • F02M61/12—Other injectors with elongated valve bodies, i.e. of needle-valve type characterised by the provision of guiding or centring means for valve bodies
    • 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
    • F02M61/00—Fuel-injectors not provided for in groups F02M39/00 - F02M57/00 or F02M67/00
    • F02M61/16—Details not provided for in, or of interest apart from, the apparatus of groups F02M61/02 - F02M61/14
    • F02M61/20—Closing valves mechanically, e.g. arrangements of springs or weights or permanent magnets; Damping of valve lift
    • F02M61/205—Means specially adapted for varying the spring tension or assisting the spring force to close the injection-valve, e.g. with damping of valve lift
    • 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
    • F02M63/02—Fuel-injection apparatus having several injectors fed by a common pumping element, or having several pumping elements feeding a common injector; Fuel-injection apparatus having provisions for cutting-out pumps, pumping elements, or injectors; Fuel-injection apparatus having provisions for variably interconnecting pumping elements and injectors alternatively
    • F02M63/0225—Fuel-injection apparatus having a common rail feeding several injectors ; Means for varying pressure in common rails; Pumps feeding common rails
    • 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
    • F02M2547/00—Special features for fuel-injection valves actuated by fluid pressure
    • F02M2547/001—Control chambers formed by movable sleeves

Definitions

  • the invention relates to a fuel injector for an internal combustion engine with common-rail injection system according to the preamble of claim 1.
  • a high injection pressure is advantageous.
  • a valve element is used, which is completely surrounded by high fuel pressure, ie without a so-called "low-pressure stage" manages.
  • a slight restriction of the fuel in the fluid path from the high pressure port proposed to the sealing seat whereby an additional hydraulic closing force is generated.
  • Object of the present invention is to provide a fuel injector, which has a good closing and opening behavior at high injection pressure and low leakage.
  • the pressure surface acting in the closing direction is selectively increased, whereby the closing behavior is also in a valve element which has no low-pressure stage and is completely surrounded by high pressure fuel by increasing the closing force is improved.
  • the inventively provided flow restrictor which also generates an additional hydraulic closing force by means of the flowing fuel.
  • the present invention provided relief valve limits the pressure difference, which adjusts over the flow restrictor away, to a maximum value.
  • the relief valve may also be referred to as a pressure relief valve.
  • a pressure relief valve As a result, an excessive force acting in the closing direction during opening of the valve element can be avoided.
  • fuel must be displaced from the space lying between the high-pressure connection and the closing piston by the closing piston and the flow restrictor when the valve element is opened, which results in a pressure difference at the flow restrictor which acts counter to the opening movement.
  • the relief valve the pressure in this between high pressure port and Closing piston lying area limited to a maximum value, whereby a too high closing force is avoided when opening the valve element.
  • the relief valve is arranged fluidically parallel to the flow restrictor.
  • a first refinement of the fuel injector according to the invention is characterized in that the relief valve opens to the fluid path lying between the closing piston and the sealing seat. This improves the efficiency of the fuel injector since the fuel flowing out of the fluid path between the closing piston and the high-pressure port is used for the injection.
  • a compact and easy to manufacture construction of the fuel injector according to the invention provides that the closing piston is annular and coaxial with the valve element.
  • the relief valve may be arranged in the closing piston.
  • the injector housing can thus remain unchanged, so that the relief valve provided according to the invention does not affect the production costs of the injector housing.
  • the closing piston can also be integrally formed with the injector or on this. This eliminates the handling of an additional separate part in the assembly of the fuel injector, which simplifies the production.
  • closing piston forms a valve element of the relief valve.
  • the closing piston is therefore also a pressure limiting or relief piston, so that an additional component for limiting the pressure in the lying between the high-pressure port and closing piston area of the fluid path or to limit the pressure difference between this area and the area between closing piston and sealing seat area not is required.
  • the closing piston is acted upon by a spring, which is supported on the valve element, against a sealing section on the valve element.
  • the closing force acting on the closing piston is transmitted via the spring to the valve element.
  • the closing force can be kept almost constant, so that pressure vibrations affect only slightly on the closing force. This leads to an improvement of the injection tolerances, the amount of fuel is thus injected with higher precision.
  • the flow restrictor can also be realized in a particularly simple manner by realizing a gap between the closing piston and an adjacent section. This may be an annular gap or a longitudinal groove, through which the gap is implemented locally.
  • the closing piston in the injector housing is guided in a fluid-tight manner.
  • the sealing seat associated with the closing piston thus lies on the valve element, so that no additional closing force is exerted on the valve element by the closing piston, at least in the idle state.
  • a fuel injector carries in FIG. 1 Overall, it is the reference numeral 10. It is used in an internal combustion engine (not shown) with common rail injection system for direct injection of the fuel in a fuel injector directly associated combustion chamber.
  • the fuel injector 10 comprises a multi-part injector housing 12, which, in FIG. 1 from top to bottom, a control valve piece 14, an end plate 16, an elongate injector body 18 and a nozzle body 20 includes. At the in FIG. 1 lower end of the nozzle body 20, a plurality of fuel outlet channels 22 are provided, through which the fuel is injected during operation of the fuel injector 10 in the associated combustion chamber.
  • valve element 28 which comprises a control rod 30 and, adjacent to the fuel outlet channels 22, a nozzle needle 32.
  • This in FIG. 1 lower end of the nozzle needle 32 cooperates with a housing-side sealing seat 33.
  • the lower end of the control rod 30 is guided over guide portions 34 in the nozzle body 20. Between the guide portions 34 flattened areas 36 are present.
  • a conical and in the opening direction acting pressure surface 37 is present on the nozzle needle 32.
  • a sealing sleeve 38 is placed on the in FIG. 1 upper end of the control rod 30, a sealing sleeve 38 is placed. This is supported by its upper edge on the end plate 16.
  • annular space 40 is formed between the valve element 28 and the injector 12, an annular space 40 is formed. This is connected to a high pressure port 42, which in turn is connected to a common rail 44.
  • An in FIG. 1 This limits together with the sealing sleeve 38 and the end plate 16, a hydraulic control chamber 48 via an inlet throttle 50, this communicates with the annulus 40.
  • Via an outlet throttle 52 communicates the hydraulic control chamber 48 with an electromagnetic Switching valve 54, which connects the hydraulic control chamber 48 with a low pressure port 56 in the open position.
  • an electromagnetic Switching valve 54 may be used.
  • valve element 28 In order to avoid tensioning of the valve element 28 between the sealing sleeve 38 and the guide sections 34, regions with reduced bending stiffness may be provided on the valve element 28 (in FIG FIG. 1 not shown).
  • the valve member may comprise a control rod and a nozzle needle which are coupled together or otherwise mechanically interconnected via a hydraulic coupler without substantially transmitting bending moments from one member to the other. It is further understood that in an embodiment not shown, the valve element may be in one piece, and / or that the valve element may be significantly shorter than in the FIG. 1 illustrated embodiment.
  • the fuel injector 10 has an annular closing piston 58 which is coaxial with the valve element 28 and is guided with its radially outer circumferential surface (without reference number) in the stepped bore 26 in the nozzle body 20 in a fluid-tight manner. Between the radially inner circumferential surface (without reference numeral) of the closing piston 58 and the control rod 30 of the valve element 28, a gap 60 is present, which ensures a radial clearance between closing piston 58 and valve element 28. On the control rod 30 is, in FIG. 1 below the closing piston 58, a support ring 62 rigidly attached. This extends radially outward slightly further than the gap 60, so that the closing piston 58 can be supported on it.
  • the closing piston 58 is acted upon by a transmission sleeve 64, which is also pushed with radial play on the control rod 30 and disposed between closing piston 58 and sealing sleeve 38.
  • a Compression spring 66 braced between transmission sleeve 64 and sealing sleeve 38.
  • a flow restrictor 68 is arranged, which is designed as a throttle bore and a located between the high-pressure port 42 and closing piston 58 portion 40a of the annular space 40 with a lying between the closing piston 58 and sealing seat 33 portion 40b of the annular space 40 connects.
  • the flow restrictor 68 is simply formed by an annular gap between closing piston 58 and injector 12 or a groove in the radially outer surface of the closing piston 58.
  • a relief valve 70 formed by a spring-loaded check valve is integrated in the closing piston 58, which opens toward the region 40b of the annular space 40 between closing piston 58 and sealing seat 33 and in this open state connects the region 40a and 40b of the annular space 40 with one another.
  • the relief valve 70 comprises a valve ball 72, which is acted upon by a valve spring 74 against a formed on the closing piston 58 sealing portion 76.
  • the fuel injector 10 comprises a fluid path which from the high-pressure port 42 via the region 40a of the annular space 40, by means of the flow restrictor 68 and optionally also by means of the (open) relief valve 70 via the closing piston 58 to the region 40b of the annular space 40, ie leads over the flattened areas 36 to the sealing seat 33.
  • the relief valve 70 is thus arranged fluidly parallel to the flow restrictor 68.
  • the fuel injector 10 operates as follows: In the idle state, with the switching valve 54 closed, the high fuel pressure prevailing at the high-pressure port 42 prevails in the entire annular space 40. This is also transmitted via the inlet throttle 50 into the hydraulic control chamber 48. The corresponding force resultant on the hydraulic control surface 46 acts on the valve element 28 in the closing direction of the valve element 28 against the sealing seat 33. The fluid path described above thus ends at the sealing seat 33, fuel can not escape through the fuel outlet channels 22. The relief valve 70 is closed.
  • the electromagnetic switching valve 54 is opened, whereby fuel flows from the hydraulic control chamber 48 via the outlet throttle 52 to the low pressure port 56.
  • the pressure in the hydraulic control chamber 48 drops and, correspondingly, the force-resultant force acting on the hydraulic control surface 46 and acting in the closing direction decreases. If the forces acting in the closing direction on the valve element 28 sink below the force acting on the pressure surface 37 in the opening direction, the valve element 28 moves upwards.
  • the high fuel pressure in the region 40b now also acts on the lower conical tip 72 of the nozzle needle 32, as a result of which additional forces in the opening direction act on the valve element 28.
  • fuel injector 10 shown by the function of the relief valve 70 avoided: namely, this is a maximum possible pressure difference between the areas 40a and 40b of the annular space 40 is set.
  • this pressure difference between these two spaces 40a and 40b exceeds the opening pressure difference of the relief valve 70, it opens, relieving the pressure in the space 40a into the space 40b.
  • the electromagnetic switching valve 54 is closed, whereby the outflow of fuel from the hydraulic control chamber 48 to the low pressure port 56 is terminated. Fuel flows into the hydraulic control chamber 48 via the inlet throttle 50, so that the pressure there again rises approximately to that level which prevails in the annular space 40a or at the high-pressure port 42.
  • the pressure in the region 40b of the annular space 40 is slightly lower than in the region 40a and thus also somewhat lower than in the hydraulic control chamber 48
  • the pressure surface 37 and the conical tip 72 now outweigh the forces acting in the closing direction on the valve element 28 - also because the closing piston 58 additionally acts in the closing direction force - so that they again in the direction moved to the sealing seat 33. If the nozzle needle 32 approaches the sealing seat 33, the pressure at the conical tip 72 drops due to throttling effects, as a result of which the forces acting in the opening direction on the valve element 28 decrease again and the closing process is accelerated.
  • FIG. 2 An alternative embodiment of a fuel injector 10 is shown in FIG. 2 shown.
  • elements and regions which have equivalent functions to elements and regions which have already been explained in connection with a preceding figure bear the same reference numerals.
  • FIG. 2 shown fuel injector 10 differs from that of FIG. 1 in that the closing piston 58 is not arranged in the region of the nozzle body 20, but in the area of the injector body 18, in the vicinity of the sealing sleeve 38. A transmission sleeve is therefore not necessary.
  • the closing piston 58 is integrally formed with the control rod 30, so there is no gap between the control rod 30 and the closing piston 58.
  • valve element 72 of the relief valve 70 is formed by the closing piston 58 itself.
  • the sealing portion 76, with which the closing piston 58 cooperates, is realized by a collar on the control rod 30.
  • the closing piston 58 is acted upon by a spring 74, which is supported on a support ring 62.
  • the closing piston 58 lifts off from the annular collar 76, whereby fuel in addition to the flow throttle 68th from area 40a into area 40b, which limits the pressure in annulus 40a.
  • the hydraulic force acting on the closing piston 58 and acting in the closing direction of the valve element 28 is transmitted via the spring 74 and the support ring 62 to the control rod 30 and the nozzle needle 32.
EP08103421A 2007-05-07 2008-04-08 Injecteur de carburant pour un moteur à combustion interne comprenant un système d'injection à rampe commune Withdrawn EP1990532A1 (fr)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
DE200710021330 DE102007021330A1 (de) 2007-05-07 2007-05-07 Kraftstoffinjektor für eine Brennkraftmaschine mit Common-Rail-Einspritzsystem

Publications (1)

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EP1990532A1 true EP1990532A1 (fr) 2008-11-12

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EP08103421A Withdrawn EP1990532A1 (fr) 2007-05-07 2008-04-08 Injecteur de carburant pour un moteur à combustion interne comprenant un système d'injection à rampe commune

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DE (1) DE102007021330A1 (fr)

Cited By (10)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2009132878A1 (fr) * 2008-04-28 2009-11-05 Robert Bosch Gmbh Systèmes d'injection de carburant à alimentation en carburant non étranglée vers les injecteurs
WO2009132879A2 (fr) * 2008-04-28 2009-11-05 Robert Bosch Gmbh Dispositif d'injection de carburant
EP2187034A1 (fr) * 2008-11-14 2010-05-19 Robert Bosch Gmbh Un injecteur de combustible avec élément d'étanchéité axial
WO2010121934A1 (fr) * 2009-04-20 2010-10-28 Continental Automotive Gmbh Ensemble soupape pour une soupape d'injection et soupape d'injection
WO2011101419A1 (fr) * 2010-02-18 2011-08-25 Continental Automotive Gmbh Soupape d'injection de carburant haute pression pour un moteur à combustion interne
WO2012163759A1 (fr) * 2011-05-30 2012-12-06 Robert Bosch Gmbh Ensemble buse pour un injecteur de carburant et injecteur de carburant
EP2818689A1 (fr) * 2013-06-27 2014-12-31 Robert Bosch Gmbh Soupape d'injection de carburant
WO2016091452A1 (fr) * 2014-12-09 2016-06-16 Delphi International Operations Luxembourg S.À R.L. Injecteur de carburant
EP3219974A1 (fr) * 2016-03-16 2017-09-20 Delphi International Operations Luxembourg S.à r.l. Injecteur de carburant
WO2017211485A1 (fr) * 2016-06-09 2017-12-14 Robert Bosch Gmbh Injecteur

Families Citing this family (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102008002528A1 (de) 2008-06-19 2009-12-24 Robert Bosch Gmbh Kraftstoff-Injektor
DE102008002527A1 (de) * 2008-06-19 2009-12-24 Robert Bosch Gmbh Kraftstoff-Injektor

Citations (5)

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Publication number Priority date Publication date Assignee Title
US6189509B1 (en) * 1997-07-16 2001-02-20 Cummins Wartsila S.A. Device for injecting fuel into a diesel engine
DE20202338U1 (de) * 2002-02-14 2002-05-29 Cummins Inc Kraftstoffinjektor mit geschlossener Düse mit verbesserter Steuerbarkeit
DE10348928A1 (de) * 2003-10-18 2005-05-12 Bosch Gmbh Robert Kraftstoffeinspritzvorrichtung
US20060186227A1 (en) * 2005-02-22 2006-08-24 Siemens Vdo Automotive Corporation Common rail injector with active needle closing device
DE102006036447A1 (de) 2006-08-04 2008-02-07 Robert Bosch Gmbh Injektor für ein Kraftstoffeinspritzsystem

Patent Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US6189509B1 (en) * 1997-07-16 2001-02-20 Cummins Wartsila S.A. Device for injecting fuel into a diesel engine
DE20202338U1 (de) * 2002-02-14 2002-05-29 Cummins Inc Kraftstoffinjektor mit geschlossener Düse mit verbesserter Steuerbarkeit
DE10348928A1 (de) * 2003-10-18 2005-05-12 Bosch Gmbh Robert Kraftstoffeinspritzvorrichtung
US20060186227A1 (en) * 2005-02-22 2006-08-24 Siemens Vdo Automotive Corporation Common rail injector with active needle closing device
DE102006036447A1 (de) 2006-08-04 2008-02-07 Robert Bosch Gmbh Injektor für ein Kraftstoffeinspritzsystem

Cited By (22)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2009132878A1 (fr) * 2008-04-28 2009-11-05 Robert Bosch Gmbh Systèmes d'injection de carburant à alimentation en carburant non étranglée vers les injecteurs
WO2009132879A2 (fr) * 2008-04-28 2009-11-05 Robert Bosch Gmbh Dispositif d'injection de carburant
WO2009132879A3 (fr) * 2008-04-28 2010-01-14 Robert Bosch Gmbh Dispositif d'injection de carburant
EP2187034A1 (fr) * 2008-11-14 2010-05-19 Robert Bosch Gmbh Un injecteur de combustible avec élément d'étanchéité axial
KR101709518B1 (ko) 2009-04-20 2017-02-23 콘티넨탈 오토모티브 게엠베하 인젝션 밸브 및 인젝션 밸브용 밸브 조립체
KR20120012817A (ko) * 2009-04-20 2012-02-10 콘티넨탈 오토모티브 게엠베하 인젝션 밸브 및 인젝션 밸브용 밸브 조립체
CN102405344A (zh) * 2009-04-20 2012-04-04 欧陆汽车有限责任公司 用于喷射阀的阀组件和喷射阀
EP2246554A1 (fr) * 2009-04-20 2010-11-03 Continental Automotive GmbH Ensemble de soupape pour soupape d'injection et soupape d'injection
WO2010121934A1 (fr) * 2009-04-20 2010-10-28 Continental Automotive Gmbh Ensemble soupape pour une soupape d'injection et soupape d'injection
US8919372B2 (en) 2009-04-20 2014-12-30 Continental Automotive Gmbh Valve assembly for an injection valve and injection valve
US9316190B2 (en) 2010-02-18 2016-04-19 Continental Automotive Gmbh High-pressure fuel injection valve for an internal combustion engine
WO2011101419A1 (fr) * 2010-02-18 2011-08-25 Continental Automotive Gmbh Soupape d'injection de carburant haute pression pour un moteur à combustion interne
WO2012163759A1 (fr) * 2011-05-30 2012-12-06 Robert Bosch Gmbh Ensemble buse pour un injecteur de carburant et injecteur de carburant
CN103582751A (zh) * 2011-05-30 2014-02-12 罗伯特·博世有限公司 用于燃料喷射器的喷嘴组件及燃料喷射器
EP2818689A1 (fr) * 2013-06-27 2014-12-31 Robert Bosch Gmbh Soupape d'injection de carburant
WO2016091452A1 (fr) * 2014-12-09 2016-06-16 Delphi International Operations Luxembourg S.À R.L. Injecteur de carburant
CN107002611A (zh) * 2014-12-09 2017-08-01 德尔福国际业务卢森堡公司 燃料喷射器
US10337478B2 (en) 2014-12-09 2019-07-02 Delphi Technologies Ip Limited Fuel injector
CN107002611B (zh) * 2014-12-09 2020-01-10 德尔福国际业务卢森堡公司 燃料喷射器
EP3219974A1 (fr) * 2016-03-16 2017-09-20 Delphi International Operations Luxembourg S.à r.l. Injecteur de carburant
EP3399177A1 (fr) * 2016-03-16 2018-11-07 Delphi International Operations Luxembourg S.à r.l. Injecteur de carburant
WO2017211485A1 (fr) * 2016-06-09 2017-12-14 Robert Bosch Gmbh Injecteur

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