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EP1692392A1 - Injecteur de carburant a commande de pointeau directe - Google Patents

Injecteur de carburant a commande de pointeau directe

Info

Publication number
EP1692392A1
EP1692392A1 EP04762764A EP04762764A EP1692392A1 EP 1692392 A1 EP1692392 A1 EP 1692392A1 EP 04762764 A EP04762764 A EP 04762764A EP 04762764 A EP04762764 A EP 04762764A EP 1692392 A1 EP1692392 A1 EP 1692392A1
Authority
EP
European Patent Office
Prior art keywords
pressure
valve member
fuel injector
injection valve
section
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
EP04762764A
Other languages
German (de)
English (en)
Other versions
EP1692392B1 (fr
Inventor
Friedrich Boecking
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 EP1692392A1 publication Critical patent/EP1692392A1/fr
Application granted granted Critical
Publication of EP1692392B1 publication Critical patent/EP1692392B1/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
    • F02M51/00—Fuel-injection apparatus characterised by being operated electrically
    • F02M51/06—Injectors peculiar thereto with means directly operating the valve needle
    • F02M51/0603—Injectors peculiar thereto with means directly operating the valve needle using piezoelectric or magnetostrictive operating means
    • 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
    • F02M2200/00—Details of fuel-injection apparatus, not otherwise provided for
    • F02M2200/16—Sealing of fuel injection apparatus not otherwise provided for
    • 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
    • F02M2200/00—Details of fuel-injection apparatus, not otherwise provided for
    • F02M2200/70—Linkage between actuator and actuated element, e.g. between piezoelectric actuator and needle valve or pump plunger
    • F02M2200/703—Linkage between actuator and actuated element, e.g. between piezoelectric actuator and needle valve or pump plunger hydraulic
    • 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

Definitions

  • Fuel injectors are used to supply the combustion chambers of internal combustion engines with fuel.
  • the injection pressure is provided via a high-pressure accumulator. Due to the large fuel volume in the high-pressure accumulator compared to the injection quantity, pressure fluctuations during the injection process are avoided.
  • the fuel injectors are operated hydraulically with the fuel made available via the high-pressure accumulator.
  • Fuel injectors as used in the prior art for high-pressure storage systems are known, for example, from Mollenhauer, Handbuch Dieselmotoren, 2nd edition, Springer Verlag, Berlin, 2002.
  • both the opening and the closing process are hydraulically controlled.
  • a control room in which fuel is under injection pressure is closed by a control valve.
  • the fuel pressure acts on the rear of a control piston, which acts into the control chamber, and on a pressure shoulder on an injection opening and a closing injection valve member.
  • the hydraulic force on the rear of the control piston is opposite to the hydraulic force that acts on the pressure shoulder. Due to the larger area on the control piston, the nozzle remains closed.
  • the control valve opens the control chamber, the pressure in the control chamber is reduced and the hydraulic force on the pressure shoulder becomes greater than the pressure force acting on the rear of the control piston. This causes the injection valve member to open.
  • the fuel is supplied both to the control chamber and to a pressure chamber, from which the fuel enters the combustion chamber via injection openings, via feed lines in the injector housing.
  • the fuel injectors known from the prior art with an injection valve member, control piston and control valve have a complex structure. Furthermore, it is necessary to manufacture fuel lines in the housing in the fuel injectors known from the prior art.
  • a fuel injector designed according to the invention for internal combustion engines with high-pressure fuel accumulator comprises a pressure intensifier and an injection valve member.
  • the injection valve member is preferably divided into a translator section, a guide section and a needle section, the needle section of the injection valve member closing at least one injection opening or releasing it for injecting fuel into a combustion chamber of the internal combustion engine.
  • the pressure booster of the fuel injector is accommodated in a booster housing and is supported on a spring element which surrounds the booster housing. The other side of the spring element is supported on a step formed on the translator housing, as a result of which the translator housing is fixed on a nozzle housing part surrounding the injection valve member.
  • Suitable spring elements are in particular tubular springs, but spiral springs or other ring-shaped spring elements can also be used.
  • the pressure intensifier, the translator housing and an actuator used to actuate the fuel injector are enclosed by an injector housing part, which is preferably non-positively connected to the nozzle housing part by means of a nozzle clamping nut.
  • the actuator used to control the fuel injector is preferably a piezo actuator.
  • electromagnets or hydraulic / mechanical actuators can also be used.
  • the translator section of the injection valve member is enclosed by a sleeve in which the injection valve member is guided.
  • a biting edge is formed on an end face of the sleeve facing the translator housing.
  • the biting edge of the sleeve is pressed against the shoulder of the translator housing by means of a spring element which acts on an end face of the sleeve opposite the biting edge. This creates a pressure- and therefore liquid-tight connection.
  • the other side of the spring element, which surrounds the booster section of the injection valve member, is supported on a ring which is arranged in a recess between the booster section and the guide section of the injection valve member.
  • the sleeve and the shoulder of the translator housing enclose a rotationally symmetrical translation space which is delimited on its side facing the actuator by a lower end face of the pressure booster and on its side facing the at least one injection opening of the fuel injector by an end face of the translator area of the injection valve member.
  • the fuel injector is operated hydraulically with fuel under system pressure.
  • the system pressure is preferably in the range from 1300 to 1600 bar.
  • the fuel under system pressure flows from the high-pressure fuel reservoir via a fuel supply line into an annular space surrounding the actuator.
  • the fuel flows out of the annular space through a gap between the pressure booster and the inner wall of the injector housing part into a first spring space surrounding the booster housing.
  • the fuel flows through at least one groove in the step of the booster housing on which the spring element is supported and which serves as a guide for the booster housing in the injector housing part, via grooves in the nozzle housing part and an annular gap between the inner wall of the nozzle housing part and the outer wall of the Sleeve in a second spring space.
  • the fuel passes from the second spring chamber along a bevel in the guide section of the injection valve member into a pressure chamber surrounding the needle section of the injection valve member.
  • the translation space is preferably filled by guide leakage between the inner surface of the sleeve and the translator section of the injection valve member or by guide leakage between the translator housing and the pressure translator.
  • the pressure in the translation room changes.
  • the pressure in the translation space can differ from the system pressure and thus also differ from the pressure in the annular gap surrounding the translation space. For this reason, it is necessary that the connection formed by the biting edge on the sleeve between the sleeve and the shoulder in the translator housing is pressure-tight.
  • the piezo actuator is energized to close the at least one injection opening through the needle section of the injection valve member.
  • the piezo actuator acts directly on an upper end face of the pressure intensifier, which means that when the piezo actuator is energized, it moves into the translation space. This reduces the volume of the translating space and increases the pressure in the translating space. Due to the increasing pressure in the translation room increases the hydraulic force acting on the face of the translator portion of the injector member. As a result, the injection valve member is moved in the direction of the at least one injection opening and closes it.
  • the spring element surrounding the booster section of the injection valve member acts as a support during the closing process.
  • the current supply to the piezo actuator is released.
  • the piezo crystals contract and the piezo actuator contracts.
  • the spring element surrounding the translator housing which is supported on a step on the pressure booster, acts to support the movement of the pressure booster.
  • the pressure in the translation space decreases. This also reduces the hydraulic force acting on the end face of the booster section of the injection valve member.
  • a hydraulic force acts on pressure stages on the injection valve member, which is opposite to the hydraulic force acting on the end face of the booster section of the injection valve member.
  • the piezo actuator is energized again, causing the piezo crystals to expand and the piezo actuator to lengthen.
  • the pressure intensifier is moved back into the translation space, whereby the volume of the translation space is reduced and the pressure in it increases. Due to the increasing pressure in the transmission space, the hydraulic force on the end face of the transmission section of the injection valve member increases. As soon as this force is greater than the hydraulic force acting on the pressure stages of the injection valve member in the opposite direction, the needle section of the injection valve member is put back into its sealing seat and thus closes the at least one injection opening.
  • the single figure shows a section through a fuel detector designed according to the invention.
  • FIG. 1 shows a fuel injector designed according to the invention.
  • a fuel injector 1 designed according to the invention fuel first comes from a fuel tank 2 by means of a high-pressure pump 3 via a high-pressure line 4 into a high-pressure fuel store 5.
  • Connections 6 are arranged on the high-pressure fuel store 5, which correspond to the number of cylinders of the crimping juicer.
  • Each of the connections 6 is connected via a fuel feed line 7 to a fuel injector 1 designed according to the invention.
  • the fuel injector 1 comprises a pressure booster 8 designed as a booster piston, which is guided in a booster housing 9, and an injection valve member 10.
  • the injection valve member 10 is in a booster section 11, a guide section 12 and a needle section 13 graded.
  • the pressure booster 8, the booster housing 9 and the injection valve member 10 are accommodated in a housing.
  • the housing is divided into an injector housing part 14 and a nozzle housing part 15.
  • the hijector housing part 14 and the nozzle housing part 15 are preferably connected non-positively by means of a nozzle clamping nut, not shown here.
  • the fuel injector 1 comprises an injection opening 16, which can be closed by the needle section 13 of the injection valve member 10.
  • the needle section 13 of the injection valve member 10 is placed against a sealing edge 17 arranged above the injection opening 16.
  • An exclusively axial movement for opening and closing the at least one injection opening 16 is ensured in that the injection valve member 10 is guided with its guide section 12 in a needle guide 18 arranged in the nozzle housing part 15.
  • the translator section 11 of the injection valve member 10 is enclosed by a sleeve 19, which also serves as a needle guide.
  • the sleeve 19 serves as a lateral delimitation of a translation space 20.
  • the sleeve 19 is provided with a biting edge 21 which is pressed against a shoulder 22 of the translator housing 9.
  • a liquid-tight and thus pressure-tight connection of the sleeve 19 to the shoulder 22 of the translator housing 9 is achieved.
  • a spring element 24 is supported on an end face 23 of the sleeve 19 opposite the biting edge 21.
  • the spring element 24 is annular and surrounds the booster section 11 of the injection valve member 10.
  • Suitable spring elements 24 are for example spiral springs, tube springs or other ring-shaped spring elements known to the person skilled in the art.
  • the spring element 24 is supported against a ring 25, which is preferably arranged in a recess 26, which is located between the translator section 11 and the guide section 12 of the injection valve member 10.
  • the translator housing 9 is surrounded by a second spring element 27, which is supported on one side on a step 28 on the translator housing 9 and on the other side on a ring 29 which rests on a step 30 on the pressure booster 8.
  • the step 28 serves at the same time as a guide for the translator housing 9 in the injector housing part 14.
  • the spring force applied by the spring element 27 fixes the translator housing 9 on a shoulder 31 on the nozzle housing part 15.
  • the spring element 27 is received in a first spring space 32, which is arranged between the translator housing 9 and the inner wall 33 of the injector housing part 14.
  • At least one groove 34 which is preferably axially aligned, is accommodated in step 28 of the converter housing 9.
  • the first spring space 32 with a translator section stands over the at least one groove 34, grooves 35 formed in the shoulder 31 on the nozzle housing part 15 and an at least one annular gap 36 which is formed between the outer wall 37 of the sleeve 19 and the inner wall 38 of the nozzle housing part 15 11 of the injection valve member 10 surrounding second spring space 39 in hydraulic connection.
  • the at least one groove 34 and the grooves 35 in the shoulder 31 of the nozzle housing part 15 are preferably aligned such that their positions correspond radially and axially.
  • the second spring space 39 is in hydraulic connection with a pressure chamber 41 via at least one channel, which is formed between at least one bevel 40 in the guide section 12 of the injection valve member 10 and the needle guide 18.
  • the fuel injector 1 is controlled via an actuator, which acts on an upper end face 42 of the pressure booster 8.
  • a piezo actuator 43 is preferably used as the actuator. Electromagnets or hydraulic / mechanical actuators are also suitable.
  • the fuel injector 1 is operated hydraulically with fuel under system pressure.
  • the fuel is provided by the high-pressure fuel reservoir 5.
  • the fuel flows via the fuel feed line 7 into an annular space 44 which surrounds the piezo actuator 43.
  • the fuel under system pressure reaches the first spring space 32 via a gap 45 between the pressure booster 8 and the inner wall 33 of the hijector housing part 14.
  • the fuel flows via the at least one groove 34, the grooves 35 in the shoulder 31 of the nozzle housing part 15 and the annular gap 36 into the second spring space 39.
  • system pressure prevails both in the annular space 44 and in the first spring space 32, the second spring space 39 and the pressure space 41.
  • the system pressure is preferably in the range from 1300 to 1600 bar.
  • the piezo actuator 43 is energized. As a result, the piezo crystals in the piezo actuator 43 expand and the piezo actuator 43 elongates. Because the piezo actuator 43 acts directly on the upper end face 42 of the pressure intensifier 8, the pressure intensifier 8 is moved into the translation space 20 with a lower end face 47 against the direction of movement identified by the arrow 46. As a result, the volume in the translation space 20 decreases, which increases the pressure therein. This increases the hydraulic force which acts on an end face 48 on the transmission section 11 of the injection valve member 10.
  • the hydraulic force acting on the end face 48 is a hydraulic force acting on a first pressure stage 49 on the ring 25, on a second pressure stage 50 between the guide section 12 and the needle section 13 of the injection valve member 10 and on a third pressure stage 51 in the needle section 13 of the injection valve member 10 opposite direction.
  • the injection valve member 10 is placed on the sealing edge 17 and thus closes the at least one injection opening 16 a combustion chamber 52 of the internal combustion engine.
  • the closing of the at least one injection opening 16 is supported by the spring force of the spring element 24.
  • the spring element 24 acts on an end face 54 of the ring 25 opposite the first pressure stage 49.
  • the current supply to the piezo actuator 43 is released.
  • the piezo crystals contract and the piezo actuator 43 contracts.
  • the pressure booster 8 moves in the direction of movement indicated by the arrow 46.
  • the lower end face 47 of the pressure intensifier 8 moves out of the translation space 20, which increases its volume. Due to the increasing volume of the translation space 20, the pressure in the translation space 20 decreases. Since the pressure in the translation space 20 drops below the system pressure, it is necessary for the connection between the sleeve 19 and the shoulder 22 is pressure-tight in the translator housing 9.
  • the translation space 20 is filled by means of guide leakage between the converter housing 9 and the pressure converter 8 or between the inside 43 of the sleeve 19 and the translation section 11 of the injection valve member 10.
  • Injection valve member 10 from the sealing edge 17 and thus releases the at least one injection opening 16.
  • fuel flows from the pressure chamber 41 into the combustion chamber 52 via the injection opening 16.
  • the piezo actuator 43 is energized again. As a result, the piezo crystals expand and the piezo actuator 43 lengthens. As a result, the pressure booster 8 moves back into the translation space 20 counter to the direction of movement indicated by the arrow 46, as a result of which the volume of the translation space 20 is reduced. This in turn increases the pressure in the translation space 20 and thus the hydraulic force acting on the end face 48 of the transmission section 11 of the injection valve member 10. At the same time, the hydraulic force acting on the first pressure stage 49, the second pressure stage 50 and the third pressure stage 51 remains constant since the second spring chamber 39 and the pressure chamber 41 are acted upon by a constant system pressure.

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

L'invention concerne un injecteur de carburant pour moteur à combustion interne, qui comprend un accumulateur de carburant haute pression (5), un multiplicateur de pression (8) et un obturateur d'injection (10) qui présente une partie de multiplication (11) et une partie pointeau (13) fermant au moins une ouverture d'injection (16). Le multiplicateur de pression (8) est logé dans un logement de multiplicateur (9) et repose sur un élément élastique (27) qui entoure le logement de multiplicateur (9). Ainsi, le logement de multiplicateur (9) est bloqué sur une partie de corps de buse (15) qui entoure l'obturateur d'injection (10).
EP04762764A 2003-11-12 2004-09-07 Injecteur de carburant a commande de pointeau directe Expired - Lifetime EP1692392B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE10352736A DE10352736A1 (de) 2003-11-12 2003-11-12 Kraftstoffinjektor mit direkter Nadeleinspritzung
PCT/DE2004/001982 WO2005050002A1 (fr) 2003-11-12 2004-09-07 Injecteur de carburant a commande de pointeau directe

Publications (2)

Publication Number Publication Date
EP1692392A1 true EP1692392A1 (fr) 2006-08-23
EP1692392B1 EP1692392B1 (fr) 2007-11-14

Family

ID=34608941

Family Applications (1)

Application Number Title Priority Date Filing Date
EP04762764A Expired - Lifetime EP1692392B1 (fr) 2003-11-12 2004-09-07 Injecteur de carburant a commande de pointeau directe

Country Status (7)

Country Link
US (1) US20070131800A1 (fr)
EP (1) EP1692392B1 (fr)
JP (1) JP4197337B2 (fr)
KR (1) KR20060103894A (fr)
BR (1) BRPI0409324A (fr)
DE (2) DE10352736A1 (fr)
WO (1) WO2005050002A1 (fr)

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DE102005032841B4 (de) * 2005-07-14 2017-06-14 Robert Bosch Gmbh Ziehender Betrieb eines Einspritzventils mit Spannungsabsenkung zwischen Einspritzungen
DE102006012078A1 (de) * 2005-11-15 2007-05-16 Bosch Gmbh Robert Kraftstoff-Einspritzvorrichtung für eine Brennkraftmaschine mit Kraftstoff-Direkteinspritzung
DE102006008647A1 (de) * 2006-02-24 2007-08-30 Robert Bosch Gmbh Kraftstoffinjektor mit direktbetätigbarer Düsennadel und variabler Aktorhubübersetzung
DE102006014251A1 (de) * 2006-03-28 2007-10-04 Robert Bosch Gmbh Kraftstoffinjektor
US20090057438A1 (en) * 2007-08-28 2009-03-05 Advanced Propulsion Technologies, Inc. Ultrasonically activated fuel injector needle
DE102007051554A1 (de) 2007-10-29 2009-04-30 Robert Bosch Gmbh Kraftstoffeinspritzventil für eine Brennkraftmaschine
JP4962872B2 (ja) * 2008-07-14 2012-06-27 株式会社デンソー 燃料噴射装置
DE102012212264B4 (de) 2012-07-13 2014-02-13 Continental Automotive Gmbh Verfahren zum Herstellen eines Festkörperaktuators
DE102012212266B4 (de) 2012-07-13 2015-01-22 Continental Automotive Gmbh Fluidinjektor
DE102013225384A1 (de) * 2013-12-10 2015-06-11 Robert Bosch Gmbh Kraftstoffinjektor
JP6443109B2 (ja) * 2015-02-17 2018-12-26 株式会社Ｓｏｋｅｎ 燃料噴射弁

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Also Published As

Publication number Publication date
DE10352736A1 (de) 2005-07-07
EP1692392B1 (fr) 2007-11-14
DE502004005534D1 (de) 2007-12-27
WO2005050002A1 (fr) 2005-06-02
JP2006513366A (ja) 2006-04-20
JP4197337B2 (ja) 2008-12-17
US20070131800A1 (en) 2007-06-14
BRPI0409324A (pt) 2006-04-25
KR20060103894A (ko) 2006-10-04

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