EP1703119A1 - Buse d'injection de carburant - Google Patents

Buse d'injection de carburant Download PDF

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Publication number
EP1703119A1
EP1703119A1 EP06100017A EP06100017A EP1703119A1 EP 1703119 A1 EP1703119 A1 EP 1703119A1 EP 06100017 A EP06100017 A EP 06100017A EP 06100017 A EP06100017 A EP 06100017A EP 1703119 A1 EP1703119 A1 EP 1703119A1
Authority
EP
European Patent Office
Prior art keywords
coupler
piston
booster
injection nozzle
needle
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
EP06100017A
Other languages
German (de)
English (en)
Other versions
EP1703119B1 (fr
Inventor
Stefan Schuerg
Wolfgang Stoecklein
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 EP1703119A1 publication Critical patent/EP1703119A1/fr
Application granted granted Critical
Publication of EP1703119B1 publication Critical patent/EP1703119B1/fr
Expired - Fee Related 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
    • 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
    • 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
    • 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
    • F02M61/167—Means for compensating clearance or thermal expansion
    • 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

Definitions

  • the invention relates to an injection nozzle for an internal combustion engine, in particular in a motor vehicle, according to the preamble of claim 1.
  • Such an injection nozzle is known from EP 1 174 615 A2 and comprises a nozzle needle, which is mounted so that it can be adjusted in terms of stroke in a nozzle body and with which an injection of fuel through at least one injection hole can be controlled.
  • the injector includes a booster piston which is drive coupled to an actuator such that a stroke adjustment of the actuator necessarily causes an identical stroke adjustment of the booster piston.
  • a coupler piston is provided which has a first coupler surface and a second coupler surface.
  • the booster piston is equipped with a translator surface that is hydraulically coupled to the first coupler face.
  • the nozzle needle is provided with a control surface which is hydraulically coupled to the second coupler face.
  • a driver coupling is provided in the known injection nozzle, at least at the beginning an opening stroke of the booster piston serving to open the nozzle needle mechanically mechanically drives the coupler piston with the nozzle needle.
  • the opening movement of the nozzle needle is positively and mechanically coupled at least at the beginning of the opening stroke of the booster piston directly and mechanically with the opening movement of the coupler piston.
  • the nozzle needle thus speaks very directly during the opening process and moves at least at the beginning of the opening stroke synchronously to the coupler piston.
  • the injector according to the invention with the features of the independent claim has the advantage that there is no mechanical coupling between the nozzle needle and coupler piston, so that the coupler piston and nozzle needle are decoupled from each other in terms of their tolerances.
  • the production of the injection nozzle is thereby considerably simplified.
  • tolerances between the booster piston and coupler piston are to be maintained in the injector according to the invention in order to realize the driver coupling, but these tolerances are less narrow and are in particular in the usual tolerance ranges.
  • the driver coupling proposed according to the invention thus acts between the booster piston and the coupler piston and thus at least at the beginning of the opening stroke of the booster piston leads to a direct drive positive coupling between booster piston and coupler piston.
  • the coupler piston directly performs the stroke of the booster piston and thus directly the stroke of the actuator, at least at the beginning of the opening stroke of the booster piston.
  • the stroke displacement of the coupler piston causes the pressure drop across the second coupler face and thus directly on the control face, whereby the nozzle needle is driven to open solely by the hydraulic opening forces.
  • the nozzle body may have an intermediate plate which separates a needle region in which the nozzle needle is arranged from a control region in which the actuator, the booster piston and the coupler piston are arranged.
  • a control path which hydraulically couples the second coupler surface to the control surface is then passed through the intermediate plate.
  • an injection nozzle 1 comprises a nozzle body 2, in which a nozzle needle 3 is mounted in a stroke-adjustable manner in a suitable manner.
  • the injection nozzle 1 is used for injecting fuel into an injection space 4 of an internal combustion engine, which can be arranged in particular in a motor vehicle.
  • the injection of fuel through at least one spray hole 5 can be controlled by means of the nozzle needle 3.
  • the nozzle needle 3 acts for this purpose with a needle seat 6 together. In its initial position or closed position or blocking position shown here, the nozzle needle 3 is seated in the needle seat 6 and thereby separates the at least one injection hole 5 from a feed path 7 which supplies the at least one injection hole 5 under high pressure fuel.
  • This feed path 7 extends within the nozzle body 2 and is connected to a Fuel supply 8 connected, which is symbolized here by an arrow.
  • the feed path 7 in this case runs in the nozzle body 2 in such a way that the inner components of the injection nozzle 1 virtually float in the fuel under high pressure.
  • the fuel supply 8 comprises a common high-pressure line, to which the supply paths 7 of a plurality of injection nozzles 1 are connected.
  • the nozzle needle 3 is here part of a needle assembly 9, which consists of several members, which are jointly adjustable stroke.
  • the individual members may be loosely attached to each other or attached to each other or made of one piece.
  • the needle needle 3 or needle assembly 9 cooperates with a closing compression spring 10, which biases the nozzle needle 3 or the needle assembly 9 in the closing direction, that is to say into the needle seat 6.
  • the closing compression spring 10 is supported at one end on the needle assembly 9 or on the nozzle needle 3 and the other end of a sealing sleeve 11, which coaxially surrounds the needle assembly 9 at one end remote from the at least one injection hole 5.
  • this sealing sleeve 11 is pressed against an intermediate plate 12 at the same time, which forms a part of the nozzle body 2.
  • the sealing sleeve 11 encloses a control chamber 13, which is also axially bounded by the intermediate plate 12.
  • the needle needle 3 and the needle assembly 9 has a control surface 14, which also limits the control chamber 13.
  • the control surface 14 is remote from the at least one injection hole 5, so that pressure forces acting thereon introduce closing forces into the nozzle needle 3 or into the needle assembly 9 closing forces.
  • the intermediate plate 12 divides the nozzle body 2 into a needle region 15 located in the figures below and a control region 16 arranged above the intermediate plate 12.
  • the needle needle 3 or needle assembly 9 arranged in the needle region 15 is mechanically disposed of the components of the injection nozzle 1 arranged in the control region 16 decoupled.
  • the components of the needle portion 15 are independent of the components of the control portion 16 in terms of tolerances, which simplifies manufacturing.
  • the connection path 7 is passed through the intermediate plate 12 in a suitable manner.
  • the injection nozzle 1 contains in its control region 16 an actuator 17, which is preferably designed as a piezoelectric actuator, and depending on its energy level or the applied current has a varying axial length, wherein the axial direction is parallel to the stroke direction of the nozzle needle 3.
  • the actuator 17 At a first energy level, which is also referred to below as energization, the actuator 17 has a large or its largest axial extent. In contrast, it has a smaller or its smallest axial extent at a second energy level, which is also referred to below as Entstromung.
  • the actuator 17 is drive-coupled with a booster piston 18, such that a stroke of the actuator 17 inevitably causes the same stroke on the booster piston 18.
  • the booster piston 18 is mounted in an adjustable stroke in a bearing sleeve 19 which is axially supported on the intermediate plate 12. Furthermore, an opening compression spring 20 is provided, which is supported at one end to the bearing sleeve 19 and the other end to a disc 21, via which the booster piston 18 is fixedly connected to the actuator 17.
  • the opening pressure spring 20 thus drives the booster piston 18 in a direction away from the nozzle needle 3 direction.
  • the booster piston 18 has a booster surface 22 defining a booster space 23.
  • the booster chamber 23 is formed within the bearing sleeve 19 and thus enclosed by the bearing sleeve 19.
  • a coupler piston 24 is provided, which is likewise mounted in a stroke-adjustable manner in the bearing sleeve 19.
  • the coupler piston 24 has a first coupler surface 25, which faces away from the at least one spray hole 5, and a second coupler surface 26, which faces the at least one spray hole 5.
  • the first coupler surface 25 also limits the translator space 23 and faces the translator surface 22.
  • Translator surface 22 and first coupler surface 25 are hydraulically coupled together.
  • the second coupler surface 26 is hydraulically coupled to the control surface 14.
  • the second coupler surface 26 defines a coupler space 27, which is also delimited from the intermediate plate 12 by the second coupler surface 26 and bordered by the bearing sleeve 19.
  • the intermediate plate 12 contains at least one control channel 28, via which the control chamber 13 communicates with the coupler space 27.
  • the hydraulic coupling between the control surface 14 and second coupler surface 26 takes place Thus, via the control chamber 13, through the control channel 28 and the coupler space 27.
  • a control path which hydraulically couples the second coupler surface 26 with the control surface 14 thus comprises the control chamber 13, the coupler chamber 27 and the at least one control channel 28 and thus by the intermediate plate 12 passed.
  • a driver coupling 29 is now also provided, which is designed such that it mechanically drives the coupler piston 24 to the booster piston 18 at least at the beginning of an opening stroke of the booster piston 18, which serves to open the nozzle needle 3.
  • the coupler piston 24 is stroke-displaced synchronously with the transmission piston 18 at least at the beginning of the opening stroke of the booster piston 18.
  • the driver coupling 29 comprises in the embodiments shown here, a first driver contour 30 which is fixedly connected to the booster piston 18, and a second driver contour 31 which is fixedly connected to the coupler piston 24.
  • the booster piston 18 includes a first driver space 32, within which the first driver contour 30 is formed in the form of an undercut.
  • the coupler piston 24 has a rod 33 which projects axially from the coupler piston 24 and projects into the first driver chamber 32. There, the rod 33 carries a head 34, on which the second driver contour 31 is formed so that it engages behind the first driver contour 30 within the first driver space 32.
  • the first driving space 32 is open to the coupler piston 24 and is hydraulically coupled to the booster chamber 23, which takes place for example via at least one connecting channel 35.
  • a driving space is also provided, which is not formed in the booster piston 18, but in the coupler piston 24 and is hereinafter referred to as the second driving space 36.
  • the second Mitauerraum 36 the second Mitauerkontur 31 is then arranged and suitably designed as an undercut.
  • the first driver contour 30 is then on a head 37 of a rod 38th formed, which is fixedly connected to the booster piston 18 and immersed in the second driving space 36. Accordingly, the first cam follower 30 engages within the second Mitauerraums 36, the second Mitauerkontur 31.
  • the second Mit sacrificeraum 36 communicates in particular via at least one connecting channel 39 with the booster chamber 23 and is open to the booster piston 18 out.
  • two driving spaces are provided, namely the first driving space 32 formed in the booster piston 18 and the second driving space 36 formed in the coupler piston 24.
  • the first driving contour 30 is formed in the first driving space 32, in particular in the form of an undercut.
  • the second driver contour 31 is arranged here in the second booster chamber 36, preferably in the form of an undercut.
  • a coupling member 40 is provided, which has a rod 41 which projects at both axial ends in each of the driver chambers 32 and 36 and there has a head 42 and 43, respectively, the respective as an undercut trained driver contour 30 and 31 engages behind.
  • At least one return spring 44 is also provided, which is supported at one end on the booster piston 18 and the other end on the coupler piston 24 and which drives said pistons 18, 24 axially away from one another.
  • a distance 45 between the booster piston 18 and coupler piston 24 can increase.
  • the maximum adjustable distance 45 is defined or limited by the driver coupling 29.
  • the driver contours 30, 31 are either directly as in the embodiments of FIGS. 1 and 2 or indirectly via the coupler member 40 as shown in FIG. 3 with each other.
  • the driver coupling 29 is also designed so that a relative displacement between the booster piston 18 and coupler piston 24 is possible, in such a way that the distance 45 thereby reduced. This is achieved in the embodiments shown here in that the respective heads 34, 37, 42 and 43 only loosely rest on the respective undercut 30, 31 and thereby move into the respective driver space 32 or 36 and from the respective undercut 30, 31 can lift off or remove. This relative movement between the booster piston 18 and coupler piston 24 then takes place counter to the pressure force of the return spring 44th
  • the actuator 17 is energized and has its greatest axial extent.
  • the nozzle needle 3 is seated in its seat 6 and blocks the at least one injection hole 5.
  • the coupler piston 24 has its greatest distance 45 from the booster piston 18.
  • the driver contours 30, 31 of the driver coupling 29 are engaged.
  • This pressure equalization can be realized, for example, by targeted play or by targeted leaks in the area of the bearings of the booster piston 18, coupler piston 24 and nozzle needle 3 or NadelVERS 9.
  • suitable throttle bores may be provided, which connect the respective spaces with the feed path 7.
  • the actuator 17 is de-energized, causing it to contract.
  • the actuator 17 is in this case operated inversely, ie, an energization of the actuator 17 causes a closing of the nozzle needle 3, while a flow of the actuator 17 causes the opening of the nozzle needle 3. Since the axial length of the actuator 17 is reduced by its inverse operation, the compulsorily coupled booster piston 18 performs an opening stroke. At the beginning of this opening stroke, which is directed away from the least one injection hole 5, the driver coupling 29 inevitably forces a stroke adjustment of the coupler piston 24. In this way, the second coupler surface 26 moves away from the intermediate plate 12, whereby the volume of the coupler chamber 27 increases.
  • the opening of the nozzle needle 3 is due to the driver coupling 29 very directly, which makes it possible to specify the opening time of the nozzle needle 3 quite accurately.
  • a ratio of second coupling surface 26 to control surface 14 a desired translation of the stroke adjustment of the actuator 17 and the opening stroke of the nozzle needle 3 can be adjusted.
  • the second coupler surface 26 is then the same size as the control surface 14.
  • the actuator 17 is operated longer.
  • the translator surface 22 is usually larger than the first coupler surface 25. This has the consequence that during the opening stroke of the booster piston 18, the volume of the booster chamber 23 increases. Accordingly, it comes in the interpreter room 23 to a pressure drop. While the pressure drop in the coupler chamber 27 is substantially compensated or limited (at least initially) by the opening movement of the nozzle needle 3, the pressure in the booster chamber 23 continues to decrease until the forces acting on the coupler surface 26 on the coupler piston 24 are opposite those at The forces acting on the first coupler surface 25 predominate. From this force balance, the opening stroke of the coupler piston 24 is faster than the opening stroke of the booster piston 18, so that the coupler piston 24 moves toward the booster piston 18 while reducing the distance 45. This relative movement is made possible by the driver coupling 29 according to the invention. As a result, the pressure drop in the coupler chamber 27 increases again, which again accelerates the nozzle needle 3 in the opening direction.
  • the ratio of control surface 14 to translator surface 22 is now appropriate expedient, this translator surface 22 is significantly larger than the control surface 14, so that a certain stroke of the actuator 17 a correspondingly larger stroke on the Nozzle needle 3 generated.
  • the nozzle needle 3 can thus be opened extremely quickly. This is advantageous for the realization of large injection quantities with comparatively short injection times.
  • the large ratio ensures a comparatively short length for the actuator 17, whereby the injector 1 can build a comparatively compact overall.
  • the actuator 17 is energized again, whereby its length is increased and the booster piston 18 is again adjusted in the direction of at least one injection hole 5.
  • the volume of the translator space 23 is reduced, thereby increasing the pressure therein.
  • This increase in pressure then causes a corresponding adjustment movement of the coupler piston 24 in the direction of the at least one injection hole 5, wherein this adjusting movement is supported by the return spring 44.
  • FIGS. 2 and 3 operate analogously to the variant of FIG. 1 and therefore need not be explained in detail.
  • the needle area 15 can be produced completely independently of the control area 16 with regard to tolerances and alignment of the movable components contained therein, since in particular no mechanical coupling between the nozzle needle 3 and the coupler piston 24 has to be realized.
  • the embodiment of the driver coupling 29 exclusively in the control region 16 can be implemented much simpler, since the tolerances to be maintained within the control region 16 can lie in a larger range.

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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)
EP20060100017 2005-02-28 2006-01-02 Buse d'injection de carburant Expired - Fee Related EP1703119B1 (fr)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
DE200510008972 DE102005008972A1 (de) 2005-02-28 2005-02-28 Einspritzdüse

Publications (2)

Publication Number Publication Date
EP1703119A1 true EP1703119A1 (fr) 2006-09-20
EP1703119B1 EP1703119B1 (fr) 2008-04-16

Family

ID=36051564

Family Applications (1)

Application Number Title Priority Date Filing Date
EP20060100017 Expired - Fee Related EP1703119B1 (fr) 2005-02-28 2006-01-02 Buse d'injection de carburant

Country Status (2)

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EP (1) EP1703119B1 (fr)
DE (2) DE102005008972A1 (fr)

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2012055464A3 (fr) * 2010-10-30 2012-06-21 Daimler Ag Injecteur piézoélectrique
EP2813698A1 (fr) * 2013-06-10 2014-12-17 Robert Bosch Gmbh Soupape d'injection de combustible

Families Citing this family (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102005026514B4 (de) * 2005-02-18 2008-12-24 Robert Bosch Gmbh Einspritzdüse
DE102012212266B4 (de) * 2012-07-13 2015-01-22 Continental Automotive Gmbh Fluidinjektor
DE102012212264B4 (de) 2012-07-13 2014-02-13 Continental Automotive Gmbh Verfahren zum Herstellen eines Festkörperaktuators

Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP0952333A2 (fr) * 1998-04-18 1999-10-27 DaimlerChrysler AG Injecteur à combustible pour systèmes d'injection de combustible
EP1174615A2 (fr) 2000-07-18 2002-01-23 Delphi Technologies, Inc. Injecteur de combustible
WO2002006665A1 (fr) * 2000-07-15 2002-01-24 Robert Bosch Gmbh Soupape d'injection de carburant
WO2003018993A1 (fr) * 2001-08-20 2003-03-06 Robert Bosch Gmbh Soupape d'injection de carburant
DE10259730A1 (de) * 2002-12-19 2004-07-01 Robert Bosch Gmbh Brennstoffeinspritzventil
WO2004109091A1 (fr) * 2003-06-10 2004-12-16 Robert Bosch Gmbh Buse d'injection pour des moteurs a combustion interne

Patent Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP0952333A2 (fr) * 1998-04-18 1999-10-27 DaimlerChrysler AG Injecteur à combustible pour systèmes d'injection de combustible
WO2002006665A1 (fr) * 2000-07-15 2002-01-24 Robert Bosch Gmbh Soupape d'injection de carburant
EP1174615A2 (fr) 2000-07-18 2002-01-23 Delphi Technologies, Inc. Injecteur de combustible
WO2003018993A1 (fr) * 2001-08-20 2003-03-06 Robert Bosch Gmbh Soupape d'injection de carburant
DE10259730A1 (de) * 2002-12-19 2004-07-01 Robert Bosch Gmbh Brennstoffeinspritzventil
WO2004109091A1 (fr) * 2003-06-10 2004-12-16 Robert Bosch Gmbh Buse d'injection pour des moteurs a combustion interne

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2012055464A3 (fr) * 2010-10-30 2012-06-21 Daimler Ag Injecteur piézoélectrique
EP2813698A1 (fr) * 2013-06-10 2014-12-17 Robert Bosch Gmbh Soupape d'injection de combustible

Also Published As

Publication number Publication date
EP1703119B1 (fr) 2008-04-16
DE502006000618D1 (de) 2008-05-29
DE102005008972A1 (de) 2006-08-31

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