EP1869310B1 - Brennstoffeinspritzventil - Google Patents

Brennstoffeinspritzventil Download PDF

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Publication number
EP1869310B1
EP1869310B1 EP06724919A EP06724919A EP1869310B1 EP 1869310 B1 EP1869310 B1 EP 1869310B1 EP 06724919 A EP06724919 A EP 06724919A EP 06724919 A EP06724919 A EP 06724919A EP 1869310 B1 EP1869310 B1 EP 1869310B1
Authority
EP
European Patent Office
Prior art keywords
housing part
housing
fuel injection
injection valve
fuel
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.)
Not-in-force
Application number
EP06724919A
Other languages
German (de)
English (en)
French (fr)
Other versions
EP1869310A1 (de
Inventor
Siegfried Ruthardt
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 EP1869310A1 publication Critical patent/EP1869310A1/de
Application granted granted Critical
Publication of EP1869310B1 publication Critical patent/EP1869310B1/de
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
    • 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
    • F02M55/00—Fuel-injection apparatus characterised by their fuel conduits or their venting means; Arrangements of conduits between fuel tank and pump F02M37/00
    • F02M55/004—Joints; Sealings
    • 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
    • F02M61/168—Assembling; Disassembling; Manufacturing; Adjusting
    • 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
    • F02M2200/00—Details of fuel-injection apparatus, not otherwise provided for
    • F02M2200/80—Fuel injection apparatus manufacture, repair or assembly
    • F02M2200/8076—Fuel injection apparatus manufacture, repair or assembly involving threaded members
    • 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
    • F02M2200/90—Selection of particular materials
    • F02M2200/9053—Metals

Definitions

  • the invention relates to a fuel injector, in particular an injector for fuel injection systems of air-compressing, self-igniting internal combustion engines, according to the preamble of claim 1.
  • Such a fuel injection valve is through the DE 100 62 960 A known.
  • This fuel injection valve has a valve housing, which is composed of a first housing part and at least one second housing part, wherein a housing wall of the first housing part is connected in a connecting region at least indirectly with a housing wall of the second housing part.
  • the housing wall of the first housing part is at least indirectly supported in the connecting region on the housing wall of the second housing part at least in the radial direction.
  • the housing wall of the second housing part is designed reinforced at least in the connection region.
  • the supply of fuel under high pressure in the fuel injection valve is effected by a centrally extending in the first housing part channel and a central channel in an injection valve member.
  • the fuel injection valve according to the invention with the features of claim 1 has the advantage that the fuel through the interior of the valve housing can be easily fed without an additional fuel channel is required.
  • the at least radial support of the housing wall of the first housing part on the housing wall of the second housing part results in a secure seal, which is supported by the pressure prevailing in the interior of the high pressure.
  • the first housing part is connected to the second housing part by means of a clamping nut. Further, it is advantageous that the first housing part has an external thread, that the clamping nut has an internal thread, that the internal thread of the clamping nut for connecting the first housing part with the second housing part is engaged and that the clamping nut is designed so that a uniform possible power transmission takes place via the engaging threads of the first housing part and the clamping nut. In a conventional screw the majority of the holding force is applied by the first threads.
  • the stresses caused by the high pressure of the fuel can be optimized, in particular evenly distributed, so that stress peaks are avoided and a uniform stress load occurs, which additionally reduces the stresses occurring due to the internal pressure.
  • the design of the clamping nut can be determined by means of a method making use of the finite element method. Specifically, the clamping nut, at least in the area of the front engaged threads a smaller wall thickness than in the area of the rear engaging threads.
  • the second housing part has a conical support shoulder and that the first housing part is supported on the support shoulder.
  • an advantageous support of the first housing part is achieved in the radial direction, in which due to the internal pressure of the fuel, the sealing force and thus the sealing function is supported at the interface between the housing parts.
  • the second housing part in the connection region has a greater wall thickness than the first housing part, so that the support effect is further improved.
  • the second housing part may be formed of a material having an increased strength.
  • the second housing part may for example be made of a high-alloy steel, so that in terms of the production of the entire fuel injection valve, the production costs and the production costs are optimized.
  • Fig. 1 shows an embodiment of a fuel injection valve 1 of the invention in a schematic axial sectional view.
  • the fuel injection valve 1 can serve, in particular, as an injector for fuel injection systems of mixture-compression, self-igniting internal combustion engines.
  • the fuel injection valve 1 is suitable for commercial vehicles or passenger cars.
  • a preferred use of the fuel injection valve 1 is for a fuel injection system with a common rail, which leads diesel fuel under high pressure to a plurality of fuel injection valves 1.
  • the fuel injection valve 1 according to the invention is also suitable for other applications.
  • the fuel injection valve 1 has a valve housing 4 consisting of a first housing part 2 and a second housing part 3.
  • the first housing part 2 is designed as an injector body 2 and the second housing part 3 is designed as a nozzle body 3.
  • the fuel injection valve 1 has a valve seat body 5, which is integrally connected to the second housing part 3.
  • a valve seat surface 6 is formed, which cooperates with a valve closing body 8 which can be actuated by a valve needle 7 to form a sealing seat.
  • the valve closing body 8 is formed integrally with the valve needle 7.
  • the valve needle 7 has a valve needle piston 9 which is guided in a valve needle guide 14 of the second housing part 3.
  • the valve needle 7 is arranged substantially inside the second housing part 3.
  • the first housing part 2 of the fuel injection valve 1 has a fuel inlet nozzle 10 shown in simplified form, to which a fuel line (not shown) can be connected in order to connect the fuel injection valve 1 to a common rail or another device.
  • the fuel inlet nozzle 10 has a fuel passage 11, via which fuel can be introduced into an inner space 12 of the valve housing 4 of the fuel injection valve 1.
  • the interior 12 is predetermined by the first housing part 2 and the second housing part 3.
  • a fuel chamber 13 is still formed, which is connected via provided in the valve needle guide 14 passage openings 15, 16 with the interior 12, so that the introduced through the fuel passage 11 into the fuel injection valve 1 via the fuel chamber 12 and the Passage openings 15, 16 passes into the fuel chamber 13.
  • the pressure of the fuel can be, for example, 200 MPa (2000 bar).
  • a piezoelectric actuator 17 is arranged, which consists of several layers.
  • an actuator base 18 is added, which is supported on an inner side 19 of the first housing part 2.
  • an electrical connection point 20 is formed, to which an electrical supply line (not shown) can be connected to the fuel injection valve 1 in order to connect electrical lines 21, 22 via the electrical supply line to a control unit or the like ,
  • the electrical lines 21, 22 are guided through the first housing part 2 and the actuator base 18 in the interior 12 of the valve housing 4 and via electrical contacts 23, 24th connected to the active layers of the actuator 17.
  • an actuator head 30 is attached to the actuator 17.
  • the actuator 17 When the actuator 17 is acted upon by a control voltage, the actuator 17 is charged, so that it expands in an axial direction 31 against the force of a valve spring 32, the actuator 17 via the actuator head 30 and a pressure plate 33, a valve piston 34 in FIG the axial direction 31 is adjusted.
  • Fig. 1 illustrated embodiment results from the charge of the actuator 17 in Fig. 1 illustrated starting position of the valve piston 34, in which the fuel injection valve 1 is in the closed state, as further explained below.
  • valve piston 34 is guided on the side facing away from the pressure plate 33 in a control chamber sleeve 35, which is supported with an edge 36 on a throttle plate 37, whereby a control chamber 38 is formed.
  • the control chamber sleeve 35 is acted upon by the valve spring 32, which is supported on the one hand on the throttle plate 33 and on the other hand on an end face of the control chamber sleeve 35.
  • the fuel injection valve 1 In the non-actuated state of the fuel injection valve 1 is located in the control chamber 38 fuel at high pressure.
  • the control chamber 38 is connected via a formed in the throttle plate 37 throttle 39 with another control chamber 40 in connection.
  • the control chamber 40 is formed by the valve needle piston 9, the throttle plate 37 and a further control chamber sleeve 41, which is supported on the one hand via an edge 42 on the throttle plate 37 and on the other hand acted upon by a further valve spring 43.
  • the valve spring 43 is supported on the one hand on the control chamber sleeve 41 and on the other hand at one with the Valve needle piston 9 fastened ring element 44.
  • valve piston 34, the control chamber sleeve 35, the throttle plate 37, the control chamber sleeve 41, the valve needle piston 9 and the valve springs 32, 43 are part of a hydraulic coupler 45.
  • hydraulic coupler 45 are caused in particular during operation of the fuel injection valve 1 due to temperature changes Changes in length of components of the fuel injection valve 1 compensated.
  • a leakage gap is formed between the valve piston 34 and the control chamber sleeve 35 and between the valve needle piston 9 and the control chamber sleeve 41, which allow a fuel flow and fuel discharge over a period of time which is large compared to an operating cycle.
  • the actuator 17 For actuating the fuel injection valve 1, the actuator 17 is discharged by lowering the control voltage, so that the actuator contracts against the axial direction 31. Due to the force of the valve spring 32, a displacement of the piston 34 connected to the pressure plate 33 takes place counter to the axial direction 31, so that the pressure of the fuel in the control chamber 38 is considerably reduced. Due to the resulting pressure difference, pressure equalization takes place via the throttle 39 between the control chamber 40 and the control chamber 38, which also reduces the pressure of the fuel in the control chamber 40.
  • valve needle piston 9 of the valve needle 7 The force acting on a pressure shoulder 50 on the valve needle piston 9 of the valve needle 7, which is caused by the high pressure of the fuel in the fuel chamber 13, then outweighs the oppositely acting force, which is composed of the force of the valve spring 43 and the pressure generated by the fuel in the control chamber 40, acting on the valve needle piston 9 force.
  • the valve needle piston 9 is displaced counter to the axial direction 31, so that the valve closing body 8 connected to the valve needle 7 lifts off from the valve seat surface 6 formed on the valve seat body 5 and the sealing seat formed between the valve seat surface 6 and the valve closing body 8 is opened.
  • fuel from the fuel chamber 13 can be injected via the open sealing seat and the spray hole 52 into a (not shown) combustion chamber of an internal combustion engine.
  • the actuator 17 is recharged by increasing the control voltage, so that the actuator 17 expands in the axial direction 31 and the pressure of the fuel in the control chamber 38 is raised again by the corresponding adjustment of the valve piston 34.
  • the fuel flows from the control chamber 38 via the throttle 39 into the control chamber 40, so that the pressure of the fuel in the control chamber 40 increases.
  • the force which is composed of the force of the valve spring 43 and the force acting on the valve pin piston 9 by the pressure of the fuel in the control chamber 40, exceeds the force which results from the pressure of the fuel passing through the pressure shoulder 50 and acts on the valve closing body 8 on the valve needle 7, there is an adjustment of the valve needle 7 in the axial direction 31 in the in the Fig. 1 illustrated starting position in which the fuel injection valve 1 is closed again.
  • the first housing part 2 is connected to the second housing part 3 in a connection region 60.
  • a housing wall 61 of the first housing part 2 on an external thread 62 which is in engagement with an internal thread 63 of a clamping nut 64.
  • the second housing part 3 has a housing wall 65, wherein a shoulder 66 of the housing wall 65 is formed, which will engage behind the clamping nut 64.
  • the clamping nut 64 is supported on the shoulder 66, so that the first housing part 2 is acted upon in the axial direction 31 against a conical support shoulder 67 of the second housing part 3 with a connecting force.
  • the conical support shoulder 67 which is formed on the housing wall 65 of the second housing part 3, the cross-section, in particular the diameter, of the interior 12 of the valve housing 4 in the axial direction 31 is reduced.
  • the components of the fuel injection valve 1, for which a large installation space is required, are accommodated in the region of the large cross section of the interior.
  • a large installation space is required for the actuator 17, the valve spring 42, the control chamber sleeve 35, the valve piston 34 and the throttle plate 37.
  • the housing wall 61 of the first housing part 2 is configured in the connection area 60 with a reduced outer diameter.
  • the diameter of the inner space 12, which is predetermined by the first housing part 2 is constant in the axial direction 31, so that the wall thickness of the first housing part 2 in the connection area 60 is reduced.
  • the housing wall 61 of the first housing part 2 Due to the high pressure of the fuel in the interior 12, therefore, high voltages occur in the housing wall 61 of the first housing part 2 in the connection region 60.
  • the open end of the first housing part 2 of the valve housing 4 in the connection region 60 is a weak point for the design of the tightness and strength.
  • the housing wall 61 of the first housing part 2 is supported at least indirectly on the housing wall 65 of the second housing part 3 in the radial direction 68 off.
  • the housing wall 65 of the second housing part 3 is made reinforced in the connection area 60.
  • the voltages occurring in the housing wall 61 of the first housing part 2 in the connection region 60 due to the high pressure of the fuel can be absorbed by the housing wall 65 of the second housing part 3, so that the above-mentioned weak point is eliminated. Specifically, this can considerably increase the pressure of the fuel in the interior 12 and, for example, assume values of 200 MPa (2000 bar).
  • the sealing effect between the housing wall 61 of the first housing part 2 and the housing wall 65 of the second housing part 3 is applied on the one hand by acting in the axial direction 31 clamping force of the clamping nut 64.
  • On the other hand results from the pressure of the fuel in the interior 12 an additional loading of the housing wall 61 of the first housing part 2 in the radial direction 68 against the conical support shoulder 67, resulting in an additional, self-reinforcing sealing effect.
  • the housing wall 65 of the second housing part 3 can be configured, at least in the area of the conical support shoulder 67, from a material having increased strength.
  • a further reduction of the occurring stresses results from the design of the clamping nut 64.
  • the geometrical design of the clamping nut 64 is by means of a Finite element method so determined that stress spikes are avoided and a uniform stress load occurs, which additionally reduces the stresses caused by the internal pressure.
  • the force distribution in the engagement region of the threads 62, 63 is improved by the clamping nut 64 in the region 69 of the front engaged threads has a smaller wall thickness than in the region 70 of the rear engaging threads, which, for example, by the in the Fig. 1 illustrated bulbous configuration of the clamping nut 64 in the connection region 60 can be achieved.
  • the invention is not limited to the described embodiments.
  • the invention is also suitable for a fuel injection valve 1, which has a valve housing 4 composed of more than two housing parts 2, 3.
  • the invention is also suitable for fuel injection valves 1 with other actuating mechanisms.
  • the hydraulic coupler 45 designed as a repeater in the exemplary embodiment can also be embodied as a power amplifier or can only assume the function of temperature compensation.

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  • Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Manufacturing & Machinery (AREA)
  • Fuel-Injection Apparatus (AREA)
EP06724919A 2005-04-06 2006-03-03 Brennstoffeinspritzventil Not-in-force EP1869310B1 (de)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102005015735A DE102005015735A1 (de) 2005-04-06 2005-04-06 Brennstoffeinspritzventil
PCT/EP2006/060423 WO2006106021A1 (de) 2005-04-06 2006-03-03 Brennstoffeinspritzventil

Publications (2)

Publication Number Publication Date
EP1869310A1 EP1869310A1 (de) 2007-12-26
EP1869310B1 true EP1869310B1 (de) 2008-11-26

Family

ID=36607450

Family Applications (1)

Application Number Title Priority Date Filing Date
EP06724919A Not-in-force EP1869310B1 (de) 2005-04-06 2006-03-03 Brennstoffeinspritzventil

Country Status (7)

Country Link
US (1) US8181893B2 (ja)
EP (1) EP1869310B1 (ja)
JP (1) JP4638938B2 (ja)
KR (1) KR101092701B1 (ja)
AT (1) ATE415556T1 (ja)
DE (2) DE102005015735A1 (ja)
WO (1) WO2006106021A1 (ja)

Families Citing this family (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102008042154A1 (de) * 2008-09-17 2010-03-18 Robert Bosch Gmbh Brennstoffeinspritzventil
DE102009001131A1 (de) * 2008-12-09 2010-06-10 Robert Bosch Gmbh Kraftstoffinjektor
DE102011081176A1 (de) * 2011-08-18 2013-02-21 Robert Bosch Gmbh Ventil zum Zumessen eines strömenden Mediums
DE102012203607A1 (de) * 2012-03-07 2013-09-12 Robert Bosch Gmbh Ventil zum Zumessen eines Fluids
DE102012208075A1 (de) * 2012-05-15 2013-11-21 Man Diesel & Turbo Se Injektor für eine Kraftstoffversorgungsanlage einer Brennkraftmaschine sowie Kraftstoffversorgungsanlage
JP6482981B2 (ja) * 2015-07-31 2019-03-13 日立オートモティブシステムズ株式会社 流量制御弁

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DE10114216B4 (de) * 2001-03-23 2006-11-30 Robert Bosch Gmbh Streckgrenzengesteuerte Schraubverbindung
DE10139622B4 (de) * 2001-03-29 2018-06-14 Robert Bosch Gmbh Einspritzventil
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Also Published As

Publication number Publication date
JP4638938B2 (ja) 2011-02-23
DE502006002203D1 (de) 2009-01-08
US8181893B2 (en) 2012-05-22
KR101092701B1 (ko) 2011-12-09
KR20070116248A (ko) 2007-12-07
ATE415556T1 (de) 2008-12-15
US20080185462A1 (en) 2008-08-07
JP2008534859A (ja) 2008-08-28
EP1869310A1 (de) 2007-12-26
WO2006106021A1 (de) 2006-10-12
DE102005015735A1 (de) 2006-10-12

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