EP0065282A1 - Buse d'injection de combustible pour moteurs à combustion interne - Google Patents

Buse d'injection de combustible pour moteurs à combustion interne Download PDF

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Publication number
EP0065282A1
EP0065282A1 EP82104180A EP82104180A EP0065282A1 EP 0065282 A1 EP0065282 A1 EP 0065282A1 EP 82104180 A EP82104180 A EP 82104180A EP 82104180 A EP82104180 A EP 82104180A EP 0065282 A1 EP0065282 A1 EP 0065282A1
Authority
EP
European Patent Office
Prior art keywords
hollow needle
valve
needle
injection nozzle
nozzle body
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
EP82104180A
Other languages
German (de)
English (en)
Other versions
EP0065282B1 (fr
Inventor
Kurt Seifert
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
Priority claimed from DE19813120044 external-priority patent/DE3120044A1/de
Priority claimed from DE19813130621 external-priority patent/DE3130621A1/de
Application filed by Robert Bosch GmbH filed Critical Robert Bosch GmbH
Publication of EP0065282A1 publication Critical patent/EP0065282A1/fr
Application granted granted Critical
Publication of EP0065282B1 publication Critical patent/EP0065282B1/fr
Expired 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
    • 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
    • F02M61/18—Injection nozzles, e.g. having valve seats; Details of valve member seated ends, not otherwise provided for
    • F02M61/1806—Injection nozzles, e.g. having valve seats; Details of valve member seated ends, not otherwise provided for characterised by the arrangement of discharge orifices, e.g. orientation or size
    • F02M61/182—Discharge orifices being situated in different transversal planes with respect to valve member direction of movement
    • 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
    • F02M45/00—Fuel-injection apparatus characterised by having a cyclic delivery of specific time/pressure or time/quantity relationship
    • F02M45/02—Fuel-injection apparatus characterised by having a cyclic delivery of specific time/pressure or time/quantity relationship with each cyclic delivery being separated into two or more parts
    • F02M45/04—Fuel-injection apparatus characterised by having a cyclic delivery of specific time/pressure or time/quantity relationship with each cyclic delivery being separated into two or more parts with a small initial part, e.g. initial part for partial load and initial and main part for full load
    • F02M45/08—Injectors peculiar thereto
    • F02M45/086—Having more than one injection-valve controlling discharge orifices
    • 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
    • F02M61/042—The valves being provided with fuel passages
    • F02M61/045—The valves being provided with fuel discharge orifices
    • 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
    • F02M61/08—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 the valves opening in direction of fuel flow

Definitions

  • the invention is based on a fuel injection nozzle according to the preamble of the main claim.
  • Injection nozzles of this type are distinguished by the fact that the section of the fuel channel which adjoins the valve seat downstream and is used for further fuel preparation and spray jet shaping can be designed and dimensioned relatively freely without obstruction by a closing member, and in addition that the fuel passes through the installation space for the closing spring is performed so that special measures to prevent or eliminate leak oil are eliminated.
  • These injection nozzles therefore combine the advantages of nozzles with an inwardly opening valve needle (I nozzle) with those of nozzles with an outwardly opening valve needle (A nozzle), without, however, having their disadvantages.
  • the hollow needle is supported in the closed position via the valve seat on the valve needle ab, which in turn rests on a shoulder fixed to the housing.
  • the valve needle is pressed against the housing-fixed shoulder by a spring.
  • the valve seat is relatively heavily stressed and, in addition, in the open position of the valve, an exact position of the valve needle with respect to the hollow needle is not guaranteed because the valve needle is only held firmly on the stop fixed to the housing. It also appears disadvantageous that the bearing gap between the hollow needle and the nozzle body is not shielded against the combustion chamber of the machine in the closed position of the valve, so that the sliding properties of the hollow needle can deteriorate over time.
  • valve seat is no longer loaded by the closing spring acting on the hollow needle, but by the valve spring pressing against the valve needle, which can be dimensioned weaker than the closing spring.
  • valve spring pressing against the valve needle which can be dimensioned weaker than the closing spring.
  • an exact position of the valve needle with respect to the hollow needle is ensured in the open position of the valve, because this position is determined by two shoulders fixed to the housing, that is to say by positive locking.
  • the stop shoulder for the hollow needle and its counter shoulder are designed according to the features of claim 2 is particularly advantageous.
  • the bearing gap between the hollow needle and the nozzle body is covered in the closed position of the hollow needle against the combustion chamber of the machine, so that proper guidance of the hollow needle in the nozzle body is ensured for a long time.
  • the hollow needle can be designed as a closing member which cooperates with the nozzle body and opens outwards to control further spray openings.
  • This arrangement is particularly advantageous in the case of cross-section-controlled hole and pin nozzles depending on the valve stroke.
  • the fuel guide can be freely designed downstream of the valve seat (s) and in particular divided into several spray holes or spray hole groups, the cross-section and direction of which can be adapted to the requirements of the respective application.
  • the hollow needle can control a first spray hole cross section with the nozzle body and a second spray hole cross section with the valve needle.
  • the means for retaining the valve needle with respect to the hollow needle moving in the opening direction can be arranged such that they come into effect immediately after the opening movement of the hollow needle begins. In this case, that of Hollow needle and valve needle controlled spray hole cross section opened, while the other spray hole cross section is only released after a partial stroke of the hollow needle.
  • the injection sequence can also be controlled so that the means for retaining the valve needle come into effect only after a first partial stroke of the hollow needle corresponding to a pre-injection phase. It is thereby achieved that the first spray hole cross section, which is arranged further at the edge of the combustion chamber, is opened by the hollow needle, and that the second spray hole cross section, which is arranged further towards the center of the combustion chamber, is only released by the valve needle at the beginning of the main injection phase. It is also achieved that after the first partial stroke of the hollow needle with the injection quantity, the closing pressure and thus the fuel pressure in front of the valves increases suddenly, so that in the partial and full load range of the internal combustion engine a perfect preparation of the fuel is guaranteed.
  • the function of a conventional perforated nozzle with an inwardly opening valve needle is obtained with respect to the second spray hole cross section, without taking measures to eliminate leakage oil.
  • the hollow needle can expediently be designed according to the features of claim 11 and control a plurality of spray holes forming the first spray hole cross section in the nozzle body.
  • the first spray hole cross section is formed by transverse bores in the hollow needle, which emerge from the guide bore of the nozzle body after a partial stroke of the hollow needle.
  • Figures 1 to 4 each show a partial section through one of the exemplary embodiments.
  • the injection nozzle according to FIG. 1 has a nozzle body 10 which is clamped to a nozzle holder 14 by a screw body 12.
  • a guide bore 16 for a hollow needle 18 and a bore 20 of larger diameter is formed in the nozzle body 10 and merges into the guide bore 16 on a shoulder 22.
  • a projection 24 of the nozzle holder 14 protrudes into the bore 20, which is provided with a bore 26 and at the front end with a smaller opening 28, the cross section of which has two surfaces.
  • a shoulder 30 fixed to the housing and having a circumferential contact surface is turned away from the injection-side end of the nozzle.
  • the hollow needle 18 has a longitudinal bore 36 extending from its upper end face 32, which leads to a conical valve seat 38, which is followed downstream by a blind hole 40 with spray holes 41, 42 leading to the outside in the front end of the hollow needle 18 designed as a tip 43.
  • the hollow needle 18 is provided with a section 48 which is slightly weakened in the outer diameter and which, in the vicinity of its transition to an un weakened section 50 guided in the nozzle body 10, has a transverse bore 52.
  • the section 48 is followed at the top by a head 54 provided with two surfaces, which, with the required play, protrudes into the opening 28 and secures the hollow needle 18 against rotation.
  • a conical annular shoulder 56 is further formed in the vicinity of the valve seat 38, which cooperates with a correspondingly shaped counter shoulder 58 at the front end of the nozzle body 10.
  • a closing spring 60 is arranged in the bore 20, which is supported at the bottom on a flange 62 of a bush 64 resting on the shoulder 22, which surrounds the section 48 of the hollow needle 18 with play. At the upper end, the closing spring 60 engages a pressure ring 66 which abuts an annular shoulder 68 of the hollow needle 18 formed between the section 48 and the head 54. The highlighted by the closing spring 60.
  • Called upward stroke (closing stroke) of the hollow needle 18 is limited by the shoulders 56 and 58 to the hollow needle 18 and nozzle body 10, which are designed as valve surfaces and seal the bearing gap between the latter and the nozzle body 10 against the combustion chamber in the closed position of the hollow needle 18.
  • a valve needle 70 is slidably guided in the longitudinal bore 36 of the hollow needle 18 and has a sealing cone 72 which cooperates with the valve seat 38 at the end on the injection side.
  • the sealing cone 72 is formed on a section 74 of the valve needle 70 which is somewhat weakened in diameter and which merges on a shoulder 76 into the unattenuated section of the valve needle 70.
  • the shoulder 76 lies somewhat above the transverse bore 52 in the hollow needle 18, so that the annular space 78 formed between the section 74 of the valve needle 70 and the wall of the longitudinal bore 36 in the hollow needle 18 via the transverse bore 52, the annular play between the hollow needle 18 and the bushing 64 , and via one or more transverse bores 80 in the bushing 64 is connected to the bore 20 in the nozzle body 10.
  • the valve needle 70 protrudes a bit from the hollow needle 18 at the top and is provided there with an annular collar 82, on the upper end face of which a valve spring 84 engages, which is supported on a threaded bushing 86 screwed into the bore 26.
  • the valve spring 84 endeavors to press the valve needle 70 against the valve seat 38 in the hollow needle 18. This is achieved in the closed position of the hollow needle 18 shown in the drawing, in which the collar 82 of the valve needle 70 is still removed from the shoulder 30 on the nozzle holder 14 by the stroke h 1 .
  • the collar 82 lies against the shoulder 30, after which the valve needle 70 is prevented from moving along with the hollow needle 18.
  • the total stroke h 2 of the hollow needle 18 is limited by the bushing 64, on the upper end of which the pressure ring 66 comes to rest.
  • the threaded bushing 86 is provided with a bore 88 for supplying the fuel.
  • the fuel path then leads via the bore 26 and an edge recess 90 surrounding the shoulder 30 in the neck 24 of the nozzle holder 14 into the bore 20, where the fuel acts on the end face 32 of the hollow needle 18 and on this force opposing the closing spring 60 in the direction of Combustion chamber.
  • the fuel passes through the transverse bore 52 in the hollow needle 18 into the annular space 78 between the hollow needle 18 and the valve needle 70 and exerts a further force on the hollow needle 18 via the narrow annular surface 92 above the valve seat 38.
  • the fuel also exerts a downward-acting resulting force on the valve needle 70 which, in support of the valve spring 84, presses the valve needle 70 against the valve seat 38.
  • the hollow needle When the fuel pressure rises at the beginning of an injection stroke, the hollow needle is moved downward out of the nozzle body 10 by compressing the closing spring 60. Under the influence of the valve spring 84 and the fuel pressure, the valve needle 70 can only follow this movement by the small distance h 1 , after which the collar 82 strikes the shoulder 30 and forces a relative movement of the valve needle 70 with respect to the hollow needle 18 which is moving further. This relative movement has approximately the same effect in relation to the fuel control in the injection region as an inwardly moving valve needle with a fixed valve seat.
  • the arrangement described has the advantage that a leakage oil flow in the guide of the valve needle 70 or the hollow needle 18 is not disruptive or does not occur and therefore no means for its removal need to be provided.
  • the closing spring 60 returns the hollow needle 18 to the starting position, in which it strikes with its shoulder 56 on the shoulder 58 of the nozzle body 10.
  • the two shoulders 56 and 58 then form a valve-like closure which prevents the combustion gases from accessing the bearing gap between the hollow needle 18 and the nozzle body 10.
  • the valve needle 70 hits the valve seat 38, after which the fuel discharge from the spray holes 41, 42 is interrupted.
  • the valve needle 70 then lifts from the shoulder 30 by the stroke h 1 .
  • the stroke h 1 is dimensioned just so large in view of the tolerances to be permitted in production that the valve needle 70 can rest safely on the valve seat 38 in the closed position of the hollow needle 18.
  • the exemplary embodiment according to FIG. 2 corresponds to that according to FIG. 1 in the details described so far, except that the hollow needle 18 itself forms the closing member for a valve device which controls a second group of spray holes 94 and 96 which run in the nozzle body 10 .
  • the hollow needle 18 is provided with a transverse bore 98 and an annular groove 100 in the circumference of the jacket, into which the transverse bore 98 opens at both ends.
  • the collar 82 of the valve needle 70 is here removed from the shoulder 30 fixed to the housing by the partial stroke h 1 , which is now used not only to eliminate manufacturing tolerances but also to control the two groups 41, 42 and 94, 96 of the spray holes as a function of the stroke.
  • the spray holes 94 which in their entirety result in a first spray hole cross section I, are first produced via the annular groove 100 and opened 96, the valve spring 84 holding the valve needle 70 against the valve seat 38 of the hollow needle 18.
  • the valve needle 70 is retained relative to the latter, as a result of which the spray holes 41, 42, which in their entirety result in a second spray hole cross section II, are opened.
  • the processes described take place in the reverse order.
  • the arrangement could also be made by appropriate selection of the distance of the transverse bore 98 from the sealing cone 72 on the valve needle 70 so that first the sealing cone 72 lifts off the valve seat 38 and only then is the second group 94, 96 of the spray holes opened.
  • the injection nozzle according to FIG. 2 also has the advantage that when opening the spray holes 41, 42 or the second spray hole cross section II and the associated sudden increase in the overall spray hole cross section, a pressure jump occurs in the closing force, which occurs due to the interception of the force of the valve spring 84 is caused and advantageously ensures that the fuel is then processed and atomized as well as in the first partial stroke h 1 .
  • the exemplary embodiment according to FIG. 3 differs from the one described above only in that the shoulder 56 of the hollow needle 18 is arranged upstream of the first spray hole cross section I and cooperates with an inner shoulder 58 of the nozzle body 10.
  • the shoulders 56 and 58 which cooperate in the closed position like a valve, additionally seal the annular space 78 against the first spray hole cross section I.
  • the spray sequence can also be reversed with regard to the spray hole cross sections I and II.
  • the exemplary embodiment according to FIG. 4 is a further modification of the exemplary embodiment according to FIG. 2.
  • the spray hole cross section I is formed here by spray holes 110 and 112 in the hollow needle 18, which in the closed position of the hollow needle 18 is covered by an overlap 114 and by that between the shoulders 56 and 58 valve seat formed on the hollow needle 18 and nozzle body 10 are sealed off from the combustion chamber.
  • the spray holes 110 ′ and 112 emerge from the guide bore in the nozzle body 10, so that the channels 46, 47 provided in the injection nozzle according to FIG. 2 are unnecessary in the nozzle body 10.
  • the injection nozzle according to FIG. 4 also has the advantage that the spray hole cross-section I is additionally sealed in the closed position of the hollow needle 18 by the valve seat formed between the shoulders 56 and 58.
  • the sequence of opening the spray hole cross sections I and II can be chosen as desired by coordinating the forward stroke h 1 and overlap 114.

Landscapes

  • Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Fuel-Injection Apparatus (AREA)
EP82104180A 1981-05-20 1982-05-13 Buse d'injection de combustible pour moteurs à combustion interne Expired EP0065282B1 (fr)

Applications Claiming Priority (4)

Application Number Priority Date Filing Date Title
DE19813120044 DE3120044A1 (de) 1981-05-20 1981-05-20 Kraftstoff-einspritzduese fuer brennkraftmaschinen
DE3120044 1981-05-20
DE3130621 1981-08-01
DE19813130621 DE3130621A1 (de) 1981-08-01 1981-08-01 Kraftstoff-einspritzduese fuer brennkraftmaschinen

Publications (2)

Publication Number Publication Date
EP0065282A1 true EP0065282A1 (fr) 1982-11-24
EP0065282B1 EP0065282B1 (fr) 1985-10-09

Family

ID=25793394

Family Applications (1)

Application Number Title Priority Date Filing Date
EP82104180A Expired EP0065282B1 (fr) 1981-05-20 1982-05-13 Buse d'injection de combustible pour moteurs à combustion interne

Country Status (3)

Country Link
US (1) US4526323A (fr)
EP (1) EP0065282B1 (fr)
DE (1) DE3266767D1 (fr)

Cited By (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US5199647A (en) * 1990-12-21 1993-04-06 Zexel Corporation Fuel injection nozzle
EP1087129A3 (fr) * 1999-09-23 2003-04-16 Delphi Technologies, Inc. Injecteur de carburant
CN110023616A (zh) * 2016-11-30 2019-07-16 日立汽车系统株式会社 燃料喷射装置
CN113775433A (zh) * 2020-06-10 2021-12-10 上海汽车集团股份有限公司 一种发动机燃烧系统

Families Citing this family (14)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE3429471A1 (de) * 1984-08-10 1986-02-13 L'Orange GmbH, 7000 Stuttgart Kraftstoffeinspritzvorrichtung fuer eine brennkraftmaschine
WO1988008081A1 (fr) * 1987-04-07 1988-10-20 Kabushiki Kaisha Komatsu Seisakusho Moteur a combustion interne
JPH09177640A (ja) * 1995-12-15 1997-07-11 Caterpillar Inc 高サック容積を有する燃料噴射器による燃焼排気ガス清浄化システムとその方法
US6000638A (en) * 1997-11-03 1999-12-14 Caterpillar Inc. Apparatus for strengthening a fuel injector tip member
GB9903496D0 (en) * 1999-02-16 1999-04-07 Lucas Ind Plc Fuel injector
GB9905231D0 (en) * 1999-03-09 1999-04-28 Lucas Ind Plc Fuel injector
US6173913B1 (en) 1999-08-25 2001-01-16 Caterpillar Inc. Ceramic check for a fuel injector
GB0021296D0 (en) * 2000-08-30 2000-10-18 Ricardo Consulting Eng A dual mode fuel injector
EP1333967B1 (fr) 2000-10-24 2008-03-12 Trexel, Inc. Soupape pour moulage par injection
US6886762B2 (en) * 2001-12-20 2005-05-03 Caterpillar Inc. Nozzle insert for dual mode fuel injector
US6843434B2 (en) * 2003-02-28 2005-01-18 Caterpillar Inc Dual mode fuel injector with one piece needle valve member
US7032566B2 (en) * 2003-05-30 2006-04-25 Caterpillar Inc. Fuel injector nozzle for an internal combustion engine
CN101307741B (zh) * 2008-07-01 2010-06-16 浙江大学 发动机燃料缸内直接喷射装置
EP3122468B1 (fr) * 2014-03-28 2022-06-22 Deyang Hou Injecteur de carburant souple pour injection de carburant simple et double

Citations (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US1333541A (en) * 1916-10-09 1920-03-09 Samuel P Cowardin Fuel-injector for internal-combustion engines
DE828327C (de) * 1950-04-02 1952-01-17 Bosch Gmbh Robert Einspritzventil

Family Cites Families (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2063709A (en) * 1933-03-25 1936-12-08 Taylor John Leonard Atomizer
GB633857A (en) * 1947-01-27 1949-12-30 Istvan Gyorgy Kammer Improvements in fuel injectors for internal combustion engines
FR1040381A (fr) * 1951-08-08 1953-10-14 Injecteur pour moteur à explosion
JPS56501096A (fr) * 1979-09-04 1981-08-06
DE2943896A1 (de) * 1979-10-31 1981-05-14 Robert Bosch Gmbh, 7000 Stuttgart Kraftstoffeinspritzduese fuer brennkraftmaschinen
IT1150819B (it) * 1981-04-14 1986-12-17 Lucas Ind Plc Ugelli di iniezione di combustibile

Patent Citations (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US1333541A (en) * 1916-10-09 1920-03-09 Samuel P Cowardin Fuel-injector for internal-combustion engines
DE828327C (de) * 1950-04-02 1952-01-17 Bosch Gmbh Robert Einspritzventil

Cited By (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US5199647A (en) * 1990-12-21 1993-04-06 Zexel Corporation Fuel injection nozzle
EP1087129A3 (fr) * 1999-09-23 2003-04-16 Delphi Technologies, Inc. Injecteur de carburant
CN110023616A (zh) * 2016-11-30 2019-07-16 日立汽车系统株式会社 燃料喷射装置
CN113775433A (zh) * 2020-06-10 2021-12-10 上海汽车集团股份有限公司 一种发动机燃烧系统

Also Published As

Publication number Publication date
US4526323A (en) 1985-07-02
DE3266767D1 (en) 1985-11-14
EP0065282B1 (fr) 1985-10-09

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