US3836080A - Fuel injection nozzle - Google Patents

Fuel injection nozzle Download PDF

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Publication number
US3836080A
US3836080A US00395828A US39582873A US3836080A US 3836080 A US3836080 A US 3836080A US 00395828 A US00395828 A US 00395828A US 39582873 A US39582873 A US 39582873A US 3836080 A US3836080 A US 3836080A
Authority
US
United States
Prior art keywords
valve
valve element
sac
valve seat
nozzle
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.)
Expired - Lifetime
Application number
US00395828A
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English (en)
Inventor
D Butterfield
A Marchetti
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.)
Ambac Industries Inc
AIL Corp
Original Assignee
Ambac Industries Inc
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 Ambac Industries Inc filed Critical Ambac Industries Inc
Priority to US00395828A priority Critical patent/US3836080A/en
Priority to CA205,531A priority patent/CA1020030A/en
Priority to DE2438014A priority patent/DE2438014A1/de
Priority to IT52625/74A priority patent/IT1019046B/it
Priority to FR7429178A priority patent/FR2243346B3/fr
Priority to JP49101825A priority patent/JPS60550B2/ja
Priority to GB3924174A priority patent/GB1477676A/en
Application granted granted Critical
Publication of US3836080A publication Critical patent/US3836080A/en
Assigned to AIL CORPORATION reassignment AIL CORPORATION ASSIGNMENT OF ASSIGNORS INTEREST. Assignors: UNITED TECHNOLOGIES AUTOMOTIVE HOLDINGS, INC.,
Anticipated expiration legal-status Critical
Expired - Lifetime 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

Definitions

  • the minimum fuel flow through the valve is controlled by the valve element configuration rather than the valve seat intersection with the sac as in the conventional nozzle.
  • the present nozzle construction facilitates manufacturing and permits a change of the valve delivery characteristics by modification of the valve element rather than the less accessible valve seat.
  • the present construction provides an increased valve seat flow capacity for a given seat angle and valve lift.
  • FIG. 1 is a diagrammatic representation of FIG.
  • FIGE. PRIOR ART
  • FUEL INJECTION NOZZLE The present invention relates generally to fuel injection nozzles for delivery of atomized fuel into the cylinders of internal combustion engines of the diesel type. More particularly, the invention relates to an improved fuel injection nozzle of the closed inwardly opening type having a nozzle valve design which minimizes engine gaseous emissions and exhaust smoke, facilitates manufacturing of the nozzle, and increases the valve seat flow capacity.
  • the nozzle tip In the closed type of fuel injection nozzle, the nozzle tip extends into the engine combustion chamber so that the nozzle spray orifices are in a position to direct a spray of atomized fuel in a predetermined pattern within the combustion chamber.
  • the spray orifices in a typical nozzle fan outwardly from a chamber known as the nozzle sac located immediately below the nozzle valve.
  • a problem with the conventional nozzle is the boiling of the residual fuel in the sac chamber during combustion of the injected fuel in the engine chamber. Vaporized fuel from the sac escapes through the spray orifices into the combustion chamber but arrives too late for combustion with the injected charge and instead is exhausted from the engine with the products of combustion thereby increasing gaseous emissions and visual smoke.
  • the present invention is a timely and important advance in reducing the emission levels of diesel engines.
  • a further related problem is the chemical breakdown of the residual fuel in the sac chamber under the intense heat conditions of the combustion chamber, resulting in a fouling of the spray orifices and a buildup of carbon on the nozzle tip.
  • the sac volume is substantially reduced in comparison to conventional nozzles, thereby reducing the amount of fuel remaining in the sac cavity following injection and minimizing the unburned fuel escaping to the exhaust from this source.
  • the valve element configuration is such as to establish the control point of minimum fuel flow with the valve element rather than at the intersection of the valve seat and sac as in the conventional nozzle.
  • the sac may be smaller since it may now have converging walls. Allowance is unnecessary for finish grinding of the valve seat, and the valve element need not project into the sac when the valve is open. Since the seat flow characteristic of the nozzle may be controlled by machining the valve element rather than the relatively inaccessible sac and seat intersection, this operation is greatly facilitated.
  • the improved shape of the valve element further increases the flexibility of manufacture of the nozzle since it permits an increase of the fuel flow area with a given valve lift simply by modifying the valve element with only a slight resultant increase in the volume of the sac cavity. Furthermore, since the improved valve shape provides increased flow at the seat for any given valve lift and any specific seat angle, it is therefore possible to reduce the valve lift in many applications to obtain the lowest possible nozzle seat and spring stresses for increased service life.
  • a further object of the invention is to provide an improved fuel injection nozzle as described having a novel valve element configuration which facilitates manufacturing of the nozzle.
  • Another object of the invention is to provide a fuel injection nozzle as described wherein the fuel flow characteristics of the nozzle may be varied by a change in the valve element configuration with only a slight resultant increase in the volume of the sac cavity.
  • Another object of the invention is to provide a fuel injection nozzle as described having a novel valve element configuration which provides either l increased fuel flow without changing valve seat angle or valve lift or (2) reduction in nozzle seat and spring stresses by reducing valve lift and maintaining existing fuel flow.
  • FIG. I is a partial side view partly in section of a nozzle assembly embodying the present invention.
  • FIG. 2 is an enlarged sectional view of the lower end of a conventional fuel injection nozzle
  • FIG. 3 is an enlarged view of the lower end of the nozzle shown in FIG. 1, showing the nozzle valve in the closed position;
  • FIG. 4 is a view similar to FIG. 3 with the valve shown in the open position;
  • FIG. 5 is a partial sectional view taken along line 55 of FIG. 4;
  • FIG. 6 is a sectional view taken along line 6-6 of FIG. 4;
  • FIG. 7 is a sectional view taken along line 77 of FIG. 4.
  • FIG. 1 illustrates the lower portion of a fuel injection nozzle assembly generally designated 10 which for installation in an engine is secured to a nozzle holder (not shown) by the partially illustrated cap nut 12.
  • the nozzle assembly 10 includes a nozzle body 14 having a lower cylindrical portion 16 and an upper concentric cylindrical portion 18 of larger diameter.
  • the cap nut 12 bears against the shoulder 20 formed at the juncture of the body portions 16 and 18.
  • a valve element 22 is disposed within a concentric bore 24 in the nozzle body 14.
  • the valve element includes a cylindrical upper portion 22a and a tapered lower portion 22b, and terminates at its lower end in a valve tip 28 having a novel configuration as described in detail below.
  • the valve tip is adapted to cooperatively engage a frusto-conical valve seat 30 in the nozzle body which extends coaxially downwardly from the bore 24.
  • a smaller chamber 32 known in the art as a sac is disposed immediately beneath and in communication with the valve seat.
  • a plurality of spray orifices 34 extend outwardly through the valve body substantially perpendicularly to the walls of the sac.
  • the exterior of the nozzle body in the region of the sac is shaped in a nipple-like configuration to permit a substantially lateral direction of the fuel spray even in the case of asymmetrical spray orifices.
  • the valve element is downwardly spring-loaded into the closed position illustrated in FIG. 1.
  • Fuel from a fuel injection pump flows downwardly through annular passage 36 between the valve element and the bore wall and acts against the valve element to open the valve when the fuel pressure exceeds the spring force.
  • the high pressure fuel flows into the sac, and is atomized as it passes out through the spray orifices into the combustion chamber. A drop in fuel pressure permits the valve to close under the spring force, cutting off the injection.
  • the present invention comprises essentially the cooperative configurations of the valve element tip, the valve seat and the sac, which details are most readily apparent from the views of FIGS. 37.
  • FIGS. 37 Prior to considering the details of the invention in these areas, however, it would be advantageous to review conventional nozzle tip construction as shown in FIG. 2 where elements common to the above described nozzle are designated by the same numerals with a prime subscript.
  • the prior art nozzle assembly includes a nozzle body 14 and a valve element 22 disposed within the bore 24 of the body.
  • the 'body 14' includes a valve seat 30' having a frusto-conical configuration, the diametrically opposed walls of which when viewed in section as in FIG. 2 form the included angle B.
  • the valve tip 28 comprises a conical surface which intersects the tapered valve element portion 22b to form the circular edge 40.
  • the diametrically opposed edges of the conical valve tip 28 form therebetween the included angle V which is a slightly larger angle than angle B of the valve seat so that the valve element will engage the valve seat in its closed position along the circular edge 40.
  • the sac 32 of the conventional nozzle is relatively large and of cylindrical shape with a semispherical end for reasons set forth below.
  • the spray orifices 34 extending outwardly from the sac 32' direct atomized fuel in a predetermined spray pattern into the engine cylinder when the nozzle valve is opened.
  • the minimum fuel flow area when the valve is in the open position occurs at the circular control edge 42 formed by the intersection of the valve seat and the cylindrical walls of the sac. Since the typical nozzle is many times smaller than the views shown (the spray orifices are barely visible to the unaided human eye), the machining of the valve seat and sac, which are relatively inaccessible at the bottom of the valve body is a difficult and time consuming operation. Since the valve seat 30' in the conventional nozzle is finish ground after heat treatment, it can be understood that the sac walls must be cylindrical and concentric so that the control edge 42 will not change as the valve seat is ground. Furthermore, a sufficient volume of the sac must be provided to permit the extending valve tip conical surface 28' to protrude into the sac cavity. This protruding portion cooperates with the edge 42 when the valve elements is in the open position to control the rate of fuel flow. The conventional nozzle accordingly must include a sac of an undesirably large volume.
  • the valve tip 28 comprises a frusto-conical surface 44, diametrically opposed faces of which are angled at the included angle V as shown in FIG. 3.
  • This frusto-conical surface 44 intersects the tapered valve element surface 22b at the circular edge 46.
  • the valve tip terminates in a conical surface 48, diametrically opposed faces of which form the included angle A as shown in FIG. 3.
  • the conical surface 48 intersects the frusto-conical surface 44 to form the circular control edge 50 which has the diameter D as illustrated in FIG. 3.
  • the diametrically opposed walls of the valve seat 30 as shown in FIG.
  • the sidewalls of the sac 32 have a frusto-conical configuration, diametrically opposed faces of which form the included angle C therebetween.
  • the angle C being a smaller angle than the angle B of the valve seat, a circular edge 52 is formed at the intersection of the sac with the valve seat.
  • FIG. 4 The operation of the present nozzle is best shown in FIG. 4 wherein the valve element is illustrated in the open position. As shown by the flow indicating arrows,
  • the high pressure fuel passes from the annular passage 36 between the valve seat and the valve element sur' faces 44 and 48 into the sac 32.
  • the rate of flow is determined by the minimum fuel flow area adjacent the control edge 50, the diameter D of which governs the nozzle delivery characteristics. From the sac 32, the fuel passes through the spray orifices 34 and exits as an atomized spray 54 into the engine combustion chamher.
  • the injection characteristics of the nozzle can be effected by machining the surface 48 while maintaining the angle A. This serves to enlarge the diameter D of the control edge 50, thereby increasing the fuel flow area with only a slight resultant increase in the sac volume.
  • the sac can be shaped with frustoconical walls to minimize its volume.
  • the sac wall angle C should, however, be less than the seat angle B to provide run-out clearance for seat grinding.
  • the sac depth can be considerably reduced since no cylindrical sac is required for seat flow control.
  • the valve element tip with the present construction does not extend to an appreciable depth into the sac.
  • the present nozzle valve construction permits a substantial decrease in sac volume in comparison to conventional nozzles, with a consequent reduction in engine gaseous emission and visual smoke. It has been found in at least one instance that a nozzle utilizing the present design need have only 1 1 percent of the sac volume that would be necessary using the conventional construction.
  • the reduction in sac volume coupled with the greatly facilitated manufacture and increased seat flow capacity of the nozzle possible with the present construction accordingly provides both an improved nozzle performance from an emission control standpoint and increased economies and flexibility of manufacture.
  • a fuel injection nozzle assembly comprising a nozzle body, a bore within said body, a valve element disposed within said bore for recipricatory movement between open and closed positions, a frusto-conical valve seat at the lower end of said bore, the lower end of said valve element being adapted to engage said valve seat to seal the passage therebetween, a sac beneath said valve seat in communication therewith, spray orifices extending outwardly through said valve body from said sac, and means for introducing pressurized fuel into said bore above said valve seat, the improvement comprising a circular control edge on said valve element lower end which defines in cooperation with said valve seat the minimum fuel flow area between said valve element and said valve seat in the open position of said valve element.
  • control edge is formed by the intersection of two surfaces of revolution on said valve element.
  • a fuel injection nozzle assembly comprising a nozzle body, a bore within said body, a valve element disposed within said bore for recipricatory movement between open and closed positions, a frusto-conical valve seat at the lower end of said bore, the lower end of said valve element being adapted to engage said valve seat to seal the passage therebetween, a sac beneath said valve seat in communication therewith, spray orifices extending outwardly through said valve body from said sac, and means for introducing pressurized fuel into said bore above said valve seat, the improvement wherein said valve element lower end configuration comprises a conical surface at the valve element tip, and a frusto-conical surface adjacent said conical surface, the intersection of said conical and frusto-conical valve element surfaces forming a circular control edge which cooperates with said valve seat to define the minimum fuel flow area between said valve element and said valve seat in the open position of said valve element.
  • valve element conical surface is greater than that of said valve element frusto-conical surface so that the fuel flow area below said control edge is greater than that at said control edge at any position of said valve element.

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  • Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Fuel-Injection Apparatus (AREA)
US00395828A 1973-09-10 1973-09-10 Fuel injection nozzle Expired - Lifetime US3836080A (en)

Priority Applications (7)

Application Number Priority Date Filing Date Title
US00395828A US3836080A (en) 1973-09-10 1973-09-10 Fuel injection nozzle
CA205,531A CA1020030A (en) 1973-09-10 1974-07-24 Fuel injection nozzle
DE2438014A DE2438014A1 (de) 1973-09-10 1974-08-07 Brennstoffeinspritzduese
IT52625/74A IT1019046B (it) 1973-09-10 1974-08-16 Perfezionamento negli ugelli di iniezione del carburante in moto ri a combustione interna a ciclo diesel
FR7429178A FR2243346B3 (enrdf_load_stackoverflow) 1973-09-10 1974-08-26
JP49101825A JPS60550B2 (ja) 1973-09-10 1974-09-04 燃料噴射ノズル
GB3924174A GB1477676A (en) 1973-09-10 1974-09-09 Fuel injection nozzle

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
US00395828A US3836080A (en) 1973-09-10 1973-09-10 Fuel injection nozzle

Publications (1)

Publication Number Publication Date
US3836080A true US3836080A (en) 1974-09-17

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Application Number Title Priority Date Filing Date
US00395828A Expired - Lifetime US3836080A (en) 1973-09-10 1973-09-10 Fuel injection nozzle

Country Status (7)

Country Link
US (1) US3836080A (enrdf_load_stackoverflow)
JP (1) JPS60550B2 (enrdf_load_stackoverflow)
CA (1) CA1020030A (enrdf_load_stackoverflow)
DE (1) DE2438014A1 (enrdf_load_stackoverflow)
FR (1) FR2243346B3 (enrdf_load_stackoverflow)
GB (1) GB1477676A (enrdf_load_stackoverflow)
IT (1) IT1019046B (enrdf_load_stackoverflow)

Cited By (36)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3980237A (en) * 1975-11-17 1976-09-14 Allis-Chalmers Corporation Differential valve in fuel injection nozzle
US4030668A (en) * 1976-06-17 1977-06-21 The Bendix Corporation Electromagnetically operated fuel injection valve
US4057190A (en) * 1976-06-17 1977-11-08 Bendix Corporation Fuel break-up disc for injection valve
US4106702A (en) * 1977-04-19 1978-08-15 Caterpillar Tractor Co. Fuel injection nozzle tip with low volume tapered sac
US4153205A (en) * 1977-10-19 1979-05-08 Allis-Chalmers Corporation Short seat fuel injection nozzle valve
FR2438172A1 (fr) * 1978-10-03 1980-04-30 Bosch Gmbh Robert Buse d'injection de carburant
EP0030103A1 (en) * 1979-11-30 1981-06-10 Caterpillar Tractor Co. Fuel injection nozzle valve and system incorporating such valve
US4275844A (en) * 1979-11-30 1981-06-30 Caterpillar Tractor Co. Fuel injection nozzle
US4637553A (en) * 1984-10-09 1987-01-20 Diesel Kiki Co., Ltd. Fuel injection nozzle unit for internal combustion engines
US4674688A (en) * 1984-10-08 1987-06-23 Usui Kokusai Sangyo Kabushiki Kaisha Accumulation-type fuel injector
GB2201462A (en) * 1987-02-28 1988-09-01 Lucas Ind Plc I.C. engine fuel injection nozzle
US4801095A (en) * 1985-08-10 1989-01-31 Robert Bosch Gmbh Fuel injection nozzle for internal combustion engines
US5037031A (en) * 1990-04-25 1991-08-06 Cummins Engine Company, Inc. Reduced trapped volume
US5042721A (en) * 1990-07-19 1991-08-27 Cummins Engine Company, Inc. Reduced gas flow open nozzle unit injector
US5163621A (en) * 1989-12-12 1992-11-17 Nippondenso Co., Ltd. Fuel injection valve having different fuel injection angles at different opening amounts
US5765755A (en) * 1997-01-23 1998-06-16 Cummins Engine Company, Inc. Injection rate shaping nozzle assembly for a fuel injector
WO2000014400A1 (de) * 1998-09-09 2000-03-16 Robert Bosch Gmbh Kraftstoffeinspritzventil für brennkraftmaschinen
WO2001004490A1 (de) * 1999-07-08 2001-01-18 Robert Bosch Gmbh Sackloch-einspritzdüse für brennkraftmaschinen mit abgerundetem übergang zwischen sackloch und düsennadelsitz
US6257506B1 (en) * 1997-12-11 2001-07-10 Robert Bosch Gmbh Fuel injector for auto-ignition internal combustion engines
US20020162906A1 (en) * 2000-06-27 2002-11-07 Axel Hockenberger Fuel injection valve for internal combustion engines
WO2003046368A1 (de) * 2001-11-23 2003-06-05 Robert Bosch Gmbh Kraftstoffeinspritzventil für brennkraftmaschinen
US20030136381A1 (en) * 2000-12-11 2003-07-24 Guenter Dantes Fuel injector
US20040056118A1 (en) * 2001-05-10 2004-03-25 Patrick Mattes Valve with radial recesses
US20040074994A1 (en) * 2002-10-16 2004-04-22 Nordson Corporation Interchangeable nozzle for a dispensing module
WO2005026526A1 (de) * 2003-09-09 2005-03-24 Robert Bosch Gmbh Kraftstoffeinspritzventil für brennkraftmaschinen
US7150410B1 (en) 1999-01-29 2006-12-19 Robert Bosch Gmbh Method for providing a controlled injection rate and injection pressure in a fuel injector assembly
US20070120087A1 (en) * 2003-12-17 2007-05-31 Wms Gaming Inc. Valve body with multiconical geometry at the valve seat
CN101994622A (zh) * 2009-08-04 2011-03-30 万国引擎知识产权有限责任公司 减少焦化的燃料喷嘴
US20130270369A1 (en) * 2012-04-16 2013-10-17 Cummins Intellectual Property, Inc. Fuel injector
US20150020778A1 (en) * 2012-03-14 2015-01-22 International Engine Intellectual Property Company Llc Fuel injector nozzle
GB2552673A (en) * 2016-08-02 2018-02-07 Delphi Int Operations Luxembourg Sarl SCR doser spray atomization
US20180080482A1 (en) * 2015-03-09 2018-03-22 Denso Corporation Ejector and ejector-type refrigeration cycle
US10865754B2 (en) 2017-04-05 2020-12-15 Progress Rail Services Corporation Fuel injector having needle tip and nozzle body surfaces structured for reduced sac volume and fracture resistance
US10895231B2 (en) 2019-06-13 2021-01-19 Progress Rail Services Corporation Fuel injector nozzle assembly having anti-cavitation vent and method
CN113339173A (zh) * 2021-06-18 2021-09-03 中国北方发动机研究所(天津) 一种高压共轨喷油器及其喷嘴
CN119533883A (zh) * 2023-08-30 2025-02-28 中国航发商用航空发动机有限责任公司 航空发动机喷嘴特性在线监测方法、监测设备及可读存储介质

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JPS54127930U (enrdf_load_stackoverflow) * 1978-02-28 1979-09-06
DE3303470A1 (de) * 1983-02-02 1984-08-02 Jaroslavskij savod diselnoj apparatury, Jaroslavl Einspritzduese fuer verbrennungsmotore
GB2229495A (en) * 1989-03-22 1990-09-26 Lucas Ind Plc Fuel injector
GB2232203A (en) * 1989-06-03 1990-12-05 Lucas Ind Plc C.i. engine fuel injector
DE4303813C1 (de) * 1993-02-10 1994-06-30 Bosch Gmbh Robert Kraftstoffeinspritzdüse für Brennkraftmaschinen
RU2124140C1 (ru) * 1997-01-06 1998-12-27 Открытое акционерное общество Ярославский завод дизельной аппаратуры Распылитель форсунки для двигателя внутреннего сгорания
RU2132479C1 (ru) * 1997-05-06 1999-06-27 Открытое акционерное общество Ярославский завод дизельной аппаратуры Распылитель форсунки для дизеля
RU2138673C1 (ru) * 1997-11-05 1999-09-27 ОАО "Ярославский завод дизельной аппаратуры" Распылитель форсунки для дизеля
RU2156376C2 (ru) * 1998-12-10 2000-09-20 ОАО Ярославский завод дизельной аппаратуры Распылитель форсунки для двигателя внутреннего сгорания
RU2175077C2 (ru) * 2000-01-18 2001-10-20 Гундоров Валентин Михайлович Способ изготовления распылителя форсунки для двигателя внутреннего сгорания
RU2175078C2 (ru) * 2000-01-31 2001-10-20 Гундоров Валентин Михайлович Распылитель форсунки для двигателя внутреннего сгорания
DE102009018767A1 (de) * 2009-04-24 2010-10-28 Man Diesel & Turbo Se Kraftstoffeinspritzdüse für eine Brennkraftmaschine

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GB906603A (en) * 1958-06-14 1962-09-26 Motorpal Jihlava Improvements in and relating to fuel injection nozzles for internal combustion engines
US3391871A (en) * 1967-03-30 1968-07-09 Bosch Gmbh Robert Fuel injection valve for internal combustion engines

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GB280153A (en) * 1926-11-03 1927-12-29 Charles Edward Cutting Improvements in means for increasing the frictional contact of the wheels of motors and other conveyors on ropeways
DE932209C (de) * 1952-04-13 1955-08-25 Bosch Gmbh Robert Kraftstoffeinspritzventil
DE976061C (de) * 1952-05-03 1963-02-07 Sulzer Ag Fluessigkeitsgekuehlte Einspritzduese fuer Brennkraftmaschinen
DE1576582A1 (de) * 1967-07-15 1970-02-12 Kloeckner Humboldt Deutz Ag Kraftstoffeinspritzventil

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Publication number Priority date Publication date Assignee Title
GB906603A (en) * 1958-06-14 1962-09-26 Motorpal Jihlava Improvements in and relating to fuel injection nozzles for internal combustion engines
US3391871A (en) * 1967-03-30 1968-07-09 Bosch Gmbh Robert Fuel injection valve for internal combustion engines

Cited By (48)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3980237A (en) * 1975-11-17 1976-09-14 Allis-Chalmers Corporation Differential valve in fuel injection nozzle
US4030668A (en) * 1976-06-17 1977-06-21 The Bendix Corporation Electromagnetically operated fuel injection valve
US4057190A (en) * 1976-06-17 1977-11-08 Bendix Corporation Fuel break-up disc for injection valve
US4106702A (en) * 1977-04-19 1978-08-15 Caterpillar Tractor Co. Fuel injection nozzle tip with low volume tapered sac
US4153205A (en) * 1977-10-19 1979-05-08 Allis-Chalmers Corporation Short seat fuel injection nozzle valve
FR2438172A1 (fr) * 1978-10-03 1980-04-30 Bosch Gmbh Robert Buse d'injection de carburant
EP0030103A1 (en) * 1979-11-30 1981-06-10 Caterpillar Tractor Co. Fuel injection nozzle valve and system incorporating such valve
WO1981001592A1 (en) * 1979-11-30 1981-06-11 Caterpillar Tractor Co Fuel injection nozzle
US4275844A (en) * 1979-11-30 1981-06-30 Caterpillar Tractor Co. Fuel injection nozzle
US4674688A (en) * 1984-10-08 1987-06-23 Usui Kokusai Sangyo Kabushiki Kaisha Accumulation-type fuel injector
US4637553A (en) * 1984-10-09 1987-01-20 Diesel Kiki Co., Ltd. Fuel injection nozzle unit for internal combustion engines
US4801095A (en) * 1985-08-10 1989-01-31 Robert Bosch Gmbh Fuel injection nozzle for internal combustion engines
GB2201462A (en) * 1987-02-28 1988-09-01 Lucas Ind Plc I.C. engine fuel injection nozzle
US5163621A (en) * 1989-12-12 1992-11-17 Nippondenso Co., Ltd. Fuel injection valve having different fuel injection angles at different opening amounts
US5037031A (en) * 1990-04-25 1991-08-06 Cummins Engine Company, Inc. Reduced trapped volume
US5042721A (en) * 1990-07-19 1991-08-27 Cummins Engine Company, Inc. Reduced gas flow open nozzle unit injector
US5765755A (en) * 1997-01-23 1998-06-16 Cummins Engine Company, Inc. Injection rate shaping nozzle assembly for a fuel injector
US6257506B1 (en) * 1997-12-11 2001-07-10 Robert Bosch Gmbh Fuel injector for auto-ignition internal combustion engines
WO2000014400A1 (de) * 1998-09-09 2000-03-16 Robert Bosch Gmbh Kraftstoffeinspritzventil für brennkraftmaschinen
US6322007B1 (en) * 1998-09-09 2001-11-27 Robert Bosch Gmbh Fuel injection valve for internal combustion engines
US7150410B1 (en) 1999-01-29 2006-12-19 Robert Bosch Gmbh Method for providing a controlled injection rate and injection pressure in a fuel injector assembly
US6695230B1 (en) 1999-07-08 2004-02-24 Robert Bosch Gmbh Blind bore injection nozzle for internal combustion engines, with a rounded transition between the blind bore and the nozzle needle seat
KR100737711B1 (ko) * 1999-07-08 2007-07-11 로베르트 보쉬 게엠베하 연료 분사 노즐
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CA1020030A (en) 1977-11-01
JPS60550B2 (ja) 1985-01-08
FR2243346B3 (enrdf_load_stackoverflow) 1977-06-17
GB1477676A (en) 1977-06-22
JPS5054725A (enrdf_load_stackoverflow) 1975-05-14
FR2243346A1 (enrdf_load_stackoverflow) 1975-04-04
IT1019046B (it) 1977-11-10
DE2438014A1 (de) 1975-03-20

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