US2017028A - Injection nozzle for self-igniting internal combustion engines - Google Patents

Injection nozzle for self-igniting internal combustion engines Download PDF

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Publication number
US2017028A
US2017028A US713072A US71307234A US2017028A US 2017028 A US2017028 A US 2017028A US 713072 A US713072 A US 713072A US 71307234 A US71307234 A US 71307234A US 2017028 A US2017028 A US 2017028A
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US
United States
Prior art keywords
needle
fuel
nozzle
valve
pin
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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
US713072A
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English (en)
Inventor
Heinrich Hans
Voit Willy
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Robert Bosch AG
Robert Bosch GmbH
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Robert Bosch GmbH
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Publication date
Application filed by Robert Bosch GmbH filed Critical Robert Bosch GmbH
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Publication of US2017028A publication Critical patent/US2017028A/en
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    • 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
    • F02M61/06—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 being furnished at seated ends with pintle or plug shaped extensions

Definitions

  • Patented Oct. 8 1935 UNITED STATES INJECTION NOZZLE roa SELF-IGNITING INTERNAL COMBUSTION enemas Hans Heinrich, Stuttgart, and Willy Volt, Stuttgart-Bad Cannstatt, Germany, assignors to Robert Bosch Aktiengesellschaft, Stuttgart,
  • the present invention relates to injection nozzles for self-igniting internal combustion engines in which the needle-valve is raised from its s'eat against the force of a closing Spring by the pressure of the fuel impinging on it; and in doing so, forms, in conjunction with the nozzle body, a throttling opening or gap during the first part of its opening lift of smaller cross-section than the valve opening during the remainder of the lift, which gap represents the narrowest cross-section in the fuel discharge path.
  • This type of nozzle is often known by the name of liquid-controlled pin nozzle.
  • the pin extension of the needle valve which is usually arranged forwardly of the seating shoulder of the needle valve at the needle end, and guided with more or less play in the nozzle body over the whole or only over a part of the lift of the needle, has already been provided in such nozzles for various reasons.
  • the form of the pin determines the guidance and breaking up of the fuel and thus the shape of the jet.
  • a pin has often been arranged at the forward end of the needle valve, because by its movements it prevents the nozzle mouth becoming incrusted.
  • the gap which determines the narrowest nozzle cross-section between the pin and the guide is so formed. that the free cross-section of the nozzle only gradually enlarges on the opening lift of the valve. In this way the quantity of fuel injected at the beginning of the opening movement of the valve was to be kept as small as possible.
  • This known proposal was based on the recognition of the fact that most nozzles, even at the very beginning of the opening of their valve, quite suddenly allow much too great a share of the quantity of fuel to be introduced into the combustion chamber at one injection operation, so that this large quantity produces explosive rises in pressure on its self-ignition, which causes heavy running of the engine.
  • this is effected by the stiffness of the closing spring being proportioned in such a way that its increase in force during the initial part of the stroke which the needle perform until the throttle gap between pin and guide is substantially enlarged is greater than that force which tends to accelerate the needle during the opening.
  • Suitable valves in practice for the stiffness of the spring are a load of about 22-40 kg. to 1 mm. of spring compression. Within these limits helical springs of steel wire can be made in acceptable sizes, the needle lift kept within the usual together with holder, in full size.
  • Figure 2 is a longitudinal section through the lower part of the nozzle according to the first construction enlarged about ten times, in the closed position of the needle.
  • Figure 3 shows on'the same enlarged scale a portion of Figure 2, but with the needle partly raised, whilst in Figure 4 the needle is shown fully raised.
  • Figure 5 shows the second example of construction, drawn in the same wayas in Figures 3 and 4, but in this case the needle is resting on its seat.
  • Figure 6 is a longitudinal section enlarged about ten-fold, of the third example.
  • Figure 7 shows the fourth construction in the same manner.
  • Figures 8, 9 and 10 show the fifth construction also in longitudinal section and enlarged about ten-fold in three different positions of the needle.
  • Figure ll shows the sixth example in the same mode of illustration.
  • the needle is here shown in its position at the beginning of the injection.
  • a is the nozzle body, 17 the nozzle needle, which with its stem is closely guided in a bore in the nozzle body.
  • the upper end of the nozzle body is pressed by'a cap-nut d firmly and tightly against the lower end of the stem of a nozzleholder e.
  • the holder stem is bored longitudinally. Through this longitudinal bore f passes a pressure rod 9, the lower end of which is seated on the upper extension h, of the needle which is supported'relative to the guide stem and projects alittle distance into the longitudinal bore 1.
  • the bore 1 has at the lower end a contracted part, whose diameter is smaller than the diameter of the guide bore of the nozzle body, so that an annular shoulder i is situated above the guide bore of the nozzle body, which limits the opening stroke of the needle to the extent x, which amounts to about 0.60.8 mm.
  • An enlarged recess is in the head of the nozzle holder receives a very stiff closing spring m, which is supported below on a spring plate 11. on the upper end of the pressure rod 9 and at top bears against a spring plate 0. The upper spring plate engages around the end of an adjusting screw 9, which is screwed into the top of a cap q I that closes the spring chamber Ic.
  • connection piece 1' The supply of fuel to the nozzle takes place through the connection piece 1', the bores s, t, in
  • the fuel passes into an annular space 0 in the nozzle body formed by reducing the needle relative to its stem.
  • the reduced needle extension w carries the seating surface 11 for the needle.
  • the extension w is again stepped down below the seating surface 1
  • the pin 2 so formed fits with quite small clearance 15' into the throat of the nozzle which is made cylindrical over its end portion.
  • the lower part of the pin is made obtusely conical for guiding the jet of fuel, and in such a way that the obtuse cone with its larger diameter forms the lower end of the go needle.
  • the fuel conveyed to the annular space 1 acts on the annular shoulder between the needle guide 0 and the extension w, and after it has sufficient pressure lifts the needle against the pressure of its closing spring m.
  • the outlet gap for the fuel is formed by the very narrow annular space existing between the cylindrical part of the pin 2 and the nozzle throat. This annular space permits only a little fuel to be sprayed.
  • This first part of the needle lift for example, from the position of the needles shown in Fig. 2 to its position shown in Fig. 3, in which the cylindrical surface of the pin 2 strongly throttles the fuel discharge, is preferably so proportioned that this part of the stroke .is adapted to the ignition delay period; that is,
  • the arrangement is such that the time interval of execution of this first part of the needle lift corresponds substantially to the duration of the ignition delay and especially so at low speeds of the engine. The result is that in this first part of the injection operation little fuel reaches the combustion chamber.
  • the second example of construction according to Fig. 5 differs from the first only by an unessential alterationof the needle pin 2, whose lower reduced end is here made cylindrical.
  • This nozzle produces a narrow straight jet, whilst the nozzle in Fig. 1 produces a more conical jet.
  • Fig. 6 shows a so-called orifice nozzle having two spraying orifices A.
  • the length of the pin 2 is here suited to the magnitude of the first part of the needle lift.
  • the throttling produced by the annular gap between the pin 2 and its guide should of.
  • the jet indicated in dotted lines in Fig. 2 shows that during the first part of the lift of the needle, that is, at the beginning of the injection, the fuel does not strike on the upper surface of the conical end of the pin. Only after a considerable lift of the needle does the jet strike and then recoil or rebound from the conical wall of the end of the pin. The action of this recoil surface, which is very conducive to the breaking up of the fuel, is thus absent in this case during the first part of the opening lift of the needle, so that the atomization of the part of the charge of fuel first sprayed which initiates the ignition is not as good as in the constructions shown in Figs. 8-11 later to be referred to. This less thorough atomization of the fuel becomes noticeable more especially at a slow speed in engines in which the speed of delivery of the injection pump is directly dependent on the engine speed. The insufficient atomization at the beginning of the injection may then cause irregular beginning of ignition and incomplete combustion.
  • the spraying of the jet past the conical rebound surface provided at the end of the pin is mainly to be ascribed to the fact that in the nozzle according to Fig. 2 the very narrow outlet opening at the beginning of the needle lift is cylindrical for a comparatively narrow length, so that the jet sprayed at the beginning of the needle lift is carried past the conical end of the pin without striking the same and rebounding therefrom.
  • the gap which determines the guidance of the jet on the first part of the opening lift is suitably formed in accordance with the constructions shown in Figs. 8-11, which is best done by making the part in question of the pin tapered towards the constriction.
  • the upper part of the pin 2 is cylindrical, and penetrates, when the needle is closed (Fig. 8), with very slight play a little way into the nozzle throat,
  • Fig. 11 differs from that shown in Figs. 8-10 only in that, in this case, the tapered part 13 of the pin merges directly into the constriction II.
  • the throttling produced by the pin in the first part of the needle lift of course decreases more quickly here than in the construction according to Figs. 8-10.
  • a fuel injection device for internal combustion engines comprising a nozzle body supplied with liquid fuel under pressure and having a discharge nozzle, a needle valve for said nozzle seat-f ing therein in the closed position of the valve and having a rearward abutment surface within said nozzle body engaged by the liquid fuel to effect the opening stroke of said valve, said nozzle and valve being cooperatively formed and arranged to provide a fuel discharge opening increasing in cross-sectional area for the discharge of fuel therethrough as said valve increases its opening movement, said needle valve having another abutment surface in the region of the valve seating exposed to the opening pressure of said liquid fuel only when said valve is moved from its seat whereby pressure of said fuel on said other abutment surfaces tends to accelerate the opening said valve with a total force for the entire opening stroke of said needle valve greater than the force exerted by the liquid fuel on said other abutment surface of said needle valve.
  • a fuel injection device for internal combustion engines comprising a nozzle body supplied with liquid fuel under pressure and having a discharge nozzle, a needle valve seating in said nozzle and having a rearward abutment surface en- -gaged by the liquid fuel to effect the opening stroke of said valve by the pressure of the liquid fuel, said nozzle and'valve being formed and co* operatively arranged to provide a restricted or throttled fuel discharge opening during an initial part of the opening stroke of said valve and a substantially increased fuel discharge opening through the remainder of its opening stroke, said valve having another abutment surface in the region of the valve seating so exposed to the presvent said acceleration of said opening stroke.
  • a fuel injection device for an internal combustion engine comprising a nozzle body supplied with liquid fuel under pressure and hafing a cylindrical discharge bore, a needle valve of circular cross section throughout and having a main body portion seating within said nozzle body and an end portion of reduced diameter projecting through said bore and reciprocating therein in the opening and closing movements of said valve, said end portion of said needle valve being of less diameter than said bore to provide an annular fuel passage between them, said end portion of said needle valve being itself of reduced diameter intermediate its length and having its annular surface to the rear of said reduced diameter forwardly and inwardly converging to said reduced diameter and its forward annular surface outwardly flaring toth'e free end of said valve whereby said bore and said end portion of said needle valve cooperate to provide an annular fuel discharge opening of cross-sectional area for the passage of fuel increasing from a minimum as the valve progresses in its opening movement and of a form so directing the fuel in its discharge -5 through said opening as to cause the same to surface area than said rearward abutment sur- 2o face engaging against

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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)
US713072A 1933-03-14 1934-02-26 Injection nozzle for self-igniting internal combustion engines Expired - Lifetime US2017028A (en)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
DEB160091D DE663301C (de) 1933-03-14 1933-03-14 Einspritzduese fuer Brennkraftmaschinen mit Selbstzuendung

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US2017028A true US2017028A (en) 1935-10-08

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US713072A Expired - Lifetime US2017028A (en) 1933-03-14 1934-02-26 Injection nozzle for self-igniting internal combustion engines

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US (1) US2017028A (enrdf_load_stackoverflow)
AT (1) AT141364B (enrdf_load_stackoverflow)
BE (1) BE399611A (enrdf_load_stackoverflow)
DE (1) DE663301C (enrdf_load_stackoverflow)
FR (1) FR764618A (enrdf_load_stackoverflow)
GB (1) GB406956A (enrdf_load_stackoverflow)

Cited By (18)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2439832A (en) * 1938-07-20 1948-04-20 Voit Willy Injection nozzle for internalcombustion engines
US2535937A (en) * 1939-07-19 1950-12-26 Bozec Leon Le Fuel injecting means for motors
US2604086A (en) * 1947-03-25 1952-07-22 Texas Co Internal-combustion engine and fuel injection nozzle therefor
US2625435A (en) * 1948-09-10 1953-01-13 Voive Ab Fuel valve and nozzle for internal combustion engines
US2647016A (en) * 1952-05-28 1953-07-28 American Locomotive Co Fuel injector
US2647015A (en) * 1951-03-17 1953-07-28 American Locomotive Co Fuel injector
US2655140A (en) * 1947-12-01 1953-10-13 Lee Royal Fuel injection apparatus
US2708601A (en) * 1951-09-27 1955-05-17 Daimler Benz Ag Fuel-injecting apparatus for an internal combustion engine
US2719055A (en) * 1951-09-28 1955-09-27 Borg Warner Fuel injector nozzle
US2746800A (en) * 1952-06-17 1956-05-22 Bosch Gmbh Robert Fuel injection nozzles for internal combustion engines
US2753217A (en) * 1952-11-08 1956-07-03 Texas Co Fuel injection nozzle for internal combustion engine
US4254915A (en) * 1977-11-15 1981-03-10 Maschinenfabrik Augsburg-Nurnberg Aktiengesellschaft Fuel injector for internal combustion engines
US4841725A (en) * 1983-09-02 1989-06-27 Ex-Cell-O Corporation Fuel spray device for gas turbine augmentor or afterburner
US5853124A (en) * 1997-05-05 1998-12-29 Servojet Products International Bottom seated pintle nozzle
US20060231647A1 (en) * 2004-07-13 2006-10-19 Guenther Hohl Fuel injection valve
US20110240770A1 (en) * 2010-04-01 2011-10-06 Gm Global Technology Operations, Inc. Fuel injector with variable area pintle nozzle
US20140060481A1 (en) * 2012-08-29 2014-03-06 GM Global Technology Operations LLC Method and apparatus of producing laminar flow through a fuel injection nozzle
US10612504B2 (en) * 2015-06-23 2020-04-07 Delphi Technologies Ip Limited Nozzle assembly with adaptive closed signal

Families Citing this family (15)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE846183C (de) * 1941-05-04 1952-08-11 Leon Le Bozec Brennstoffeinspritzvorrichtung fuer Verbrennungskraftmaschinen
DE855486C (de) * 1941-10-09 1952-11-13 Bosch Gmbh Robert Einspritzventil fuer Brennkraftmaschinen
DE927183C (de) * 1942-02-10 1955-05-02 Daimler Benz Ag Vorkammer-Einspritzbrennkraftmaschine
NL70310C (enrdf_load_stackoverflow) * 1946-08-28
DE861344C (de) * 1948-10-02 1952-12-29 Bosch Gmbh Robert Einspritzventil fuer Brennkraftmaschinen
DE1046950B (de) * 1951-12-20 1958-12-18 Friedmann & Maier Ag Einspritzduese fuer Einspritzbrennkraftmaschinen
DE1192874B (de) * 1962-05-09 1965-05-13 Ricardo & Co Engineers Brennstoffeinspritzeinrichtung
DE2814999A1 (de) * 1978-04-07 1979-10-18 Maschf Augsburg Nuernberg Ag Kraftstoff-einspritzduese fuer brennkraftmaschinen
DE2930716A1 (de) * 1979-07-28 1981-02-19 Daimler Benz Ag Drosselzapfenduese
JPS5882068A (ja) * 1981-11-09 1983-05-17 Nissan Motor Co Ltd 燃料噴射ノズル
JPS5882069A (ja) * 1981-11-09 1983-05-17 Nissan Motor Co Ltd 燃料噴射ノズル
GB2123481B (en) * 1982-06-19 1985-04-17 Lucas Ind Plc C i engine fuel injection nozzles
IT1167325B (it) * 1983-04-11 1987-05-13 Roberto Bosio Polverizzatore per iniettori del combustibile di motori diesel
GB2185070B (en) * 1983-07-12 1987-12-09 Lucas Ind Plc Fuel injection nozzles
DE3734587A1 (de) * 1987-10-13 1989-05-03 Bosch Gmbh Robert Kraftstoff-einspritzduese fuer brennkraftmaschinen

Cited By (19)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2439832A (en) * 1938-07-20 1948-04-20 Voit Willy Injection nozzle for internalcombustion engines
US2535937A (en) * 1939-07-19 1950-12-26 Bozec Leon Le Fuel injecting means for motors
US2604086A (en) * 1947-03-25 1952-07-22 Texas Co Internal-combustion engine and fuel injection nozzle therefor
US2655140A (en) * 1947-12-01 1953-10-13 Lee Royal Fuel injection apparatus
US2625435A (en) * 1948-09-10 1953-01-13 Voive Ab Fuel valve and nozzle for internal combustion engines
US2647015A (en) * 1951-03-17 1953-07-28 American Locomotive Co Fuel injector
US2708601A (en) * 1951-09-27 1955-05-17 Daimler Benz Ag Fuel-injecting apparatus for an internal combustion engine
US2719055A (en) * 1951-09-28 1955-09-27 Borg Warner Fuel injector nozzle
US2647016A (en) * 1952-05-28 1953-07-28 American Locomotive Co Fuel injector
US2746800A (en) * 1952-06-17 1956-05-22 Bosch Gmbh Robert Fuel injection nozzles for internal combustion engines
US2753217A (en) * 1952-11-08 1956-07-03 Texas Co Fuel injection nozzle for internal combustion engine
US4254915A (en) * 1977-11-15 1981-03-10 Maschinenfabrik Augsburg-Nurnberg Aktiengesellschaft Fuel injector for internal combustion engines
US4841725A (en) * 1983-09-02 1989-06-27 Ex-Cell-O Corporation Fuel spray device for gas turbine augmentor or afterburner
US5853124A (en) * 1997-05-05 1998-12-29 Servojet Products International Bottom seated pintle nozzle
US20060231647A1 (en) * 2004-07-13 2006-10-19 Guenther Hohl Fuel injection valve
US20110240770A1 (en) * 2010-04-01 2011-10-06 Gm Global Technology Operations, Inc. Fuel injector with variable area pintle nozzle
US9879644B2 (en) * 2010-04-01 2018-01-30 GM Global Technology Operations LLC Fuel injector with variable area pintle nozzle
US20140060481A1 (en) * 2012-08-29 2014-03-06 GM Global Technology Operations LLC Method and apparatus of producing laminar flow through a fuel injection nozzle
US10612504B2 (en) * 2015-06-23 2020-04-07 Delphi Technologies Ip Limited Nozzle assembly with adaptive closed signal

Also Published As

Publication number Publication date
AT141364B (de) 1935-04-10
FR764618A (fr) 1934-05-25
GB406956A (en) 1934-03-08
BE399611A (enrdf_load_stackoverflow) 1933-12-30
DE663301C (de) 1938-08-04

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