EP0133470A1 - Injecteur de carburant pour moteurs à combustion interne - Google Patents

Injecteur de carburant pour moteurs à combustion interne Download PDF

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Publication number
EP0133470A1
EP0133470A1 EP19840107559 EP84107559A EP0133470A1 EP 0133470 A1 EP0133470 A1 EP 0133470A1 EP 19840107559 EP19840107559 EP 19840107559 EP 84107559 A EP84107559 A EP 84107559A EP 0133470 A1 EP0133470 A1 EP 0133470A1
Authority
EP
European Patent Office
Prior art keywords
valve needle
fuel
piston
cylinder bore
pressure
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
EP19840107559
Other languages
German (de)
English (en)
Other versions
EP0133470B1 (fr
Inventor
Dietrich Dipl.-Ing. Trachte
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 DE19833328824 external-priority patent/DE3328824A1/de
Priority claimed from DE19833344396 external-priority patent/DE3344396A1/de
Application filed by Robert Bosch GmbH filed Critical Robert Bosch GmbH
Publication of EP0133470A1 publication Critical patent/EP0133470A1/fr
Application granted granted Critical
Publication of EP0133470B1 publication Critical patent/EP0133470B1/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
    • 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
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
    • Y10T—TECHNICAL SUBJECTS COVERED BY FORMER US CLASSIFICATION
    • Y10T137/00—Fluid handling
    • Y10T137/7722—Line condition change responsive valves
    • Y10T137/7781—With separate connected fluid reactor surface
    • Y10T137/7832—Plural valves biased closed
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
    • Y10T—TECHNICAL SUBJECTS COVERED BY FORMER US CLASSIFICATION
    • Y10T137/00—Fluid handling
    • Y10T137/8593—Systems
    • Y10T137/877—With flow control means for branched passages
    • Y10T137/87708—With common valve operator
    • Y10T137/87764—Having fluid actuator

Definitions

  • the invention relates to a fuel injection nozzle according to the preamble of the main claim.
  • injection nozzles of this type in order to end the pre-injection phase, a certain volume of the fuel supplied is swallowed by the evasive accumulator piston, so that the valve needle is braked temporarily or, if appropriately designed, is even returned to the valve seat.
  • the effective pressure area on the valve needle is reduced by the size of the second pressure shoulder, so that a noticeably higher fuel pressure is required to move the valve needle further or to reopen the valve, and the majority of the fuel is injected at this higher pressure.
  • the reduced effective pressure area is maintained until the end of the injection process, which results in an exact injection end with a high closing pressure.
  • the storage piston is arranged displaceably in a cylinder bore in the interior of the valve needle.
  • the confluence of the auxiliary fuel channel lies at one end of the cylinder bore, which forms the second pressure shoulder of the valve needle.
  • the accumulator piston has a valve pin shoulder with a diameter which is pressed by the return spring against the mouth of the auxiliary channel and monitors the mouth.
  • the opening of the auxiliary channel at the end of the pre-injection phase is dependent on the fuel pressure, which propagates almost unthrottled into the auxiliary channel and there acts on the valve surface of the valve pin extension on the accumulator piston.
  • the fuel pressure in the cylinder bore acts on the entire cross-sectional area of the storage piston and quickly leads it to its end position, in which it is supported on the housing and remains approximately until the end of injection.
  • the pressure-dependent introduction of the main injection phase has the disadvantage that when the opening pressures for the valve needle and the evasive piston are changed, the evasive piston can be opened without a pre-injection taking place.
  • the arrangement according to the invention with the characterizing features of the main claim has the advantage that the main injection phase depending on stroke of the valve needle is initiated, which ensures that the measures for reducing the effective pressure area and swallowing part of the supplied fuel are only initiated when the valve needle has released a cross-section for the pre-injection, ie the pre-injection has actually taken place.
  • a simple structural design results if the storage piston is mounted in a cylinder bore of the nozzle housing so as to be displaceable coaxially with the valve needle, during the pre-injection phase it is pressed against the second pressure shoulder of the valve needle and is movable with the valve needle, and even the one that opens into the cylinder bore from the side Auxiliary fuel channel controls. With this arrangement, the valve needle itself does not need to have any means for controlling the emergency fuel channel.
  • the nozzle body and the valve needle of a conventional type can be used if the cylinder bore receiving the storage piston is formed in the nozzle holder and opens into the closing spring chamber, and when the valve needle acts on the storage piston via a tappet which extends into the cylinder bore and carries a piston shoulder sealing the opening of the cylinder bore into the closing spring chamber.
  • a design of an injection nozzle that is not or only slightly extended compared to conventional designs is obtained if the storage piston is designed as an annular body and is mounted in an annular chamber, which is formed between the wall of the cylinder bore in the nozzle body leading the valve needle and a valve needle section with a diameter, and on the an end face is bounded by the annular shoulder serving as the second pressure shoulder at the transition to the stepped valve needle section.
  • Another constructive solution of a stroke-dependent control is, according to the invention, that the storage piston is movably mounted in a cylinder bore in the valve needle and that the auxiliary fuel channel leads through a transverse bore in the valve needle opening into the cylinder bore.
  • the means for opening the auxiliary channel are coupled to the valve needle via a stroke-converting fuel cushion. It is thereby achieved that the overlap of the auxiliary channel in the closed position of the valve needle can be dimensioned greater than the valve needle stroke approximately in the ratio of the stroke ratio of the fuel cushion, as a result of which the tightness of the overlap is increased. Furthermore, the opening speed of the Eilfskanal is increased accordingly.
  • a simple design results if the fuel cushion is in a cylinder bore graduated in diameter is included, the further bore section leads a piston firmly connected to the valve needle and the narrower bore section is delimited by the control piston.
  • the cylinder bore receiving the fuel cushion can advantageously serve as a storage space and the control piston itself can form a storage piston.
  • FIG. 1 shows the first exemplary embodiment, partly in longitudinal section and partly in side view
  • FIGS. 2 to 4 each show a partial longitudinal section through the second, third and fourth exemplary embodiments.
  • the injection nozzle according to FIG. 1 has a nozzle body 10, in which an only indicated valve needle 12 is slidably mounted.
  • the nozzle body 10 is only shown in side view, because the special design of the actual nozzle area with the spray openings is only of minor importance in the present context.
  • the nozzle body 10 is clamped by a union nut 14 to a nozzle holder 16, which has a threaded connector 18 for the connection of a leakage oil line at the upper end.
  • valve needle 12 Between the nozzle body 10 and the nozzle holder 16, an intermediate disk 20 is stretched, which limits the opening stroke of the valve needle 12.
  • the valve needle 12 has an annular shoulder at the transition to a needle section 22 weakened in diameter, which comes to rest on the lower end face of the intermediate disk 20 at the end of the opening stroke.
  • a pressure piece 24 is attached to the needle section 22, on which a closing spring 26 engages, which is arranged in a closing spring chamber 28 in the nozzle holder 16.
  • the closing spring 26 is supported by a spring plate 30 on the bottom of the closing spring chamber 28.
  • a cylinder bore 32 for a storage piston 34 is provided coaxially to the closing spring chamber 28, which starts from the threaded connector 18 and opens into the closing spring chamber 28.
  • a storage spring 36 acts on the storage piston 34, which is supported on a screw piece 38 which is screwed into an outer threaded section of the cylinder bore 32 and contains a central bore 39 for the drainage of leakage oil.
  • a plunger 40 is arranged within the closing spring 26 and seals into the cylinder bore 32 with a piston-shaped extension 42 protrudes. A ring protrudes at the transition to Ansatn 42. At the transition to the neck 42, an annular shoulder is formed, which rests on the spring plate 30 at the top in the position of the plunger 40 shown. The lower end 50 of the plunger 40 extends to a central shoulder surface of the pressure piece 24.
  • the accumulator piston 34 is provided on its end facing the plunger 40 with an elevation 52 which ensures a free space between the accumulator piston 34 and the piston-shaped extension 42 of the plunger 40.
  • the storage spring 36 presses the storage piston 34 against the shoulder 42 of the tappet 40.
  • the accumulator piston 34 covers an annular groove 54 by a small stroke dimension h 1 , which is connected via an auxiliary channel 56 to a connecting piece 58 for a fuel feed line.
  • a main duct 60 leads from the connecting piece 58 into a pressure chamber in the nozzle body 10, in which the valve needle 12 has a first pressure shoulder, as is known, and which is connected to the spray openings via a valve seat monitored by the valve needle 12.
  • the injection nozzle according to FIG. 2 has a valve needle 64, which is displaceably mounted in a nozzle body 66 and has a first pressure shoulder 70 in the area of a pressure chamber 68.
  • the nozzle body 66 and an intermediate disc 72 70 has.
  • the nozzle body 66 and an intermediate disk 72 are by means of a screw nut, not shown a nozzle holder 74 clamped. In this clamped to a nozzle holder 74.
  • a chamber 76 is provided for a closing spring, which acts on the valve needle 64 via a pressure piece 78.
  • the pressure chamber 68 is connected to a fuel connection piece on the nozzle holder 74 via a main channel 80 formed by bores and annular grooves in the individual housing parts.
  • a cylinder bore 82 is provided in the nozzle body 66, in which the valve needle 64 is guided axially with a small amount of movement, shown enlarged in the drawing.
  • the intermediate disk 72 has a central through-bore 84, the diameter of which is smaller than that of the cylinder bore 82, so that there is a in the parting plane of the parts 66, 72. Ring shoulder 86 results.
  • the valve needle 64 has a reduced-diameter section 88 which extends within the cylinder bore 82 and merges into an end pin 89 which passes through the through bore 84 and carries the pressure piece 78.
  • a second pressure shoulder 90 is formed on the valve needle 64, which is opposite to the first pressure shoulder 70 and whose area is smaller than the overall surface area of the fuel acting on the valve needle 64 in the opening direction.
  • An annular chamber 92 is formed between the section 88 of the valve needle 64 and the wall of the cylinder bore 82 and is delimited in the axial direction by the annular shoulder 86 fixed to the housing and the pressure shoulder 90 on the valve needle 64.
  • a storage piston 94 designed as an annular body is slipped onto the section 88, both opposite the extension 88 and opposite the wall of the cylinder bore 32 has only a slight radial movement and which has the total stroke h of the valve movement and which is shorter by the total stroke h g of the valve needle 64 than the annular chamber 92 when the valve needle 64 is in the closed position.
  • the storage piston 94 is provided on its upper edge with three recesses 96, which are evenly distributed over the circumference, for receiving coil springs 97, which are supported on the annular shoulder 86 and press the storage piston 94 against the pressure shoulder 90 'of the valve needle 64.
  • An annular groove 98 is provided in the cylinder bore 82 and is connected to the main channel 80 via an auxiliary channel 100.
  • the lower flank of the annular groove 94 is offset by the length h v of a pre-injection stroke with respect to the pressure shoulder 90 when the valve needle 64 is in the closed position.
  • the chamber 76 in the nozzle holder 74 is, as is known, provided with a Leckol connection.
  • the pressure shoulder 90 reaches the area of the annular groove 98. From this moment on, the fuel pressure acts via the auxiliary channel 100 in the gap between the annular piston 94 and the pressure shoulder 90 and leads the storage piston 94 upwards. until it hits the washer 72.
  • the accumulator piston 94 swallows a certain volume of the fuel and at the same time the fuel pressure exerts a closing force on the pressure shoulder 90, so that the valve needle 64 closes again.
  • the surface of the fuel that acts in the opening direction is reduced by the area of the pressure shoulder 90.
  • the Fuel pressure must now rise to a noticeably higher value, as in the example described above, until the valve needle 64 is again lifted from the valve seat and transferred to its full open position, in which it is supported on the intermediate disk 72 via the storage piston 9 4 .
  • the higher closing pressure remains until the valve needle has returned to its closed position.
  • the injection nozzle according to FIG. 3 has a storage piston 110 which is guided in a cylinder bore 112 of a valve needle 114 with little play.
  • a transverse bore 116 opens into the cylinder bore 112, the upper edge of which, in the closed position of the valve needle 114, is a length of a forward stroke h v away from the lower flank of an annular groove 118, which is connected to a main channel 122 via an auxiliary channel 120.
  • An annular shoulder 128 is formed in the cylinder bore 112, against which the storage piston 110 is pressed by a coil spring 130. This is supported on a plate 132, which is fixedly connected to the valve needle 114 and serves as a pressure piece for a closing spring 134, which acts on the valve needle 114 in the closing direction.
  • the closing spring 134 is arranged in a chamber 136, on the bottom 138 of which it is supported.
  • a stop bolt 140 is also fastened to the bottom 138 and, in cooperation with the plate 132, limits the valve needle stroke to the dimension h g .
  • a pin 142 is formed on the accumulator piston 110 and, in cooperation with the stop pin 140, the entire Limit the stroke of the accumulator piston 110 to the dimension h s .
  • the chamber 136 is connected to a leak oil line 144.
  • the transverse bores 116 and the annular groove 118 overlap, so that the force pressure builds up in the cylinder bore 11 below the accumulator piston 110 and guides the accumulator piston up to the stop on the stop pin 140 .
  • the accumulator piston 110 swallows a certain volume of fuel so that the fuel pressure is applied to the bottom surface 146 of the cylinder bore 112 so that the valve needle 114 is returned to the valve seat. If the fuel pressure subsequently rises to a correspondingly higher value, the valve needle is moved again in the opening direction until the plate 132 strikes the stop bolt 140 after the entire stroke h g has been covered . The increased closing pressure is then maintained until the valve needle is completely closed.
  • the storage piston 110 which returns to its illustrated starting position under the influence of the coil spring 130, displaces the previously absorbed fuel volume into the main channel 122 as long as the Cover transverse bore 116 and annular groove 118. Thereafter, the fuel volume that may still need to be displaced can reach the leakage oil line 144 via the radial play between the storage piston 110 and the wall of the cylinder bore 112, and via the chamber 136.
  • auxiliary channel 56 corresponds in principle to the injection nozzle according to FIG. 1.
  • the means for opening the auxiliary channel 56 are coupled to the valve needle via a stroke-converting fuel cushion 152.
  • the fuel cushion 152 is enclosed in a cylinder bore 154 which has two bore sections 156, 158 of different diameters.
  • a piston 160 is tightly guided in the larger bore section 156 and is mechanically coupled to the valve needle via the tappet 40.
  • the accumulator piston 150 is tightly guided, which has an annular collar 162 which, in the closed position of the valve needle, is pressed by a return spring 164 against a shoulder 166 fixed to the housing.
  • the auxiliary channel 56 opens into an annular groove 54 which surrounds the narrower bore section 158 of the cylinder bore 154, which at the same time forms the storage space.
  • the storage piston 150 is dimensioned such that it covers the annular groove 54 by the dimension h 2 in the starting position shown.
  • the dimension h 2 can or must be dimensioned larger than the dimension h 1 in FIG. 1 because the accumulator piston 150 a distance larger than the diameter ratio d./d 2 of the pistons as the valve needle or the piston 160 travels. This improves the brightness of the overlap of the auxiliary channel 56 or the annular groove 54. Otherwise, the processes run as in the embodiment according to FIG. 1.
  • the stroke of the accumulator piston 150 is limited by an inserted socket 168.

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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)
EP19840107559 1983-08-10 1984-06-29 Injecteur de carburant pour moteurs à combustion interne Expired EP0133470B1 (fr)

Applications Claiming Priority (4)

Application Number Priority Date Filing Date Title
DE3328824 1983-08-10
DE19833328824 DE3328824A1 (de) 1983-08-10 1983-08-10 Kraftstoff-einspritzduese fuer brennkraftmaschinen
DE19833344396 DE3344396A1 (de) 1983-12-08 1983-12-08 Kraftstoff-einspritzduese fuer brennkraftmaschinen
DE3344396 1983-12-08

Publications (2)

Publication Number Publication Date
EP0133470A1 true EP0133470A1 (fr) 1985-02-27
EP0133470B1 EP0133470B1 (fr) 1988-05-11

Family

ID=25813075

Family Applications (1)

Application Number Title Priority Date Filing Date
EP19840107559 Expired EP0133470B1 (fr) 1983-08-10 1984-06-29 Injecteur de carburant pour moteurs à combustion interne

Country Status (3)

Country Link
US (1) US4566635A (fr)
EP (1) EP0133470B1 (fr)
DE (1) DE3471134D1 (fr)

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US5934254A (en) * 1998-03-27 1999-08-10 Cummins Engine Company, Inc. Top stop assembly for a fuel injector

Families Citing this family (18)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE3610658A1 (de) * 1985-11-21 1987-05-27 Bosch Gmbh Robert Kraftstoff-einspritzduese fuer brennkraftmaschinen
JPH07109182B2 (ja) * 1986-11-11 1995-11-22 日本電装株式会社 内燃機関用燃料噴射装置
JPH07109181B2 (ja) * 1986-12-05 1995-11-22 日本電装株式会社 内燃機関用燃料噴射装置
JP2523759B2 (ja) * 1987-02-04 1996-08-14 フエスト − アルピネ オウトモチブ ゲゼルシャフト ミットベシュレンクテル ハフツンク 燃料噴射ノズル
DE3811885C2 (de) * 1988-04-09 1994-10-06 Daimler Benz Ag Kraftstoffeinspritzvorrichtung mit Vor- und Haupteinspritzung für eine Brennkraftmaschine, insbesondere solche mit Luftverdichtung und Selbstzündung
DE3941151A1 (de) * 1989-12-13 1991-06-20 Bosch Gmbh Robert Kraftstoff-einspritzduese fuer brennkraftmaschinen
CH689267A5 (de) * 1994-05-02 1999-01-15 Eth Christian Mathis Dipl Ing Einspritzventil fuer eine Kraftstoffeinspritzanlage einer Brennkraftmaschine, insbesondere eines Dieselmotors.
US5429309A (en) * 1994-05-06 1995-07-04 Caterpillar Inc. Fuel injector having trapped fluid volume means for assisting check valve closure
GB9525369D0 (en) 1995-12-12 1996-02-14 Lucas Ind Plc Injector
GB9623469D0 (en) * 1996-11-12 1997-01-08 Lucas Ind Plc Injector
GB9700491D0 (en) * 1997-01-11 1997-02-26 Lucas Ind Plc Injector
US5947382A (en) * 1997-06-11 1999-09-07 Stanadyne Automotive Corp. Servo controlled common rail injector
US6360727B1 (en) 2000-03-14 2002-03-26 Alfred J. Buescher Reduce initial feed rate injector with fuel storage chamber
US6568602B1 (en) 2000-05-23 2003-05-27 Caterpillar Inc Variable check stop for micrometering in a fuel injector
DE10031576C2 (de) * 2000-06-29 2002-07-11 Bosch Gmbh Robert Druckgesteuerter Injektor zum Einspritzen von Kraftstoff
US7334741B2 (en) * 2005-01-28 2008-02-26 Cummins Inc. Fuel injector with injection rate control
US7900604B2 (en) * 2005-06-16 2011-03-08 Siemens Diesel Systems Technology Dampening stop pin
US10753493B2 (en) * 2018-03-29 2020-08-25 Hamilton Sunstrand Corporation Valve with segmented spring guide assembly

Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR707617A (fr) * 1929-12-31 1931-07-10 Sulzer Ag Soupape à accumulation à commande hydraulique pour moteurs à combustion interne à injection
FR851618A (fr) * 1938-03-15 1940-01-12 Dispositif d'injection de combustible pour moteurs à combustion interne
CH235636A (de) * 1943-04-21 1944-12-15 Ag Scintilla Einspritzvorrichtung für Brennkraftmaschinen.
US2558148A (en) * 1948-03-08 1951-06-26 Cav Ltd Liquid fuel injection nozzle for internal-combustion engines
US2813752A (en) * 1956-11-13 1957-11-19 Studebaker Packard Corp Two stage fuel injection nozzle

Family Cites Families (10)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3430866A (en) * 1967-03-31 1969-03-04 Int Harvester Co Fuel injection nozzle
GB1314017A (en) * 1969-07-07 1973-04-18 Cav Ltd Fuel injection nozzles
GB1420931A (en) * 1972-01-15 1976-01-14 Cav Ltd Fuel injection nozzles
DE2235083A1 (de) * 1972-07-18 1974-01-31 Bosch Gmbh Robert Kraftstoffeinspritzduese fuer brennkraftmaschinen
DE2500644C2 (de) * 1975-01-09 1988-07-07 Klöckner-Humboldt-Deutz AG, 5000 Köln Kraftstoffeinspritzventil für Brennkraftmaschinen
DE2555019A1 (de) * 1975-12-06 1977-06-16 Bosch Gmbh Robert Kraftstoffeinspritzventil fuer vor- und haupteinspritzung
US4186884A (en) * 1978-01-11 1980-02-05 Lucas Industries Limited Liquid fuel injection nozzles
DE2833431C2 (de) * 1978-07-29 1987-05-14 Robert Bosch Gmbh, 7000 Stuttgart Kraftstoffeinspritzdüse für Brennkraftmaschinen
JPS57160966U (fr) * 1981-04-03 1982-10-08
US4402456A (en) * 1982-04-02 1983-09-06 The Bendix Corporation Double dump single solenoid unit injector

Patent Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR707617A (fr) * 1929-12-31 1931-07-10 Sulzer Ag Soupape à accumulation à commande hydraulique pour moteurs à combustion interne à injection
FR851618A (fr) * 1938-03-15 1940-01-12 Dispositif d'injection de combustible pour moteurs à combustion interne
CH235636A (de) * 1943-04-21 1944-12-15 Ag Scintilla Einspritzvorrichtung für Brennkraftmaschinen.
US2558148A (en) * 1948-03-08 1951-06-26 Cav Ltd Liquid fuel injection nozzle for internal-combustion engines
US2813752A (en) * 1956-11-13 1957-11-19 Studebaker Packard Corp Two stage fuel injection nozzle

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US5934254A (en) * 1998-03-27 1999-08-10 Cummins Engine Company, Inc. Top stop assembly for a fuel injector

Also Published As

Publication number Publication date
US4566635A (en) 1986-01-28
EP0133470B1 (fr) 1988-05-11
DE3471134D1 (en) 1988-06-16

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