US3443760A - Fail-safe fuel injection nozzle - Google Patents

Fail-safe fuel injection nozzle Download PDF

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Publication number
US3443760A
US3443760A US633794A US3443760DA US3443760A US 3443760 A US3443760 A US 3443760A US 633794 A US633794 A US 633794A US 3443760D A US3443760D A US 3443760DA US 3443760 A US3443760 A US 3443760A
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United States
Prior art keywords
nozzle
primary
valve
flow
fuel
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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
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US633794A
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English (en)
Inventor
Harold C Simmons
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.)
Parker Hannifin Corp
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Parker Hannifin Corp
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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F23—COMBUSTION APPARATUS; COMBUSTION PROCESSES
    • F23D—BURNERS
    • F23D11/00—Burners using a direct spraying action of liquid droplets or vaporised liquid into the combustion space
    • F23D11/24—Burners using a direct spraying action of liquid droplets or vaporised liquid into the combustion space by pressurisation of the fuel before a nozzle through which it is sprayed by a substantial pressure reduction into a space
    • F23D11/26—Burners using a direct spraying action of liquid droplets or vaporised liquid into the combustion space by pressurisation of the fuel before a nozzle through which it is sprayed by a substantial pressure reduction into a space with provision for varying the rate at which the fuel is sprayed

Definitions

  • the present invention relates generally, as indicated, to a fail safe fuel injection nozzle and more particularly to a dual orifice fuel injection nozzle having means for blocking the flow through the secondary discharge orifice in the event of breakage or failure of the secondary flow control valve stern, valve biasing spring, or retainer therefor.
  • ⁇ Dual orifice nozzles are usually provided with two separate nozzles; a primary nozzle having a primary discharge orifice through which fuel is discharged at low fuel pressures for low fuel flow; and a secondary nozzle having a secondary discharge orifice through which fuel is additionally discharged at higher fuel pressures for greater rates of fuel flow.
  • the secondary flow is completely shut off by the head of the secondary flow control valve in the case of breakage or failure of the valve stem or other associated parts to prevent such overflow and improper atomization of the fuel.
  • Another object is to provide such a nozzle with a novel adaptor for supporting the shutoff plate in the nozzle body and including separate passages communicating with the primary and secondary orifices ⁇ of the nozzle.
  • the invention comprises the features hereinafter fully described and particularly pointed out in the claims, the following description and the annexed drawing setting forth in detail certain illustrative embodiments of the invention, these being indicative, however, of but a few of the various ways in which the principles of the invention may be employed.
  • FIG. 1 is a side elevation view of one form of fuel injection nozzle constructed in accordance with this invention
  • FIG. 2 is an enlarged central longitudinal section through the nozzle of FIG. 1 in which the secondary flow control valve is shown in phantom lines in both the normal full open position and flow blocking position seated against the secondary nozzle shutoff plate;
  • FIG. 3 is an enlarged central longitudinal section similar to FIG. 2 but of another form of nozzle in accordance with this invention.
  • FIG. 4 is a transverse section through the nozzle of FIG. 3 taken on the plane of the line 4 4 thereof.
  • such fuel injection nozzle is generally indicated at 1 and cornprises a body member 2 in which there is received a primary nozzle 3 having a primary plug 4 partially threaded into the primary nozzle 3 from the rear.
  • the forward end of the primary plug 4 is of reduced diameter and cha-mferred at 6 for establishing fluid tight engagement with the correspondingly tapered wall 7 ⁇ of a spin chamber 8 located forward of the primary plug 4.
  • Fluid is supplied to the spin chamber 8 for discharge from the primary discharge orifice 9 through angularly disposed swirl slots 11 in the forward end wall 12 of the primary plug 4i which impart a swirling motion to the fuel in known manner for better atomization.
  • the outer wall 13 of the primary nozzle 3 is concentrically located in spaced relation from the inner wall 14 of the body member 2 by an outwardly directed flange 15 on the rear end of the primary nozzle 3 closely slidably received in a counterbore 16.
  • Such outer and inner walls 13, 14 extend forwardly in a longitudinal direction and then taper inwardly to define therebetween a secondary nozzle 17 comprising a secondary spin chamber 19 and secondary discharge orifice 20 surrounding the primary discharge tone 9.
  • 'both such discharge orifices 9 and 20 communicate with :a common exit orifice 21 in the body member 2.
  • a shroud 23 may be provided on the body member 2 outwardly of the exit orifice 21 and secured thereto in suitable manner, as by welding at 24 or the like.
  • the primary plug 4 extends rearwardly beyond the primary nozzle flange 15 and has threaded thereon an adaptor 26 whose forward end face 27 is flush against the back face 28 of such flange to provide a fluid seal therewith.
  • a generally cylindrical strainer support 29 having threaded engagement with the rearward end of the body member 2 surrounds the adapter 26 in spaced relation to define therebetween an annular flow passage 30 which communicates with the interior 31 of the primary plug 4 via one -or more radial passages 32 in the adapter 26 and an internally threaded central recess 33 in the adapter into which the primary plug 4 is threadedly received.
  • a ring 37 having tabs 38 for receipt in axial slots 39 in the rear end of the body member 2 may be crimped radially inwardly into circumferentially spaced recesses 40 in the outer surface of the strainer support 29 to lock these two members together.
  • a pntle valve 44 having a stem 45 telescopically received in the bore 46 of a sleeve 47.
  • the forward end or head 48 of the pintle valve 45 is tapered outwardly to permit engagement with a seat 49 on the sleeve 47, and there is a piston 50 on the valve stem 45 adjacent the rear end thereof which is closely slidably received in a liner 51 surrounding the sleeve 47 for guiding the valve 44 during its movement toward and away from the seat 49.
  • a helical groove 52 in the outer surface of the piston 50 permits the escape of stagnant fuel which may become trapped behind the piston.
  • the piston 50 may be retained on the valve stem 45 by a C-washer 53 received in a peripheral groove 54 on the valve stem 45 and a retaining cap 55 which fits over the C-washer 53 and is held in place by a cotter pin 56 inserted through a transverse bore in the stem 45.
  • a spacer element 60 and spring support washer 61 may be disposed between the rearward end of the liner 51 and bottom wall 62 of the strainer support 29 for maintaining the adaptor 26, primary nozzle flange 15, and body member 2 in firm sealing engagement with each other.
  • An end cap 65 slidably received on an extension 66 of the strainer support 29 and held in place by a retaining ring 67 engaged in a groove 68 in such extension has a forwardly directed flange 69 which overlies one end of the cylindrical strainer 34 to hold the same in place.
  • the sleeve 47 has a rearwardly facing shoulder 70 which is engaged by a washer 71, and there is a compression spring 72 disposed between the washer 71 and piston 50 for yieldably maintaining the valve head 48 in seating engagement with the seat 49. Shims 73 of different thicknesses may be interposed between the piston 50 and C-washer 53 to vary the compressive force exerted by the spring 72 on the pntle valve 44.
  • the bias of the spring 72 will be overcome and the pntle valve 44 will move away from its seat 49 to provide for additional fuel flow through the secondary discharge orifice 20 via a ⁇ central recess 75 in the adaptor 26 into which the pntle valve 44 projects, a generally axially extending passage 76 in the adaptor 26 communicating with an annular chamber 77 in the forward end face 27 of such adaptor, and holes 78 in the primary nozzle flange 15 which may be angularly disposed to provide a swirling motion to the fuel as it enters the secondary spin chamber 19.
  • valve head 48 will be lifted progressively away from its seat 49 for additional secondary fuel flow which varies automatically with changes in fuel pressure and may be as much as ten times the primary fuel flow.
  • valve stem 45 break or the spring 72 or retainer cap 55 fail or become disengaged from the valve stem, even at low fuel pressures the pntle valve 44 would remain wide open resulting in uncontrolled ow through the secondary discharge orifice 20 and improper atomization of the fuel except for the shutoff plate 80 which is disposed in the recess 75 in the adaptor 26.
  • the shutoff plate 80 which is disposed in the recess 75 in the adaptor 26.
  • the shutoff plate has an annular side wall 81 terminating in an outturned fiange 82 which extends between the adjacent ends of the adaptor 26 and sleeve 47 to provide a fluid seal precluding primary fuel in the annular passage 30 from entering the recess 75.
  • the length of the side wall 81 is such that the shutoff plate 80 is located a sufficient distance from the adjacent end face of the sleeve 45 to provide the necessary clearance for movement of the pntle valve from the fully closed position shown in solid lines t-o the intermediate or normal full open position indicated in phantom lines at 48 without restricting the flow around the valve head 48 and through the central opening 83 in the shutoff plate.
  • the distance between the rear face 84 of the shutoff plate 80 and the flat front face 85 of the valve head 48 when in the fully closed position is slightly more than twice the distance that the valve moves between the fully closed and fully open positions.
  • shutoff plate 80 acts as a valve seat for the pntle valve 45 which is engaged by the fiat front face 85 of the valve when it comes into Contact with the shutoff plate 80 because of a broken valve stem or the like.
  • FIGS. 3 and 4 there is shown another form of fuel injection nozzle which like the fuel injection nozzle 1 of FIGS. 1 and 2 has a body member 91 in which there is concentn'cally disposed a primary nozzle 92 having a spin chamber 93 therein and a primary discharge orifice 94 communicating with the exit orifice 95 of the body member 91.
  • the nozzle 90 has a secondary nozzle 96 surrounding the primary nozzle 92 which comprises a secondary spin chamber 97 defined between the inner and outer walls 98 and 99 of the body member 91 and primary nozzle 92, respectively, communicating with a secondary discharge orifice 100 which continues into the exit orifice 95.
  • shutoff plate 101 interposed between the primary nozzle 92 and valve housing 102 having a central opening 103 therethrough which is closed off by engagement of the head 104 of the pntle valve 105 with the plate 101 as seen in phantom lines at 104" to halt secondary flow to the secondary discharge orifice 100 via radial passages 106 and longitudinal bore 107 in the valve housing 102 in which the valve 105 is disposed and angularly disposed slots 108 in the outturned flange 109 of the primary nozzle 92 in the event of failure of the valve stem 110, valve biasing spring 111, or spring retainer 112.
  • a C-washer 113 received in a groove 114 in the rear end of the valve stem.
  • shutoff plate 101 has an outer sleeve portion 115 which extends axially beyond both faces of the shutoff plate 101 to establish a fluid seal with the adjacent faces of the primary nozzle 92 and valve housing 102 and provide the necessary spacing between the shutoff plate and valve head 104 when in the full open position (104') for unrestricted fiow through the central aperture 103 and secondary discharge orifice 101.
  • a plug 116 adjacent the rear end of the primary spin chamber 93 precludes the secondary flow from entering the primary nozzle 92.
  • Primary flow is continually supplied to the primary nozzle 92 through an annular passageway 117 surrounding the sleeve portion 115 which communicates with a pair of oppositely disposed chambers 118 between the primary nozzle 92 and valve body '91, and through tangential holes 119 in the primary nozzle ange 109.
  • Proper sealing engagement between the contacting surfaces of the valve housing 102, sleeve portion 115, primary nozzle ange 109, and body member 91 is established by tightening the valve housing 102 which has threaded engagement with the body member 91.
  • a lock ring 121 having tabs 122 projecting into circumferentially spaced slots 123 in the valve housing 102 may be crimped at circumferentially spaced zones into slots 124 in the body member 91 for locking such valve housing and body member together.
  • the sleeve portion 115 overlies a shoulder 125 on the forward end of the valve housing 102 for concentrically locating the plate 101 with respect to the valve 105.
  • the operation of the fuel injection nozzle 90- is substantially the same as the nozzle 1.
  • the flow is only through the primary discharge orifice 94 via the annular passageway 117, chambers 118, holes 119, and spin chamber 93.
  • the fuel pressure acting on the valve head 104 is sufficiently high to overcome the bias of the spring 111, there is additional fuel fiow through the secondary discharge orifice 100 via the central aperture 103 in the shutoff plate 101, slots 108, and spin chamber 97 which flow automatically varies in accordance with the fuel pressure.
  • the valve head 104 will close off the central aperture 103 much in the same manner that the aperture 83 is closed off by the valve head 48 of the nozzle 1 previously discussed.
  • a dual orifice flow nozzle having a fluid inlet passage and primary and secondary flow passages through which fuel from said inlet passage is adapted to flow through the primary and secondary discharge orifices of primary and secondary discharge nozzles, and a pressure actuated valve means in said secondary flow passage effective when closed at low pressures to cut off flow of fluid to said secondary nozzle whereby fiuid fiows only through said primary nozzle at such low pressures, and effective when opened by higher pressures to permit flow of fluid to said secondary nozzle to supplement the flow through said primary nozzle; wherein the improvement comprises providing a shutoff plate, means for supporting said shutoff plate in said secondary ow passage downstream of said valve means, said shutoff plate having an opening through which the secondary fluid ows when said valve means is opened as aforesaid, said valve means when moved beyond full open position due to failure of any part of said valve means being adapted to engage said plate and close off said opening for blocking such secondary fiuid flow, said primary fiow passage bypassing said valve means and shutoff plate and said primary discharge
  • the dual orifice flow nozzle of claim 1 wherein the improvement further comprises a spring means and spring retainer operatively connecting said spring means to said valve means for yieldably maintaining said valve means in closed position, said valve means in the event of failure of said spring means or retainer being adapted to engage said plate and close off said opening therein for blocking such secondary fluid flow as aforesaid.
  • said means for supporting said shutoff plate comprises an adaptor disposed between said discharge nozzles and said shutoff plate, said adaptor having first and second iiow passages therein which constitute a part of said primary and secondary flow passages, respectively, said adaptor also having a recess in the rear face thereof in said secondary flow passage, said shutoff plate being disposed in said recess intermediate the inner and outer ends thereof to provide sufficient clearance between said shutoff plate and both the inner end of said recess and said valve means when in the full open position so as not to restrict the flow through the opening in said shutoff plate and into said second fiow passage.
  • the dual orifice nozzle of claim 4 wherein the improvement further comprises a sleeve having a bore in which said valve means is slidably receiver, an apertured liner surrounding said sleeve, and an apertured support member surrounding said liner having threaded engagement with the body of said nozzle, said sleeve having an outwardly extending shoulder interposed between said adaptor and liner, and said support member having an end wall which forces said adaptor and sleeve into sealing contact with each other through said liner upon tightening of said support member to preclude primary fluid flow from entering said secondary fiow passage via said recess in said adaptor.
  • the dual orifice nozzle of claim 4 wherein the improvement further comprises a plug having threaded engagement with both said primary nozzle and said adaptor, and a passage through said plug communicating said primary discharge orifice with said first flow passage in said adaptor.
  • valve housing having an axial bore in which said valve means is slidably disposed said shutoff plate being located between said primary nozzle and said housing and having an annular sleeve portion extending axially beyond opposite faces of said shutoff plate to provide sufficient clearance of said shutoff plate with said primary discharge nozzle and said valve means when in the full open position so as not to restrict the ow through the opening in said shutoff plate.
  • the dual orifice nozzle of claim 8 wherein the improvement Afurther comprises an annular shoulder on the forward end of said valve housing over which one end of said annular sleeve portion is slidably received for concentrically locating said annular sleeve por-tion and thus said shutoff plate With respect to said valve means, said valve housing having threaded engagement with the body of said dual orifice flow nozzle whereby said valve housing is tightened, the adjacent surfaces of said valve housing, annular sleeve portion, and primary nozzle are held in sealing engagement with each other.
  • the dual orifice nozzle of claim 9 wherein the improvement further comprises an annular passage surrounding said annular sleeve portion and communicating with circumferentially spaced chambers around said primary nozzle, said annular passage and circumferentially spaced chambers constituting part of said primary flow passage.
  • a dual orifice nozzle comprising a body member having a primary nozzle including a primary spin chamber and primary discharge orifice disposed therein and a secondary nozzle including a secondary spin chamber and secondary discharge orifice concentrically disposed about said primary nozzle, a fluid inlet, primary and secondary fiow passages communicating said inlet with said primary and secondary spin chambers, respectively, a pressure actuated valve means in said secondary flow passage effective when closed at low pressures to cut off flow of fiuid to said secondary discharge orifice whereby fiuid flows only through said primary discharge orifice at such low pressures, and effective when opened by higher pressures to permit flow of fluid to said secondary discharge orifice to supplement the flow through said primary discharge orilice, and a shutoi plate in said secondary flow passage downstream of said valve means, said shutolf plate having an opening therein through which the secondary fluid ows when said Valve means is opened as aforesaid, said valve means when moved beyond full open position due to failure of a part of said valve means being
  • the dual réelle nozzle of claim 12 further comprising radial holes in said outturned flange communicating said primary flow passage with said primary spin chamber.

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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)
US633794A 1967-04-26 1967-04-26 Fail-safe fuel injection nozzle Expired - Lifetime US3443760A (en)

Applications Claiming Priority (1)

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US63379467A 1967-04-26 1967-04-26

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US633794A Expired - Lifetime US3443760A (en) 1967-04-26 1967-04-26 Fail-safe fuel injection nozzle

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US (1) US3443760A (en:Method)
BE (1) BE714168A (en:Method)
DE (1) DE1751250A1 (en:Method)
GB (1) GB1182392A (en:Method)

Cited By (26)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3520480A (en) * 1968-04-24 1970-07-14 Ex Cell O Corp Fuel spray nozzle
DE2203259A1 (de) * 1971-01-25 1972-08-10 Parker Hannifin Corp Mengenregelventil fuer Kraftstoffeinspritzduesen
US3685741A (en) * 1970-07-16 1972-08-22 Parker Hannifin Corp Fuel injection nozzle
US3785570A (en) * 1972-08-30 1974-01-15 Us Army Dual orifice fuel nozzle with air-assisted primary at low flow rates
US3804333A (en) * 1972-10-16 1974-04-16 Gulf Research Development Co Liquid waste burner
US3829027A (en) * 1973-02-28 1974-08-13 Src Lab Variable vacuum producing nozzle
US4317542A (en) * 1979-02-23 1982-03-02 Toyota Jidosha Kogyo Kabushiki Kaisha Fuel injector
FR2502701A1 (fr) * 1981-03-26 1982-10-01 Renault Vehicules Ind Systeme d'injection a pilotage de l'injecteur, pour un moteur a combustion interne
US4491272A (en) * 1983-01-27 1985-01-01 Ex-Cell-O Corporation Pressure atomizing fuel injection assembly
US4798330A (en) * 1986-02-14 1989-01-17 Fuel Systems Textron Inc. Reduced coking of fuel nozzles
US5078324A (en) * 1990-10-11 1992-01-07 United Technologies Corporation Pressurized stem air blast fuel nozzle
US5421521A (en) * 1993-12-23 1995-06-06 Caterpillar Inc. Fuel injection nozzle having a force-balanced check
US5513798A (en) * 1993-08-08 1996-05-07 Tavor; Elhanan Atomizer
US5628293A (en) * 1994-05-13 1997-05-13 Caterpillar Inc. Electronically-controlled fluid injector system having pre-injection pressurizable fluid storage chamber and direct-operated check
US5673669A (en) * 1994-07-29 1997-10-07 Caterpillar Inc. Hydraulically-actuated fluid injector having pre-injection pressurizable fluid storage chamber and direct-operated check
US5687693A (en) * 1994-07-29 1997-11-18 Caterpillar Inc. Hydraulically-actuated fuel injector with direct control needle valve
US5697342A (en) * 1994-07-29 1997-12-16 Caterpillar Inc. Hydraulically-actuated fuel injector with direct control needle valve
US5826562A (en) * 1994-07-29 1998-10-27 Caterpillar Inc. Piston and barrell assembly with stepped top and hydraulically-actuated fuel injector utilizing same
US6082332A (en) * 1994-07-29 2000-07-04 Caterpillar Inc. Hydraulically-actuated fuel injector with direct control needle valve
US6425375B1 (en) 1998-12-11 2002-07-30 Caterpillar Inc. Piston and barrel assembly with stepped top and hydraulically-actuated fuel injector utilizing same
US6575137B2 (en) 1994-07-29 2003-06-10 Caterpillar Inc Piston and barrel assembly with stepped top and hydraulically-actuated fuel injector utilizing same
US20100107653A1 (en) * 2008-11-05 2010-05-06 Paskevich Stephen C Nozzle tip assembly with secondary retention device
US20180250697A1 (en) * 2017-03-06 2018-09-06 Engineered Spray Components LLC Stacked pre-orifices for sprayer nozzles
US10427182B2 (en) * 2014-07-28 2019-10-01 Yu Chiung Huang Atomizing nozzle structure with filtering assembly
US10961967B1 (en) 2017-12-12 2021-03-30 Microfabrica Inc. Fuel injector systems, fuel injectors, fuel injector nozzles, and methods for making fuel injector nozzles
US11262012B2 (en) 2019-09-09 2022-03-01 Engineered Controls International, Llc Coupling nozzle for cryogenic fluid

Families Citing this family (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN118847395B (zh) * 2024-09-25 2024-12-03 江苏欧威环保科技发展有限公司 一种雾化喷嘴

Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2213928A (en) * 1936-11-04 1940-09-03 Weber Engine Company Fuel injection nozzle
US2893647A (en) * 1957-05-06 1959-07-07 Gen Motors Corp Adjustable fuel nozzle
US3095153A (en) * 1961-11-20 1963-06-25 Delavan Mfg Company Variable area spray nozzle

Patent Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2213928A (en) * 1936-11-04 1940-09-03 Weber Engine Company Fuel injection nozzle
US2893647A (en) * 1957-05-06 1959-07-07 Gen Motors Corp Adjustable fuel nozzle
US3095153A (en) * 1961-11-20 1963-06-25 Delavan Mfg Company Variable area spray nozzle

Cited By (33)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3520480A (en) * 1968-04-24 1970-07-14 Ex Cell O Corp Fuel spray nozzle
US3685741A (en) * 1970-07-16 1972-08-22 Parker Hannifin Corp Fuel injection nozzle
DE2203259A1 (de) * 1971-01-25 1972-08-10 Parker Hannifin Corp Mengenregelventil fuer Kraftstoffeinspritzduesen
US3727636A (en) * 1971-01-25 1973-04-17 Parker Hannifin Corp Flow control valve for fuel injection nozzle
US3785570A (en) * 1972-08-30 1974-01-15 Us Army Dual orifice fuel nozzle with air-assisted primary at low flow rates
US3804333A (en) * 1972-10-16 1974-04-16 Gulf Research Development Co Liquid waste burner
US3829027A (en) * 1973-02-28 1974-08-13 Src Lab Variable vacuum producing nozzle
US4317542A (en) * 1979-02-23 1982-03-02 Toyota Jidosha Kogyo Kabushiki Kaisha Fuel injector
FR2502701A1 (fr) * 1981-03-26 1982-10-01 Renault Vehicules Ind Systeme d'injection a pilotage de l'injecteur, pour un moteur a combustion interne
EP0061979A1 (fr) * 1981-03-26 1982-10-06 RENAULT VEHICULES INDUSTRIELS Société dite: Système d'injection à pilotage de l'injecteur, pour un moteur à combustion interne
US4491272A (en) * 1983-01-27 1985-01-01 Ex-Cell-O Corporation Pressure atomizing fuel injection assembly
US4798330A (en) * 1986-02-14 1989-01-17 Fuel Systems Textron Inc. Reduced coking of fuel nozzles
US5078324A (en) * 1990-10-11 1992-01-07 United Technologies Corporation Pressurized stem air blast fuel nozzle
US5513798A (en) * 1993-08-08 1996-05-07 Tavor; Elhanan Atomizer
US5421521A (en) * 1993-12-23 1995-06-06 Caterpillar Inc. Fuel injection nozzle having a force-balanced check
US5628293A (en) * 1994-05-13 1997-05-13 Caterpillar Inc. Electronically-controlled fluid injector system having pre-injection pressurizable fluid storage chamber and direct-operated check
US5673669A (en) * 1994-07-29 1997-10-07 Caterpillar Inc. Hydraulically-actuated fluid injector having pre-injection pressurizable fluid storage chamber and direct-operated check
US5687693A (en) * 1994-07-29 1997-11-18 Caterpillar Inc. Hydraulically-actuated fuel injector with direct control needle valve
US5697342A (en) * 1994-07-29 1997-12-16 Caterpillar Inc. Hydraulically-actuated fuel injector with direct control needle valve
US5738075A (en) * 1994-07-29 1998-04-14 Caterpillar Inc. Hydraulically-actuated fuel injector with direct control needle valve
US5826562A (en) * 1994-07-29 1998-10-27 Caterpillar Inc. Piston and barrell assembly with stepped top and hydraulically-actuated fuel injector utilizing same
US6065450A (en) * 1994-07-29 2000-05-23 Caterpillar Inc. Hydraulically-actuated fuel injector with direct control needle valve
US6082332A (en) * 1994-07-29 2000-07-04 Caterpillar Inc. Hydraulically-actuated fuel injector with direct control needle valve
US6575137B2 (en) 1994-07-29 2003-06-10 Caterpillar Inc Piston and barrel assembly with stepped top and hydraulically-actuated fuel injector utilizing same
US6425375B1 (en) 1998-12-11 2002-07-30 Caterpillar Inc. Piston and barrel assembly with stepped top and hydraulically-actuated fuel injector utilizing same
US20100107653A1 (en) * 2008-11-05 2010-05-06 Paskevich Stephen C Nozzle tip assembly with secondary retention device
US9464808B2 (en) * 2008-11-05 2016-10-11 Parker-Hannifin Corporation Nozzle tip assembly with secondary retention device
US10427182B2 (en) * 2014-07-28 2019-10-01 Yu Chiung Huang Atomizing nozzle structure with filtering assembly
US20180250697A1 (en) * 2017-03-06 2018-09-06 Engineered Spray Components LLC Stacked pre-orifices for sprayer nozzles
US10603681B2 (en) * 2017-03-06 2020-03-31 Engineered Spray Components LLC Stacked pre-orifices for sprayer nozzles
US10961967B1 (en) 2017-12-12 2021-03-30 Microfabrica Inc. Fuel injector systems, fuel injectors, fuel injector nozzles, and methods for making fuel injector nozzles
US11262012B2 (en) 2019-09-09 2022-03-01 Engineered Controls International, Llc Coupling nozzle for cryogenic fluid
US12152713B2 (en) 2019-09-09 2024-11-26 Engineered Controls International, Llc Coupling nozzle for cryogenic fluid

Also Published As

Publication number Publication date
GB1182392A (en) 1970-02-25
BE714168A (en:Method) 1968-10-25
DE1751250A1 (de) 1971-06-16

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