WO1983000639A1 - Springless fuel injection nozzle - Google Patents
Springless fuel injection nozzle Download PDFInfo
- Publication number
- WO1983000639A1 WO1983000639A1 PCT/US1980/000122 US8000122W WO8300639A1 WO 1983000639 A1 WO1983000639 A1 WO 1983000639A1 US 8000122 W US8000122 W US 8000122W WO 8300639 A1 WO8300639 A1 WO 8300639A1
- Authority
- WO
- WIPO (PCT)
- Prior art keywords
- valve
- cavity
- housing
- cavity portion
- lower cavity
- 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.)
- Ceased
Links
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
- F02M61/04—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
- F02M61/10—Other injectors with elongated valve bodies, i.e. of needle-valve type
-
- 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
- F02M47/00—Fuel-injection apparatus operated cyclically with fuel-injection valves actuated by fluid pressure
- F02M47/06—Other fuel injectors peculiar thereto
Definitions
- This invention relates generally to fluid sprinkling, spraying and diffusing and more particularly to fluid pressure responsive discharge modifiers such as fuel injectors.
- fuel injection nozzle valves operate in response to high pressure fuel creating forces acting on differential areas of the valve causing rapid reciprocation of the valve.
- the rapid reciproca ⁇ tion causes intermittent seating and unseating of a tip of the valve with a valve seat which permits the fuel to be injected into engine cylinders.
- fuel at one pressure acts on one side of the valve to lift or unseat the valve for starting fuel injection, and fuel at another pressure acts opposite the one pressure to seat the valve for stopping fuel injection.
- Another type of fuel injector utilizes fuel pressure acting on one side of the valve to lift or unseat the valve for starting fuel injection, and a high rate spring acts opposite the fuel pressure to seat the valve for stopping fuel injection.
- the high rate springs are a costly item and are subject to breakage which of course requires re ⁇ placement. Also, the forces created by such springs cause tip damage to the needle valves commonly used in such nozzles due to the high impact loads occurring when the valves seat.
- a springless fuel injection nozzle including a housing having a fuel cavity including upper and lower cavity portions separated by a valve guide.
- a conduit supplies high pressure fuel only to the -lower cavity portion.
- a valve reciprocates to meter fuel between the upper and lower cavity portions. The valve reciprocation results from pressure differentials acting on the valve without the aid of any resilient member acting on the valve.
- / ⁇ r- WIPO Figure 1 is a view illustrating a fuel system including an embodiment of the present invention
- Figure 2 is a view illustrating an enlarged partial section of the nozzle valve guide and guide clearance of this invention.
- Figure 3 is another view illustrating an enlarged partial section of the nozzle valve guide and guide clearance.
- a fluid fuel system is generally designated 10, and includes a reservoir 12.
- a well known fuel transfer pump 13 is connected via a conduit 14 for pumping fuel from reservoir 12 at a system pressure of about 30-35 psi.
- the fuel is then passed through a known filter 16 in conduit 18 to a conventional high pressure fuel injection pump 20 which supplies the fuel at pressures ranging from about 2000 psi to about 15,000 psi and then to a fuel injection nozzle 22 via a conduit 24.
- a known reverse flow check valve 26 is between high pressure pump 20 and nozzle 22 to check against pressure waves which may oscillate between pump 20 and nozzle 22 as a result of rapidly created high pressure surges of fuel being pumped through nozzle 22 into an associated engine cylinder 23 at a rate of several times per second.
- Nozzle 22 comprises a housing 28 having a fuel passage 30 for communicating fuel between system 10 and cavity 32 formed in housing 28.
- Housing 28 is preferably formed of high carbon steel and defines an upper cavity portion 32a and a lower cavity portion 32b and further defines a reduced diameter cylindrical guide 34 separating the upper and lower cavity portions 32a,32b, respectively.
- passage 30 is connected so that fuel communication with cavity 32 occurs only at lower cavity portion 32b. Once fuel communicates with lower cavity portion 32b, fuel fills upper cavity portion 32a only through guide 34. Thus, 5 upper cavity portion 32a comprises a trapped volume.
- Lower cavity portion 32b includes conventional fuel injection orifices 48.
- a valve member 36 is preferably formed of a high carbon steel and is reciprocably disposed in cavity
- Valve 36 includes a lower valve portion 36b extending into lower cavity portion 32a and having a tip 38 engaged with a valve seat 40 at a seating contact diameter 39 of at least from about
- valve portion 36c has a first diameter portion 36d adjacent upper cavity 32a and has a second diameter portion 36e adjacent lower cavity
- First diameter portion 36d has a diameter D, of at
- Second diameter portion 36e is frusto-conical and extends to a length L 2 of at least about .0305cm from the constant dianeter portioi ⁇ tapering to a reduced
- valve portion 36c permits valve 36 to reciprocate in cavity 32 to meter fuel between upper cavity 32a and lower cavity 32b due only to differential 5 fuel pressure acting on valve 36 so that nozzle 22 functions free of any resilient member acting on valve 36.
- variable diameter of intermediate valve portion 36c permits clearance between valve portion 36c 10 and guide 34 to vary from at least about .0003cm between constant diameter portion 36d and guide 34 to at least about .0023cm between frusto-conical portion 36e and guide 34.
- valve 36 During idle, when peak system pressure is about 3000 to 5000 psi, valve 36 lifts about .0102cm H/-7 rm tf -' J - i -'-SO inehaO during injection which maintains constant diameter •s 30 portion 36d within guide 34, see Figure 2.
- the substantially tight guide clearance of at least about I ⁇ /& r f ⁇ - ⁇ . e ⁇ - ' %O O003cm ⁇ *__ch j .-_ restricts fuel communication between upper cavity portion 32a and lower cavity portion 32b.
- valve 36 lifts about .0305cm -inches- during injection which lifts constant diameter portion 36d entirely out of guide 34 and into upper cavity portion 32a thus lifting frusto-conical portion 36e to a posi ⁇ tion, as illustrated in Figure 3, where clearance between guide 34 and frusto-conical portion 36e in ⁇ creases substantially to at least about ,0023cm.
- a sufficient amount of higher pressure fuel in lower cavity portion 32b is permitted to bleed into the trapped volume of upper cavity portion 32a.
- system 10 goes on bypass and injection is stopped. When injection is stopped, the substantially steady peak trapped volume pressure of about 1,000 psi is sufficient to urge tip 38 against seat 40 free of any resilient member such as springs used in some conventional fuel injection nozzle.
- the springless nozzle 22 is advantageous for many reasons.
- the 1,000 psi peak trapped volume pressure is a relatively light load on valve 36 and the absence of a spring limits the possibility of the valve bouncing at tip 38 and seat 40.
- Such bouncing is common where undamped springs resonate when used to seat fuel injec ⁇ tion nozzle valves.
- Such bouncing is a major cause of tip wear, tip breakage and increased emissions.
- Elimi- nation of a spring also precludes spring breakage and reduces cost.
- Another observable advantage has been that timing of injection is retarded with load at any speed due to the fact that trapped volume residual pressure increases with load.
- the foregoing has described a fuel injection nozzle including a housing and a valve reciprocating in the housing to meter fuel between upper and lower cavity portions. The valve reciprocation results from pressure differentials acting on the valve without the aid of any resilient member acting on the valve.
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- Engineering & Computer Science (AREA)
- Chemical & Material Sciences (AREA)
- Combustion & Propulsion (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Physics & Mathematics (AREA)
- Fluid Mechanics (AREA)
- Fuel-Injection Apparatus (AREA)
Abstract
Des ressorts non amortis de haute pression utilisés dans les soupapes des tuyères d'injection de combustible conventionnelles endommagent la pointe et le siège de la soupape. De même, de tels ressorts non amortis résonnent et admettent du combustible superflus dans les cylindres du moteur, ce qui se traduit par un gaspillage de carburant et de fortes émissions. La cassure et les coûts des ressorts sont également des problèmes dans de telles soupapes de tuyères. Une soupape de tuyère sans ressort (36) fonctionne d'après une utilisation dosée de la pression différentielle du carburant qui alimente l'enceinte (28) de la tuyère et permet d'éliminer les problèmes associés avec les soupapes de tuyères conventionnelles.Unpressurized high pressure springs used in the valves of conventional fuel injection nozzles damage the tip and seat of the valve. Likewise, such non-damped springs resonate and admit excess fuel into the engine cylinders, which results in wasted fuel and high emissions. Breakage and spring costs are also problems in such nozzle valves. A springless nozzle valve (36) operates by metering the differential pressure of the fuel that feeds the nozzle enclosure (28) and eliminates the problems associated with conventional nozzle valves.
Description
Description
Springless Fuel Injection Nozzle
Technical Field
This invention relates generally to fluid sprinkling, spraying and diffusing and more particularly to fluid pressure responsive discharge modifiers such as fuel injectors.
Background Art
In general, fuel injection nozzle valves operate in response to high pressure fuel creating forces acting on differential areas of the valve causing rapid reciprocation of the valve. The rapid reciproca¬ tion causes intermittent seating and unseating of a tip of the valve with a valve seat which permits the fuel to be injected into engine cylinders.
In one type of fuel injector, fuel at one pressure acts on one side of the valve to lift or unseat the valve for starting fuel injection, and fuel at another pressure acts opposite the one pressure to seat the valve for stopping fuel injection.
Another type of fuel injector utilizes fuel pressure acting on one side of the valve to lift or unseat the valve for starting fuel injection, and a high rate spring acts opposite the fuel pressure to seat the valve for stopping fuel injection.
The high rate springs are a costly item and are subject to breakage which of course requires re¬ placement. Also, the forces created by such springs cause tip damage to the needle valves commonly used in such nozzles due to the high impact loads occurring when the valves seat.
Further, high impact loads caused by spring
forces often create a resonance in the undamped spring which causes the needle valve to bounce. Such bounce permits undesirable leakage of fuel into an engine cylinder after injection. As a result, the leaked fuel is admitted to the cylinder out of cycle and thus is not fully consumed. This results in increased emissions and poor fuel economy.
The foregoing illustrates limitations of the known prior art. Thus, it is apparent that it would be advantageous to provide an alternative directed to over¬ coming one or more of the limitations as set forth above.
Disclosure of Invention
In one aspect of the present invention, this is accomplished by providing a springless fuel injection nozzle including a housing having a fuel cavity including upper and lower cavity portions separated by a valve guide. A conduit supplies high pressure fuel only to the -lower cavity portion. A valve reciprocates to meter fuel between the upper and lower cavity portions. The valve reciprocation results from pressure differentials acting on the valve without the aid of any resilient member acting on the valve. The foregoing and other aspects will become apparent from the following detailed description of the invention when considered in conjunction with the ac¬ companying drawings. It is to be expressly understood, however, that the drawings are not intended as a defi- nition of the invention but are for the purpose of illustration only.
Brief Description of the Drawings In the drawings:
OMPI
/Λr- WIPO
Figure 1 is a view illustrating a fuel system including an embodiment of the present invention;
Figure 2 is a view illustrating an enlarged partial section of the nozzle valve guide and guide clearance of this invention; and
Figure 3 is another view illustrating an enlarged partial section of the nozzle valve guide and guide clearance.
Best Ilode for Carrying Out the Invention In Figure 1, a fluid fuel system is generally designated 10, and includes a reservoir 12. A well known fuel transfer pump 13 is connected via a conduit 14 for pumping fuel from reservoir 12 at a system pressure of about 30-35 psi. The fuel is then passed through a known filter 16 in conduit 18 to a conventional high pressure fuel injection pump 20 which supplies the fuel at pressures ranging from about 2000 psi to about 15,000 psi and then to a fuel injection nozzle 22 via a conduit 24. It is preferred that a known reverse flow check valve 26 is between high pressure pump 20 and nozzle 22 to check against pressure waves which may oscillate between pump 20 and nozzle 22 as a result of rapidly created high pressure surges of fuel being pumped through nozzle 22 into an associated engine cylinder 23 at a rate of several times per second.
Nozzle 22 comprises a housing 28 having a fuel passage 30 for communicating fuel between system 10 and cavity 32 formed in housing 28.
Housing 28 is preferably formed of high carbon steel and defines an upper cavity portion 32a and a lower cavity portion 32b and further defines a reduced diameter cylindrical guide 34 separating the upper and lower cavity portions 32a,32b, respectively.
In the preferred embodiment, passage 30 is
connected so that fuel communication with cavity 32 occurs only at lower cavity portion 32b. Once fuel communicates with lower cavity portion 32b, fuel fills upper cavity portion 32a only through guide 34. Thus, 5 upper cavity portion 32a comprises a trapped volume. Lower cavity portion 32b includes conventional fuel injection orifices 48.
It has been found that the preferred trapped volume of upper cavity portion 32a is at least from
10 about 2cc to about 12cc; the volume of lower cavity portion is at least about 5cc to about 16cc and the diameter of guide 34 is about 3.9883cm.
A valve member 36 is preferably formed of a high carbon steel and is reciprocably disposed in cavity
15 32. An extended upper valve portion 36a extends into upper cavity portion 32a. Valve 36 includes a lower valve portion 36b extending into lower cavity portion 32a and having a tip 38 engaged with a valve seat 40 at a seating contact diameter 39 of at least from about
20 .142cm to about .279 cm so as to block fuel from com¬ municating between lower cavity portion 32b and orifices 48. Upper and lower valve portions 36a,36b, respectively, are separated by an intermediate enlarged diameter valve portion 36c which reciprocates within guide 34 and has a
25 variable diameter so as to form a variable clearance with guide 34.
More specifically, valve portion 36c has a first diameter portion 36d adjacent upper cavity 32a and has a second diameter portion 36e adjacent lower cavity
30 32b. First diameter portion 36d has a diameter D, of at
0.3??? - 1
Wtf*»i7 l-zf-l ø least about -3-r-9-8-&-θcιrt along a length L. of at least about .0102cm. Second diameter portion 36e is frusto-conical and extends to a length L2 of at least about .0305cm from the constant dianeter portioi^ tapering to a reduced
W<& /-i«-Jt85 diameter D2 of at
Figs. 2 and 3).
OMPI
Surprisingly and unexpectedly, the unique structure of valve portion 36c permits valve 36 to reciprocate in cavity 32 to meter fuel between upper cavity 32a and lower cavity 32b due only to differential 5 fuel pressure acting on valve 36 so that nozzle 22 functions free of any resilient member acting on valve 36.
The variable diameter of intermediate valve portion 36c permits clearance between valve portion 36c 10 and guide 34 to vary from at least about .0003cm between constant diameter portion 36d and guide 34 to at least about .0023cm between frusto-conical portion 36e and guide 34.
Industrial Applicability 15 With the parts assembled as set forth above peak pressure in system 10 reaches about 15,000 psi to act on constant diameter 36d less seating contact diameter 39 for lifting valve 36 and permit fuel to be injected through orifices 48. System 10 pressure drops 20 to about 30-35 psi as the system goes on bypass and valve 36 seats for cutting off injection in the well- known manner. Pressure in upper cavity portion 32a acts on constant diameter portion 36d to seat the valve 36. According to this invention it has been found 25 that peak pressure in upper cavity portion 32a maintains substantially steady at about 1,000 psi during both idle and full loads. During idle, when peak system pressure is about 3000 to 5000 psi, valve 36 lifts about .0102cm H/-7rmtf -'J-i-'-SO inehaO during injection which maintains constant diameter •s 30 portion 36d within guide 34, see Figure 2. Thus, the substantially tight guide clearance of at least about Iλ/&r f }-\.eϊ-'%O O003cm ■*__chj.-_ restricts fuel communication between upper cavity portion 32a and lower cavity portion 32b. During full loads, when peak system pressure is about ,* > , ι*t . 35 15,000 psi, valve 36 lifts about .0305cm -inches- during
injection which lifts constant diameter portion 36d entirely out of guide 34 and into upper cavity portion 32a thus lifting frusto-conical portion 36e to a posi¬ tion, as illustrated in Figure 3, where clearance between guide 34 and frusto-conical portion 36e in¬ creases substantially to at least about ,0023cm. As a result, a sufficient amount of higher pressure fuel in lower cavity portion 32b is permitted to bleed into the trapped volume of upper cavity portion 32a. However, before the bleed pressure is permitted to appreciably affect peak trapped volume pressure, system 10 goes on bypass and injection is stopped. When injection is stopped, the substantially steady peak trapped volume pressure of about 1,000 psi is sufficient to urge tip 38 against seat 40 free of any resilient member such as springs used in some conventional fuel injection nozzle.
The springless nozzle 22 is advantageous for many reasons. The 1,000 psi peak trapped volume pressure is a relatively light load on valve 36 and the absence of a spring limits the possibility of the valve bouncing at tip 38 and seat 40. Such bouncing is common where undamped springs resonate when used to seat fuel injec¬ tion nozzle valves. Such bouncing is a major cause of tip wear, tip breakage and increased emissions. Elimi- nation of a spring also precludes spring breakage and reduces cost. Another observable advantage has been that timing of injection is retarded with load at any speed due to the fact that trapped volume residual pressure increases with load. The foregoing has described a fuel injection nozzle including a housing and a valve reciprocating in the housing to meter fuel between upper and lower cavity portions. The valve reciprocation results from pressure differentials acting on the valve without the aid of any resilient member acting on the valve.
OMPI
It is anticipated that aspects of the present invention, other than those specifically defined in the appended claims, can be obtained from the foregoing de¬ scription and the drawings so that the above-stated parameters may be varied to meet criteria for various fuel systems.
O
Claims
1. In a fuel injection nozzle (22) of the type including a housing (28) having a fluid cavity (32) having an upper cavity portion (32a) fluidly connected to a lower cavity portion (32b) , said housing (28) having a valve guide (34) formed between said upper and lower cavity portions (32a,32b) , said housing (28) having means (30) for supplying pressurized fluid to said cavity portions (32a,32b) of said cavity (32) , said means (30) connected to said cavity (32) only at said lower cavity portion (32b) , said housing (28) having fluid outlet orifices (48) only at said lower cavity portion (32b) , said housing (28) having a reciprocable valve (36) , said valve having an upper valve portion (36a) extending_into said upper cavity portion (32a), a lower valve portion (36b) extending into said lower cavity portion (32b) and an intermediate valve portion (36c) within said guide (34) , an improvement comprising: said intermediate valve portion (36c) forming a variable clearance with said guide (34) ; and said nozzle (22) being free of any resilient member acting on said valve (36) .
2. The nozzle of claim 1 wherein said inter¬ mediate valve portion (36c) includes a variable diameter.
3. The nozzle of claim 1 wherein said inter- mediate valve portion (36c) includes a first diameter portion (36d) adjacent said upper cavity portion (32a) and includes a second diameter portion (36e) adjacent said lower cavity portion (32b) , said second diameter portion (36e) being less than said first diameter portion (36d) .
_OMPI
4. The nozzle of claim 1 wherein said inter¬ mediate valve portion (36c) includes a constant diameter v portion (36d) adjacent said upper cavity portion (32a) and includes a frusto-conical portion (36e) extending from said constant diameter portion and tapering to a reduced diameter less than said constant diameter por¬ tion (36d) .
5. A fuel injection nozzle (22) comprising: a housing (28) , said housing having a fluid cavity (32) including an upper cavity portion (32a) fluidly connected to a lower cavity portion (32b) , said housing having a valve guide (34) formed between said upper and lower cavity portions (32a,32b) , said housing having means (30) for supplying pressurized fluid to said portions (32a,32b) of said cavity (32), said means (30) connected to said cavity (32) only at said lower cavity portion (32b) , and said housing having fluid outlet orifices (48) only at said lower cavity portion (32b) ; means for metering fluid between said upper cavity portion (32a) and said lower cavity portion (32b) , said means being a reciprocable valve (36) having an upper valve portion (36a) extending into said upper cavity portion (32a) , a lower valve portion (36b) ex- tending into said lower cavity portion (32b) and an intermediate valve portion (36c) within said guide (34) , said intermediate valve portion (36c) forming a variable clearance with said guide (34) ; and said nozzle (22) being free of any resilient member acting on said valve (36) .
OMPI A, WIPO
6. A fuel system (10) comprising: a fuel reservoir (12) ; a fuel transfer pump (13) connected for pump¬ ing fuel from said reservoir (12) ; a high pressure fuel pump (20) connected for pumping and pressurizing said fuel from said fuel transfer pump (13) ; a fuel injection nozzle (22) comprising a housing (28) , said housing having a fluid cavity (32) including an upper cavity portion (32a) fluidly con¬ nected to a lower cavity portion (32b) , said housing having a valve guide (34) formed between said upper and lower cavity portions (32a,32b) , said housing having means (30) for supplying pressurized fluid to said portions (32a,32b) of said cavity (32) , said means (30) connected to said cavity (32) only at said lower cavity portion (32b) , and said housing having fluid outlet orifices (48) only at said lower cavity portion (32b) ; and means for metering fluid between said upper cavity portion (32a) and said lower cavity portion (32b) , said means being a valve (36) having an upper valve portion (36a) extending into said upper cavity portion (32a) , a lower valve portion (36b) extending into said lower cavity portion (32b) and an intermediate valve portion (36c) within said guide (34) , said inter¬ mediate valve portion (36c) forming a variable clearance with said guide (34) ; and said nozzle (22) being free of any resilient member acting on said valve (36) .
7. A fuel injection nozzle (22) comprising: a housing (28) , said housing having a fluid cavity (32) including an upper, cavity portion (32a) fluidly connected to a lower cavity portion (32b) , said housing having a valve guide (34) formed between said upper and lower cavity portions (32a,32b) , said housing having means (30) for supplying pressurized fluid to said portions (32a,32b) of said cavity (32) , said means (30) connected to said cavity (32) only at said lower cavity portion (32b) , and said housing having fluid outlet orifices (48) only at said lower cavity portion (32b) ; and means for moving in said cavity (32) for intermittently seating with said housing (28) for start- ing and stopping fuel injection through said orifices
(48) , said means being a reciprocable valve (36) having an upper valve portion (36a) extending into said upper cavity portion (32a) , a lower valve portion (36b) ex¬ tending into said lower cavity portion (32b) and an intermediate valve portion (36c) within said guide (34) for metering said fluid and varying pressure between said upper cavity portion (32a) and said lower cavity portion (32b) in response to said intermediate valve portion (36c) forming a variable clearance with said guide (34) , said nozzle (22) being free of any resilient member acting on said valve (36) .
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| PCT/US1980/000122 WO1983000639A1 (en) | 1980-02-04 | 1980-02-04 | Springless fuel injection nozzle |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| PCT/US1980/000122 WO1983000639A1 (en) | 1980-02-04 | 1980-02-04 | Springless fuel injection nozzle |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| WO1983000639A1 true WO1983000639A1 (en) | 1983-03-03 |
Family
ID=22154193
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| PCT/US1980/000122 Ceased WO1983000639A1 (en) | 1980-02-04 | 1980-02-04 | Springless fuel injection nozzle |
Country Status (1)
| Country | Link |
|---|---|
| WO (1) | WO1983000639A1 (en) |
Citations (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US1840256A (en) * | 1929-02-07 | 1932-01-05 | Fried Krupp Germaniawerft Ag | Fuel feeding valve |
| US3368761A (en) * | 1965-10-15 | 1968-02-13 | Mack Trucks | Variable flow rate fuel injection nozzle |
| US3511442A (en) * | 1968-02-29 | 1970-05-12 | Ambac Ind | Sumpless fuel injection nozzle |
| US3640466A (en) * | 1968-11-05 | 1972-02-08 | Sulzer Ag | Fuel injection system for an internal combustion piston engine |
| US3791591A (en) * | 1972-06-08 | 1974-02-12 | H Hedges | Fuel injection nozzle assembly |
-
1980
- 1980-02-04 WO PCT/US1980/000122 patent/WO1983000639A1/en not_active Ceased
Patent Citations (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US1840256A (en) * | 1929-02-07 | 1932-01-05 | Fried Krupp Germaniawerft Ag | Fuel feeding valve |
| US3368761A (en) * | 1965-10-15 | 1968-02-13 | Mack Trucks | Variable flow rate fuel injection nozzle |
| US3511442A (en) * | 1968-02-29 | 1970-05-12 | Ambac Ind | Sumpless fuel injection nozzle |
| US3640466A (en) * | 1968-11-05 | 1972-02-08 | Sulzer Ag | Fuel injection system for an internal combustion piston engine |
| US3791591A (en) * | 1972-06-08 | 1974-02-12 | H Hedges | Fuel injection nozzle assembly |
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Designated state(s): US |