US2096711A - Fuel pump for injectors - Google Patents

Fuel pump for injectors Download PDF

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Publication number
US2096711A
US2096711A US755157A US75515734A US2096711A US 2096711 A US2096711 A US 2096711A US 755157 A US755157 A US 755157A US 75515734 A US75515734 A US 75515734A US 2096711 A US2096711 A US 2096711A
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US
United States
Prior art keywords
pump
pressure
reservoir
plunger
port
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Expired - Lifetime
Application number
US755157A
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English (en)
Inventor
Fielden Arthur
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.)
Motors Liquidation Co
Original Assignee
Motors Liquidation Co
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Motors Liquidation Co filed Critical Motors Liquidation Co
Priority to US755157A priority Critical patent/US2096711A/en
Priority to GB15196/36A priority patent/GB461791A/en
Priority to DEG5013D priority patent/DE908681C/de
Priority to DK53214D priority patent/DK53214C/da
Application granted granted Critical
Publication of US2096711A publication Critical patent/US2096711A/en
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

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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
    • F02M57/00—Fuel-injectors combined or associated with other devices
    • F02M57/02—Injectors structurally combined with fuel-injection pumps
    • 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
    • F02M59/00—Pumps specially adapted for fuel-injection and not provided for in groups F02M39/00 -F02M57/00, e.g. rotary cylinder-block type of pumps
    • 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
    • F02M2700/00—Supplying, feeding or preparing air, fuel, fuel air mixtures or auxiliary fluids for a combustion engine; Use of exhaust gas; Compressors for piston engines
    • F02M2700/07—Nozzles and injectors with controllable fuel supply
    • F02M2700/078—Injectors combined with fuel injection pump
    • 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
    • F02M2700/00—Supplying, feeding or preparing air, fuel, fuel air mixtures or auxiliary fluids for a combustion engine; Use of exhaust gas; Compressors for piston engines
    • F02M2700/13—Special devices for making an explosive mixture; Fuel pumps
    • F02M2700/1317—Fuel pumpo for internal combustion engines

Definitions

  • This invention relates to pumps and especially toplunger pumps 'for intermittent delivery of fluid through a pressure loaded delivery valve during the middle portion only of the discharge stroke of the plunger, the beginning and ending of each discharge stroke being made ineffective for delivery through the loaded delivery valve by the opening of suitable bypass or relief ports providing an alternative path for the flow of fluid from the pump pressure space during these portions of each discharge stroke.
  • It relates particularly to injection pumps for the supply of fuel to an internal combustion enr gine in which the pressure loaded delivery valve may constitute an injection valve.
  • the fuel rejected before delivery through the loaded delivery valve is rejected from the uppermost part of the pump pressure space, thereby eliminating along with the rejected fuel any air or gas bubbles which will rise to the uppermost part 'of the pressure space, before delivery takes place, the pump plunger moving downwardly on its delivery stroke for the injection of fuel downwardly into an engine cylinder.
  • the pump plunger is 45 provided'with helical control edges whereby the time and quantity of fuel delivered may be varied'in known manner by a turning adjustment of the plunger.
  • the present invention relates to improvements 50 in the unit fuel pump and injector shown in Patent No. 1,981,913 and to a modification enabling the functional results of the structure shown in Patent No. 1,981,913 to be obtained in those cases where the assembly is inverted 55 for the injection of fuel upwardly into an engine cylinder, the plunger moving upwardly on its delivery stroke.
  • One object of the invention is a fuel pump of the kind described in which the amount of fuel bypassed before delivery through the loaded de- 5 livery valve is constant, or alternatively, directly proportional to the amount delivered through the loaded delivery valve.
  • Another object of the invention is a fuel pump of the kind described having positive valve venting means open through a certain period of the cycle of operation of the pumpto relieve the reservoir of any excess air or gas bubbles.
  • Another object of the invention is to provide for a through flow scavenging of the reservoir at the fuelsupply pressure.
  • a further object of the invention is to provide for air venting of the reservoir at a pressure higher than the fuel supply pressure.
  • a still further object of the invention is a modification of the structure of the unit fuel pump and injector of U. S. Patent No. 1,981,913 adapted for operation in a relatively inverted position for upward injection of fuel and having the foregoing objects of the invention applied thereto.
  • control edge on the pump plunger which controls the closure with the latter arrangement the degree of preliminary bypassing may be proportional to the quantity delivered.
  • venting of the reservoir both for the elimination of air from the system and for any desired amount of "through flow scavenging is effected tive valve means for venting the reservoir for the elimination of undesired air in the system enables this elimination to be positively effected with a minimum of through flow of fuel, thus reducing the quantity of fuel to be recirculated through the low pressure supply system and hence avoiding any infiltration of additional air in the fuel so recirculated.
  • the velocity of air or gas at a certain pressure through an orifice being several times greater than the velocity of a liquid at the same pressure through the same orifice, the bore of the vent and the time which it remains open can be made such that all undesired air or gas can be eliminated from the reservoir, while only a comparatively small amount of liquid fuel can escape through the vent in the same circumstances.
  • the reservoir may be vented either before the beginning of the discharge stroke at the supply pump pressure, or after the end of the discharge stroke at a pressure higher than the supply pump pressure, in a manner later to be described.
  • Figure 1 shows in part sectional elevation
  • Figure la is an enlarged view of a part of Figure 1 showing the injection nozzle.
  • Figure 2 is a perspective view of a suitabl check valve for the bypass port to prevent the influx of fuel'into the cylinder barrel through this port.
  • Figure 3 is a section on line 3--3 of Figure 1 showing the means for angular turning adjustment of the plunger, to vary the time and quantity delivered through the loadedv delivery valve.
  • Figure 4 is a section on line 4-4 of Figure 1.
  • Figure 5 is a section on line 55 of Figure 1, showing the means of locating the cylinder bushing in the pump housing and the ducts for draining excess air and fuel leakage away from the injector.
  • Figure 6 is an enlarged perspective view of the end of the pump plunger showing a control edge for the closure of the inlet port providing for a constant interval between closure of the inletport and closure of the preliminary bypass port as shown in Figures 7, 9 and 10.
  • Figure 7 shows a fuel pump similar to Figure 1, but having a plunger controlled port 'for the air venting and pressure relief of the reservoir, and a combined check valve and safety valve in the supply line.
  • Figure 8 is-an enlarged section on line 8-8 of Fig. '7.
  • Figure 9 shows a fuel pump for use with injectors discharging downwardly, having "a plunger controlled port for the air venting and pressure relief of the-reservoir, and a combined check" valve and safety valve in the supply line.
  • Figure 10 shows a modification of Figure 9 with .means for opening the port for the air venting and pressure relief of the reservoir at the end of the discharge stroke of the pump plunger.
  • Figure 11 shows a similar modification of Figure 7.
  • Figure 12 is an enlarged view of a part of Figbushirig in the housing I.
  • An annular groove or space 2 divides the circumferential surface of the plunger into two parts.
  • the annular groove isbounded by a helical edge 3 and a helical edge 4.
  • the plunger works in a cylinder 8 which is a Between the bushing and the housing is an annular chamber 8 formed by an enlarged bore of the housing. Two ports 9 and Illthrough the wall of the bushing 6 connect the annular chamber 8 with the bore of the bushing.
  • a duct drilled through the housing into the end of the annular chamber 8 serves for the supply of fuel to this annular chamber from any suitable low pressure source.
  • the housing is counterbored to form a pocket l3 for a pinion
  • the plungerl has a' hexagonal spline portion l! in the pinion I4 so that it may be turned thereby, but is capable of longitudinal reciprocating motion therein.
  • the pinion l4 may be angularly turned for adjustment of the beginning and end of injection by a rack I8 which can slide back and forth in a horizontal groove IS in the housing, opening out into the pocket IS.
  • the rack is retained in the groove by a plate l9.
  • the housing I is counterbored to provide a
  • the outer end of the plunger is provided with a head 22 and a seating collar 23 for the spring 2
  • the other end of the spring is provided with a seating collar 24 bearing against the end of the pocket 26.
  • the outer end of the plunger with its spring is enclosed by a cover 25, which reciprocates in the pocket 20 under the influence of any suitable driving means.
  • the plunger is actuated on its discharge stroke, through the medium of a rocking lever 26 with rollers 26 and 26", by a cam 21, the spring 2
  • the end of the housing 1 is internally threaded for the injection valve parts, consisting of a nozzle piece 28, a valve seat piece 29, and, a distance piece 30 constituting a spring .housing, .all within a bored out threaded cap piece 3
  • the nozzle piece 28 has a conical seating in the cap piece 3
  • a duct or ducts 34 through the piece 30 lead the fuel from the pump pressure space to a duct or ducts 36, leading to a chamber 31 in the piece 29.
  • a chamber 31 In this chamber 31 is a seating for an 111-- collar 44 on a stem piece 45 for the valve which I predetermined amount.
  • the strength of the spring 43 and the loading it provides for the injection valve 38 which is the loaded delivery valve of the pump determines the minimum injection pressure.
  • the port It! is provided with a check valve of any suitable type.
  • a check valve of any suitable type.
  • it consists of a fiat spring 48 curved to fit tightly in a shallow annular groove 49 around the bushing 6, with one end over the port I and the other end locating and holding the spring in position by a projection or dimple 50 formed thereon, and sprung into a corresponding depression in the bushing.
  • the bushing 6 is located in the housing I with its ports 9 and I0 at'a normal definite angular relationship to the housing by a pin 52 (see Figure 5).
  • the complete assembly constitutes a unit fuel pump and injection nozzle which may be mounted in a suitable bore through the cylinder head of an internal combustion engine.
  • of the combined fuel pump and injection nozzle has a conical seating in a bore through a'cylinder head 55 in which it is held by-the studs 56.
  • A-suitable clearance between this bore and the housing! provides an annular space 51 into which all leakage and ventage from the pump may collect.
  • the clearance space I5 is connected to the annular space 51 by a port46' in Figures 1, 5, '7 and 11 and by a port 46 in Figures 9 and 10.
  • the flanged end 60 of the cylinder barrel 6 which is clamped onto the shoulder 32 of the housing 1 has its periphery grooved by channels 6
  • the air chamber 33 acts as a. pressure accumulator, reducing the pressure variations on the inlet side of the pump as a result of the opening and closing of the ports 9 and Il Excess air in the airchamber 33 escapes at any time through the port 62, by virtue of the clearances provided.
  • the edge I of the plunger, which controls the closure of the inlet port 9 is cut square with its axis, and therefore if thetime of closing of the bypass port ID by the helical edge 4 is advanced by a turning adjustment of the plunger, the quantity bypassed before the beginning of injection will be lessened'while the quantity injected is increased, and vice versa.
  • this bypassed volume should be at least constant or directly proportional to the amdunt of fuel delivered through the injector and not lessened when the quantity injected is increased.
  • the edge I of the plurfger-- which is the control edge for the closure of the inlet port 9- - is helical and of the same pitch as the helical edge 4 which controls the closure of the bypass port l8; 1. e. it has the same lead or advance as the helical edge 4, and therefore if in the plunger stroke the time of closing of the bypass port is advanced or retarded by a turning adjustment of the plunger, the time of closing of the inlet port will be advanced or retarded to a like extent, and the distance moved through by the'pump plunger between closure of the inlet port and closure of the bypass port will be constant; hence the volume bypassed through the bypass port I0 before the beginning of in? ction will be invariable.
  • the volume bypassed through the bypass port M before the beginning of injection may be made directly proportional to the amount of fuel delivered through the injector.
  • Airor vapor separating out from the fuel in excess of that required to fill the cushion chamber I2 is displaced from the reservoir 8 through a port 63 by thexpre'ssure of the fuel therein.
  • this venting of the reservoir takes place along with a through flow" of the fuel during the dwell period between suction and discharge strokes of the pump, there being an annular groove 64 around the plunger which, during this period, puts the port 68 in communication with a drilled hole 65 in the bushing 6, leading to the clearance space l6 and thence throughthe port 46 into the annular space 51.
  • valved venting of the reservoir, 8 are preferably provided with a combined nonlar passage through which, when the member 14 is oil its seating, fluid may flow through radial grooves such as in the end of the pipeunion, into the supply pipe 18-.
  • yieldingiy urged onto its seating 82 therein at that end thereof remote from the seating 1rby-aspringr83l lhesprings 83 and 11 are respectively such that fluid can flow through the ball check valve 8
  • this intermediate pressure higher than the supply pressure, will be effective to recharge the pumping space on the suction stroke until the pressure in the reservoir 8 falls to supply pressure, when the non-return ball check valve 8
  • a more rapid filling of the pump pressure space is thus obtained, which is advantageous in a pump working at high speed.
  • the intermediate pressure will be relieved by the opening of the vent port 68 and the vent stroke, whereby the reservoir is vented at a pressure higher than the supply pressure.
  • a fluid pump comprising a cylinder, 9.
  • a plunger cooperative therewith as a pump for the pressure discharge of a predetermined quantity of fluid through a delivery outlet, coacting ports and control edges therefor on the cylinder and plunger, respectively, including an inlet port and a bypass port whereby fluid is bypassed out from the cylinder after the closing of the inlet port and before the pressure discharge through the delivery outlet, the control edges for closing the inlet and bypass ports being inclined and so arranged that Y upon a relative adjustment of the cylinder and plunger the inlet port is closed earlier as the bypass port is closed earlier, the inclination of the control edge for closing the inlet port being not less than the inclination of the control edge for closing the bypass port, whereby the quantity bypassed before discharge through the delivery outlet is not lessened as the bypass port is closed earlier.
  • a plunger cooperative therewith as a pump for the pressure discharge of a predetermined quantity of fluid through a delivery outlet, coacting ports and conrespectively, including an inlet port and a bypass port whereby fluid is bypassed out from the cylinder after the closing of the inlet port and before the pressure'discharge through .
  • the dethe quantity bypassed before discharge throughthe delivery outlet remains constant irrespective of the time of closing of the bypass port.
  • a plunger cooperative therewith as a pump for the pressure discharge of a predetermined quantity of fluid through a delivery outlet, coacting ports and control edges therefor on the cylinder and plunger, respectively, including an inlet port and a bypass port whereby fluid is bypassed out from the the inclination of the control edge for closing the bypass port, whereby the quantity bypassed before discharge through the delivery outlet is increased as the bypass port is closed earlier.
  • a fluid pump having a cylinder, at plunger cooperative therewith as a pump: for the pressure discharge of a predetermined quantity of fluid through a delivery outlet, coacting ports and control edges therefor on the cylinder and plunger respectively including an inlet port and a bypass port whereby fluid is bypassed out from the cylinder after the closing of the inlet port and before the pressure discharge through the delivery outlet, the control edge for closing the bypass port being inclined so that the time of closing of the bypass port is variable by a relative adjustment of the cylinder and"plunger, the quantity delivered being increased as the bypass port is closed earlier, the control edge for closing the inlet port being inclined and so arranged that the inlet port is closed earlier as the bypass port isclosed earlier, said lastnamed control edge having an inclination not less than the inclination of the controledge for closing the bypass port whereby the quantity bypassed before discharge through the delivery outlet is not lessened as the quantity delivered is increased.
  • control edge for closing the inlet port has an inclination equal to that of the control edge for closing the bypass port, whereby the quantity bypassed before discharge through the trol edges therefor on the cylinder and plunger,
  • control edges for closing the inlet and bypass ports being inclined and so arranged that upon a relative adjustment of the cylinder and plunger the inlet port is closed earlier as thebypass port is closed earlier, the inclination of the control edge for closing the inlet port being greater than I delivery outlet-remains constant as the quantity delivered is increased.
  • a fluid pump comprising a cylinder and a plunger cooperative therewith as a pump, a delivery outlet for the pressure discharge of a part only of the volume of fluid displaced by the pump, a. reservoir for fluid under pressure forming part of the supply line to the pump from a low'pressure source of supply, inlet and bypass valve means between the pump pressure space and the reservoir, and means for venting the reservoir including suitable passageways independent of the pump pressure space,- having valve means constituted by a port and a coacting control edge therefor on the cylinder and plunger respectively.
  • a fluid pump according to claim 8 in which fluid including any gas bubbles is bypassed from the'pump into the reservoir after the closing o'fithe inlet valve and before the beginning of discharge through the delivery outlet.
  • a fluid pump according to claim 8 having a non-return valve in the supply line to the reservoir.
  • a fluid pump according to claim 8 having a non-return and safety valve in the supply line to the reservoir.
  • a reservoir for fluid under pressure forming part of the supply line tothe pump from a low pressure source of supply, inlet and bypass-.
  • valve means between the pump pressure space and the reservoir, said inlet and bypass valve means being constituted by ports and coacting control edge therefor on the cylinder and plunger respectively, and valve venting means for the reservoir constituted by an additional port and coacting control edge therefor on the cylinder and plunger respectively.
  • valve venting means opens from the reservoir at a point higherthan the inlet and bypass valves open thereinto.
  • bypass port both adapted to provide a path of flow between the pump pressure space and the reservoir, the bypass port opening from thatpart of the pressure space which is uppermost at a pointhigher than the inlet port and the said delivery outlet, whereby fluid and any air or gas bubbles in the cylinder are bypassed out from the uppermost part thereof, into the reservoir, after the closing of the inlet port and before pressure discharge through the loaded delivery valve, and means for venting the reservoir at a point higher than the inlet and bypass ports open thereinto, to relieve the reservoir of air or gas in excess of the capacity of that portion of the reservoir and communicating space above the said point at which the said valve venting means opens from the reservoir, said venting means in-' cluding an additionalport and coacting control edge therefor on the cylinder and plunger respectively.
  • a plunger pump for the pressure discharge of a predetermined but variable quantity of fluid through a delivery outlet, a pump cylinder, 8. plunger in the cylinder, a reservoir surrounding the cylinder, an inlet valve for the flow of fluid into the cylinder, a bypass valve forthe flowof fluid including any air or gas bubbles from tlie uppermost -part of the pump pressure space into the-reservoir on the delivery stroke after, the closing of the inlet valve, means for opening and closing the said valves at' variable points relative to the stroke of the plunger, the
  • the reservoir having a resilient capacity expansible under pressure and being provided with valve means whereby on each delivery stroke of the plunger and. before the beginning of discharge, the fluid bypassed builds up a suitable pressure ,in the reservoir intermediate of the supply and discharge pressures, said pressure being maintained in the reservoir during the period of discharge through the delivery outlet,
  • valve with controlling means therefor to relieve the pressure in the reservoir and to vent the reservoir of air or gas in excess of a definite quantity, at a suitable point in the stroke of the pump.
  • a reservoir for fluid under pressure forming part of the supply line to the pump from a low pressure source of supply said reservoir having a.
  • resilient capacity expansible under pressure, inlet and bypass valve means between the pump pressure space and the reservoir, a part of the pump charge including any air or gas bubbles, being bypassed from the pump pressure space into the reservoir on the discharge stroke of the pump before the beginning of high pressure discharge through the delivery outlet, and means whereby during a desired phase in the cycle of operation of the pump the reservoir is maintained at a suitable pressure stage intermediate of the supply and discharge pressures, said means including a non-return valve in the supply line to the reservoir, and valve means opening at another phase in the cycle of operation of the pump for venting the reservoir of any air or gas bubbles separating out from the fluid in the system and rising to the uppermost part of the reservoir, in excess of the capacity of that portion of the reservoir and communicating space above the point atwhich the valve venting means opens from the reservoir.
  • valve means for venting the reservoir is opened at the end of the suction stroke of the pump, whereby the reservoir is maintained at a suitable pressure stage intermediate of the supply and discharge pressures during the suction stroke of the pump, and a more rapid filling of the pump when the pressure in the reservoir exceeds a certain maximum less than the pressure of discharge from the pump.
  • a fluid pump in combination, a cylinder, a plunger cooperative therewith as a pump for high pressure discharge of fluid from the cylinder through a delivery outlet provided with a loaded delivery valve, a closed fluid reservoir forming part of the supplyline to the pump from a low pressure source of supply, coacting ports and control edges therefor on the cylinder and u plunger respectively, including an inlet port and a bypass port, both adapted to provide a path of flow between the pump pressure space and the reservoir, the bypass port opening from that part of the pressure space which is uppermost at a point higher than the inlet port and the said delivery outlet, whereby fluid and any air or gas bubbles in the cylinder are bypassed out from the uppermost part thereof, into the reservoir, after the closing of the inlet port and before pressure discharge through the loaded delivery valve,
  • venting means including an additional port and coacting control edge therefor on the cylinder and plunger respectively, are'so. arranged and disposed that the reservoir is vented. when the plunger is at the end of itssuction stroke.
  • venting means including an additional port and coacting control edge therefor on the cylinder and plunger respectively, are so arranged and disposed that the reservoir is vented when the plunger is at the end of its discharge stroke.

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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)
US755157A 1934-11-28 1934-11-28 Fuel pump for injectors Expired - Lifetime US2096711A (en)

Priority Applications (4)

Application Number Priority Date Filing Date Title
US755157A US2096711A (en) 1934-11-28 1934-11-28 Fuel pump for injectors
GB15196/36A GB461791A (en) 1934-11-28 1935-11-25 Improvements relating to fuel injection or like pumps
DEG5013D DE908681C (de) 1934-11-28 1935-11-26 Brennstoffeinspritzpumpe
DK53214D DK53214C (da) 1934-11-28 1935-11-27 Pumpe til Indsprøjtning af Brændsel og til lignende Formaal.

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
US755157A US2096711A (en) 1934-11-28 1934-11-28 Fuel pump for injectors

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US2096711A true US2096711A (en) 1937-10-26

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Application Number Title Priority Date Filing Date
US755157A Expired - Lifetime US2096711A (en) 1934-11-28 1934-11-28 Fuel pump for injectors

Country Status (4)

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US (1) US2096711A (de)
DE (1) DE908681C (de)
DK (1) DK53214C (de)
GB (1) GB461791A (de)

Cited By (14)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2437529A (en) * 1943-06-23 1948-03-09 Northwest Eng Co Fuel injector
US2496804A (en) * 1945-01-16 1950-02-07 United Aircraft Corp Fuel injection device
US2551053A (en) * 1946-12-06 1951-05-01 Gardiner M Rogers Fuel pump
US2556171A (en) * 1945-11-13 1951-06-12 Harold M Dudek Injection valve assembly
US2590575A (en) * 1945-08-02 1952-03-25 Gardiner M Rogers Fuel injector
US2603159A (en) * 1947-10-23 1952-07-15 Caterpillar Tractor Co Fuel injection system
US2612884A (en) * 1939-02-03 1952-10-07 Reggio Ferdinando Carlo Fuel injection pump
US2641196A (en) * 1947-06-02 1953-06-09 William V Falcon Fuel pump
US2791965A (en) * 1954-03-18 1957-05-14 Robert W Boehringer Fuel supply pump for diesel engine fuel injection equipment
DE1016493B (de) * 1950-10-02 1957-09-26 Stuttgarter Motorzubehoer G M Kraftstoffeinspritzgeraet fuer Brennkraftmaschinen
US3283727A (en) * 1964-11-02 1966-11-08 Microchemical Specialties Co Liquid dispenser with automatic air purge
EP0019933A1 (de) * 1979-06-04 1980-12-10 Caterpillar Tractor Co. Einspritzventil mit Temperaturregelung
US4527738A (en) * 1982-06-18 1985-07-09 Caterpillar Tractor Co. Modular unit fluid pump-injector
US4648556A (en) * 1983-07-29 1987-03-10 Robert Bosch Gmbh Pump/nozzle unit for fuel injection in internal combustion engines

Cited By (14)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2612884A (en) * 1939-02-03 1952-10-07 Reggio Ferdinando Carlo Fuel injection pump
US2437529A (en) * 1943-06-23 1948-03-09 Northwest Eng Co Fuel injector
US2496804A (en) * 1945-01-16 1950-02-07 United Aircraft Corp Fuel injection device
US2590575A (en) * 1945-08-02 1952-03-25 Gardiner M Rogers Fuel injector
US2556171A (en) * 1945-11-13 1951-06-12 Harold M Dudek Injection valve assembly
US2551053A (en) * 1946-12-06 1951-05-01 Gardiner M Rogers Fuel pump
US2641196A (en) * 1947-06-02 1953-06-09 William V Falcon Fuel pump
US2603159A (en) * 1947-10-23 1952-07-15 Caterpillar Tractor Co Fuel injection system
DE1016493B (de) * 1950-10-02 1957-09-26 Stuttgarter Motorzubehoer G M Kraftstoffeinspritzgeraet fuer Brennkraftmaschinen
US2791965A (en) * 1954-03-18 1957-05-14 Robert W Boehringer Fuel supply pump for diesel engine fuel injection equipment
US3283727A (en) * 1964-11-02 1966-11-08 Microchemical Specialties Co Liquid dispenser with automatic air purge
EP0019933A1 (de) * 1979-06-04 1980-12-10 Caterpillar Tractor Co. Einspritzventil mit Temperaturregelung
US4527738A (en) * 1982-06-18 1985-07-09 Caterpillar Tractor Co. Modular unit fluid pump-injector
US4648556A (en) * 1983-07-29 1987-03-10 Robert Bosch Gmbh Pump/nozzle unit for fuel injection in internal combustion engines

Also Published As

Publication number Publication date
DE908681C (de) 1954-04-08
DK53214C (da) 1937-06-14
GB461791A (en) 1937-02-24

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