US3046963A - Fuel injection systems for internal combustion engines with automatic variation of the advance of fuel injection - Google Patents

Fuel injection systems for internal combustion engines with automatic variation of the advance of fuel injection Download PDF

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US3046963A
US3046963A US73857A US7385760A US3046963A US 3046963 A US3046963 A US 3046963A US 73857 A US73857 A US 73857A US 7385760 A US7385760 A US 7385760A US 3046963 A US3046963 A US 3046963A
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piston
pump
shaft
fuel injection
ram
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US73857A
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English (en)
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Bessiere Pierre Etienne
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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02D—CONTROLLING COMBUSTION ENGINES
    • F02D1/00—Controlling fuel-injection pumps, e.g. of high pressure injection type
    • F02D1/16—Adjustment of injection timing
    • F02D1/18—Adjustment of injection timing with non-mechanical means for transmitting control impulse; with amplification of control impulse
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02D—CONTROLLING COMBUSTION ENGINES
    • F02D1/00—Controlling fuel-injection pumps, e.g. of high pressure injection type
    • F02D1/16—Adjustment of injection timing
    • F02D1/18—Adjustment of injection timing with non-mechanical means for transmitting control impulse; with amplification of control impulse
    • F02D1/183—Adjustment of injection timing with non-mechanical means for transmitting control impulse; with amplification of control impulse hydraulic
    • 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
    • F02M41/00—Fuel-injection apparatus with two or more injectors fed from a common pressure-source sequentially by means of a distributor
    • F02M41/08—Fuel-injection apparatus with two or more injectors fed from a common pressure-source sequentially by means of a distributor the distributor and pumping elements being combined
    • F02M41/10—Fuel-injection apparatus with two or more injectors fed from a common pressure-source sequentially by means of a distributor the distributor and pumping elements being combined pump pistons acting as the distributor
    • F02M41/12—Fuel-injection apparatus with two or more injectors fed from a common pressure-source sequentially by means of a distributor the distributor and pumping elements being combined pump pistons acting as the distributor the pistons rotating to act as the distributor
    • F02M41/123—Fuel-injection apparatus with two or more injectors fed from a common pressure-source sequentially by means of a distributor the distributor and pumping elements being combined pump pistons acting as the distributor the pistons rotating to act as the distributor characterised by means for varying fuel delivery or injection timing
    • F02M41/125—Variably-timed valves controlling fuel passages
    • F02M41/127—Variably-timed valves controlling fuel passages valves being fluid-actuated slide-valves, e.g. differential rotary-piston 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
    • 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
    • F02M59/20—Varying fuel delivery in quantity or timing
    • F02M59/30—Varying fuel delivery in quantity or timing with variable-length-stroke pistons
    • 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
    • F02M2700/1376—Fuel pump with control of the pump piston stroke

Definitions

  • the present invention relates to fuel injection systems for internal combustion engines with automatic variation of the advance of fuel injection.
  • the object of my invention is to provide a device of this kind which is better adapted to meet the requirements of practice than those known up to this time.
  • the variation of area of this outlet as a function of the speed serves to moderate the variation of pressure acting upon the piston of the hydraulic ram. It is thus possible to obtain a variation of the advance of fuel injection over a very wide range of different speeds.
  • volumetric pump designates a pump such that the delivery flow rate thereof is proportional to the speed at which it is driven.
  • FIG. 1 diagrammatically shows, in axial section, a fuel injection pump made according to the invention and in which the variable pressure acting upon the hydraulic ram is proportional to the speed at which the pump is driven.
  • FIG. 2 is a partial view diagrammatically showing a modification of the pump of FIG. 1, where the hydraulic ram is operated in accordance with the load of the engine fed with fuel by the injection pump.
  • FIGS. 3 to 5 inclusive show a detail of FIG. 1 according to three modifications, respectively.
  • the pump illustrated by way of example in FIG. 1 is a pump the piston of which acts as a distributing valve so as to produce successive fuel injections into the respective cylinders of an internal combustion engine from a single pump working chamber.
  • This is a possible application of the invention but this disclosure has no limitative character.
  • Fuel is fed to the working chamber of cylinder 2, that is to say the portion of said cylinder located above piston 1, through a feed conduit 11 provided in the side wall of the cylinder and a conduit 12 provided in piston 1, fuel feed taking place when these two conduits 11 and 12 register with each other, which is for instance the case when piston -1 is in its lower dead center position, as illustrated by the drawing.
  • the side wall of cylinder 2 is provided with a plurality of delivery conduits 13 (only one of which is shown by FIG. 1) each provided with a check-valve 14. Each of these delivery conduits is, during one delivery stroke, in communication with the working chamber of cylinder 2 through a groove 15 provided in the side wall of piston 1.
  • Said piston is rotated about its axis through means which will be hereinafter described, so that it acts as a distributing valve. It will be understood that the delivery of fuel through each of said conduits 13 and the feed of fuel to an injector (not shown) to which said delivery conduit leads begins as soon as piston 1, at the beginning of its upward stroke (delivery stroke), has separated conduits 11 and 12 from each other.
  • Camshaft 3 is rotated through a shaft 16 journalled, for instance through bearings 17 and 18, in the casing 19 of the pump.
  • This shaft 16 is driven in such manner by the shaft of the engine fed with fuel by the injection pump that the instantaneous angular positions of shaft 16 always correspond to the same instantaneous angular positions of the engine driving shaft.
  • Hollow shaft 3 is mounted on an extension 16a of shaft 16 so as to be able to rotate about said shaft without however being able to move axially with respect thereto.
  • the coupling connection between shaft 16 and shaft 3 is ensured by a threaded sleeve 20 provided with helical teeth of small obliquity 21, 22, in mesh with corresponding helical teeth carried, respectively, by shaft 16 and shaft 3.
  • Teeth 21, 22 are inclined in opposite directions. It will be understood that said sleeve 21 serves to couple shafts 16 and 3 together, while producing a variation of the angular position of shaft 3 with respect to shaft 16 when it is displaced in the axial direction. Such a variation corresponds to a variation of the advance of fuel injection by the pump.
  • the tubular piston 23 of said ram is a stepped piston including two portions which are slidably fitted in two respective bores 24, 25 of difierent respective diameters of the pump casing.
  • a free space 26 exists between the shoulder separating the outer surfaces of stepped piston 23 and the shoulder separating the cylindrical walls of bores 24 and 25. This free space 26 constitutes the variable volume working chamber of the hydraulic ram,
  • the annular shoulder of piston 23 preferably acts, as illustrated, through a coupling ring or annular plate 52 cooperating with a flange or collar 51 of threaded sleeve 20. 'Ihus the cooperating surfaces of annular plate 52 on the one hand and flange 51 and the annular shoulder of piston 23 on the other hand are in frictional contact with one another respectively over large areas, so that piston 23 is driven in rotation by sleeve 20 with some slipping with respect to ring 52, which increases the sensitivity of response of piston 23 to variations of the forces acting thereon to move it axially.
  • spring 27 does not bear, at one of its ends, directly against piston 23 but against a flange 51 of sleeve 20.
  • the other end of spring 27 bears against a shoulder 53 of an annular element 54 interposed between the rotating ring 17a of bearing 17 and a shoulder of shaft 16. Therefore, both ends of spring 27 bear against rotating pieces in turn together with them about the axis of shaft 16. This further has the advantage of protecting spring 27 against torsional stresses.
  • Friction ring or plate 52 is advantageously provided, on both of its faces, with radial lubricating grooves 55.
  • the portion of piston 23 which is slidable in bore 25 is so dimensioned that the edge 23a .of said piston portion is always on the outside of said bore and never enters therein. This prevents any possibility of jamming of the ram.
  • the pressure variations in the working chamber 26 of the ram are produced by a volumetric pump, as above It should be noted that in a hydraulic ram such as above described, it is [impossible to avoid some leakage which reduces the pressure of the fuel supplied in workfed with fuel by the injection pump, for instance at idling,
  • the delivery pressure of said auxiliary volumetric pump 31, 32 may become insuffi'cient, due to the existence of such a leakage, to feed fuel to the injection pump. This danger is particularly great when the engine is being started by cold weather. On the contrary, for higher speeds of the engine, the delivery pressure of the volumetric pump 31, 32 is quite suflicient, despite the above mentioned leakage, and even requires the action of the moderating valve 56. On the other hand, at low speeds of the engine, there is no utility in obtaining a correction of the advance of fuel injection. This may remain con-' stant for speeds of the engine up to for instance 800 revolutions/minute.
  • I provide a closing valve 59 in conduit 33 at a point thereof downstream of that where feed conduit 58 branches off from conduit 33 and also downstream of the leak producing means 34.
  • this closing valve is controlled in accordance with the delivery pressure of volumetric pump 31, 32, that is to for instance below 800 revolutions/minute, valve 59 cuts f ofi the delivery of pump 31, 32 from the working chamber 26 of the ram and any leakage as may exist in this ram can have no effect on the delivery pressure of the pump, which is determined exclusively by the leak producing means 34 controlled by moderator valve 56.
  • a gear pump 31, 32 driven at a speed proportional to that of the internal combustion engine and which delivers liquid into a condui-t33 provided with a discharge outlet forming a leak 34, said conduit 33 leading to the working chamber 26 of the ram.
  • the pressurerin chamber 26 increases when the speed of rotation of pump 31, 32 increases, and inversely.
  • the cross-section area of the outlet forming the leak is controlled by a moderating valve.
  • a valve is constituted, inthe embodiment illustrated, by. a piston. 56 subjected in onejdirection to the pressure existing in conduit 33, and, in the other direction, to the action of an opposing spring 57.
  • the whole is arranged in such manner that said moderating valve increases the area of the outlet forming the leak when the pressure in conduit 33 increases and reduces said cross-section area when this pressure in conduit 33, decreases.
  • the shape of the outline of the outlet through which liquid can leak out isrsuitably chosen (circular, rectangular, triangular, or other shape) so that the variation of pressure in chamber 26 takes place according to a law corresponding to the desired variation of theadvance of fuel injection. 7
  • Gear pump 31, 32 is driven by hollow shaft 3 which drives the gear 32 of said pump through a toothed wheel 35.
  • V 7
  • auxiliary pump 31, 32 serves both to supply the control pressure for the hydraulic ram and to feed fuel to the cylinder of the injection pump through a conduit 58 which connects the feed conduit 11 of the injection pump with the delivery conduit 33 of pump 31, 32.
  • the pump illustrated by the drawings comprises selfregulating means for controlling, in accordance With the speed, the flow rate of the pump per cycle thereof. Said means operate on the basis of the so-called liquid abutment phenomenon.
  • Such self-regulating means comprise a control member 36 called shuttle which, during the delivery stroke of the piston 1 of the pump, moves upwardly under the effect of a liquid delivered by an auxiliary piston 37 which is integral with the main piston 1 and which cooperates with an auxiliary cylinder 38; At the end of its upward stroke, which is determined by theopening of a discharge conduit 39, the shuttle opens another discharge conduit 40 in communication with the working chamber of cylinder 2 so that the opening of said discharge conduit 40 stops injection.
  • shuttle 36 During the downward stroke of pistons 1 and 37, shuttle 36 also moves in the downward direction under the action of a return spring 41, but this movement is slowed down due to the factthat the shuttle must force the liquid located under it, through a throttled passage 42, preferably adjustable by means of a screw 43. Consequently, when the speed of the pump exceeds a given value, shuttle 36 has not had time, during its downward strokes, to come back to its lowermost position when a new stream of liquid is supplied into the space below it to produce the nextupward stroke thereof. The stroke is therefore shortened, which advances the time when the shuttle opens shaped wheel 45. In the hub 46 of said wheel 45 there is provided a longitudinal groove 47 which cooperates with a radial projection 4 carried by piston 1. The Whole is arranged in such manner that piston 1 can have its reciprocating movements under the effect of cam 4, while being able to rotate about its axis under the action of elements 3, 35 and 45.
  • bell-shaped Wheel 45 rotates in a housing 49 of casing 19 which acts as a guide and bears against a needle bearing 51?.
  • the pressure produced in the working chamber 26 of the ram and consequently the advance of fuel injection depend upon the speed of the engine which is fed with fuel from the injection pump.
  • this speed does not vary or varies a little and when it is desired to vary this advance to fuel injection as a function of the load of the engine, it is advantageous to have recourse to another feature of the invention which is based upon the fact that the load depends upon the amount of fuel that is truly injected into the engine.
  • adjustment of this amount takes place in such manner that only a portion of the fuel displaced by the piston 1 of the pump during its delivery stroke is sent toward the injector, whereas another portion is discharged to the outside.
  • the amount of fuel that is truly injected is the smaller as the discharged amount is greater. Therefore I make use of the variation of the amount of fuel discharged to the outside to control the pressure in the working chamber of the hydraulic ram.
  • FIG. 2 An embodiment of such a system is shown by FIG. 2.
  • This figure shows a modification of the injection pump of FIG. 1, in which the variable pressure in working chamber 26 depends upon the load of the engine.
  • FIG. 2 diagrammatically shows, in the form of a screw 34a, means for varying the section of passage for the leak, but of course said means might be automatically arranged as shown by FIG. 1.
  • a fuel injection system for an internal combustion engine which comprises, in combination, a fuel injection pump including a cylinder and a piston mounted for reciprocating movement in said cylinder, a rotating member having its axis located in fixed position with respect to said cylinder, said rotating member being operatively connected with said piston for imparting thereto said reciprocating movement, a driving shaft coupled with said engine and in line With said rotating member, a threaded sleeve in mesh both with said shaft and with said rotating member for coupling them in rotation, both said shaft and said member being fixed in the direction of their common axis with respect to said cylinder and said sleeve being movable axially with respect to said shaft and said member so that axial displacement of said sleeve with respect to said shaft and said member varies the angular setting of said rotating member with respect to said shaft, a hydraulic ram comprising on the one hand, a casing fixed with respect to said cylinder and provided with a cylindrical recess coaxial with said shaft and said member and on the other hand a hydraulic
  • a fuel injection system for an internal combustion engine which comprises, in combination, a fuel injection pump including a cylinder and a piston mounted for reciprocating movement in said cylinder, a rotating member having its axis located in fixed position with respect to said cylinder, said rotating member being operatively connected with said piston for imparting thereto said reciprocating movement, a driving shaft coupled with said engine and in line with said rotating member, a threaded sleeve in mesh both with said shaft and with said rotating member for coupling them in rotation, both said shaft and said member being fixed in the direction of their common axis with respect to said cylinder and said sleeve being movable axially with respect to said shaft and said member so that axial displacement of said sleeve with respect to said shaft and said member varies the angular setting of said rotating member with respect to saidshaft, a hydraulic ram comprising on the one hand, a casing fixed with'respect to said cylinder and provided with a cylindrical recess coaxial with said shaft and said member and on the other hand
  • a fuel injection system for an internal combustion engine which comprises, in combination, a fuel injection pump including a cylinder and a piston mounted for reciprocating movement in said cylinder, a rotating member having its axis located in fixed position with respect to said cylinder, said rotating member being operatively connected with said piston for imparting thereto said reciprocating movement, a driving shaft coupled with said engine and in line with said rotating member, a threaded sleeve surrounding adjoining portions of said shaft and said rotating member and in mesh with said portions for coupling them in rotation, both said shaft and said member being fixed in the direction of their common axis with respect to said cylinder and said sleeve being movable axially with respect to said shaft and said member so that axial displacement of said sleeve with respect to said shaft and said member varies the angular setting of said rotating member with respect to said shaft, a hydraulic ram comprising on the one hand, a casing fixed with respect to said cylinder and provided with a cylindrical recess coaxial with said shaft and said member and on
  • a fuel injection system for an internal combustion engine which comprises, in combination, a fuel injection pump including a cylinder and a piston mounted for reciprocating movement in said cylinder, a rotating mem her having its axis located in fixed position with respect to said cylinder, said rotating member being operatively connected with said piston for imparting thereto said reciprocating movement, a driving shaft coupled with said engine and in line with said rotating member, a threaded sleeve surrounding adjoining portions of said shaft and said rotating member and in mesh with said portions for coupling them in rotation, both said shaft and said mem ber being fixed in the direction of their common axis with respect to said cylinder and said sleeve being movable axially with respect to said shaft and said member'so that axial displacement of said sleeve with respect to said shaft and said member varies the angular setting of said rotating member with respect to said shaft, 21 hydraulic ram comprising on the one hand, a casing fixed withrespect to said'cylinder and provided with a cylindrical re cess coaxial
  • a system according to claim 5 further including an annular part fixed to said driving shaft to form an outward projection around it, said part being located at'a distance from saidsleeve flange and on the other side thereof from said working chamber, said resilient means operatively connected with said ram piston consisting of a spring interposed between said annular part and said sleeve flange.
  • a fuel injection system for an internal combustion engine which comprises, in combination, a fuel injection pump including a cylinder and a piston mounted for 're-.
  • a rotating member having its axis located in fixed position with respect 7 to said cylinder, said rotating member being operatively connected with said piston for imparting thereto said reciprocating movement
  • a driving shaft coupled with said engine and in line with said rotating member, a threaded sleeve surrounding adjoining portions of said shaft and said rotating member and in mesh with said portions for 7 coupling them in rotation, both said shaft and said member being fixed inthe direction of their common axis with respect to said cylinderand said sleeve being movable axially with respect to said shaft and said member so that axial displacement of said sleeve with respect to said shaft and said member varies the angular-setting of said rotating member with respect to said shaft, a hydraulic ram comprising on the one hand, a casing fixed with respect to said cylinder and provided with a cylindrical recess coaxial with said shaft and said member and on the other hand a ram piston fitting slidably in said recess, said recess and said ram
  • a system according to claim 9 in which the cylindrical portion of said casing recess that is closer to said rotating member is shorter, in the axial direction, than the portion of said stepped piston that is housed therein.
  • a fuel injection system for an internal combustion engine which comprises, in combination, a fuel injection pump including a cylinder and a piston mounted for reciprocating movement in said cylinder, a rotating memher having its axis located in fixed position with respect to said cylinder, said rotating member being operatively connected with said piston for imparting thereto said reciprocating movement, a driving shaft coupled with said engine and in line with said rotating member, a threaded sleeve in mesh both with said shaft and with said rotating member for coupling them in rotation, both said shaft and said member being fixed in the direction of their common axis with respect to said cylinder and said sleeve being movable axially with respect to said shaft and said member so that axial displacement of said sleeve with respect to said shaft and said member varies the angular setting of said rotating member with respect to said shaft, a hydraulic ram comprising on the one hand, a casing fixed with respect to said cylinder and provided with a cylindrical recess coaxial with said shaft and said member and on the other hand
  • a fuel injection system for an internal combustion engine which comprises, in combination, a fuel injection pump including a cylinder and a piston mounted for reciprocating movement in said cylinder, a rotating member having its axis located in fixed position with respect to said cylinder, said rotating member being operatively connected with said piston for imparting thereto said reciprocating movement, a driving shaft coupled with said engine and in line with said rotating member, a threaded sleeve in mesh both with said shaft and with said rotating member for coupling them in rotation, both said shaft and said member being fixed in the direction of their common axis with respect to said cylinder and said sleeve being movable axially with respect to said shaft and said member so that axial displacement of said sleeve with respect to said shaft and said member varies the angular setting of said rotating member with respect to said shaft, a hydraulic ram comprising on the one hand, a casing fixed with respect to said cylinder and provided with a cylindrical recess coaxial with said shaft and said member and on the other hand

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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)
  • High-Pressure Fuel Injection Pump Control (AREA)
US73857A 1959-12-10 1960-12-05 Fuel injection systems for internal combustion engines with automatic variation of the advance of fuel injection Expired - Lifetime US3046963A (en)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
FR812698A FR1251425A (fr) 1959-12-10 1959-12-10 Perfectionnements apportés aux moyens d'autorégulation de pompes d'injection pour moteurs, notamment à ceux susceptibles de faire varier l'avance de l'injection
FR838927A FR78863E (fr) 1959-12-10 1960-09-19 Perfectionnements apportés aux moyens d'autorégulation de pompes d'injection pour moteurs, notamment à ceux susceptibles de faire varier l'avance de l'injection

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US3046963A true US3046963A (en) 1962-07-31

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US73857A Expired - Lifetime US3046963A (en) 1959-12-10 1960-12-05 Fuel injection systems for internal combustion engines with automatic variation of the advance of fuel injection

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US (1) US3046963A (es)
CH (1) CH373224A (es)
DE (1) DE1218796B (es)
ES (1) ES263109A1 (es)
FR (2) FR1251425A (es)
GB (1) GB963069A (es)

Cited By (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE1295311B (de) * 1963-07-19 1969-05-14 United States Steel Corp Vorrichtung zum Herstellen von Metallueberzuegen durch Vakuumaufdampfen
US3557764A (en) * 1967-12-08 1971-01-26 Cav Ltd Liquid fuel pumping apparatus
US3726263A (en) * 1970-03-18 1973-04-10 K Kemp Liquid fuel pumping apparatus
US3777731A (en) * 1973-02-14 1973-12-11 Diesel Kiki Co Fuel injection system in a distributor-type injection pump for internal combustion engine
US3930480A (en) * 1974-05-02 1976-01-06 Yanmar Diesel Engine Co., Ltd. Fuel-injection pump for an internal combustion engine
DE2754152A1 (de) * 1976-12-13 1978-06-15 Stanadyne Inc Kraftstoffeinspritzpumpe mit umlaufendem verteiler

Families Citing this family (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR1306633A (fr) * 1961-06-15 1962-10-19 Perfectionnements apportés aux pompes d'injection de combustible

Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US1736242A (en) * 1924-01-25 1929-11-19 Andre C Attendu Fuel pump
US2177120A (en) * 1936-09-09 1939-10-24 Scintilla Ltd Fuel injection apparatus
US2305308A (en) * 1939-02-17 1942-12-15 Fischlmayr Hans Automatic timing mechanism for fuel injection pumps
US2624327A (en) * 1950-03-30 1953-01-06 American Bosch Corp Fuel injection apparatus
US2902019A (en) * 1957-04-13 1959-09-01 Bosch Gmbh Robert Fuel supply system for internal combustion engines
US2910975A (en) * 1957-02-22 1959-11-03 Cav Ltd Liquid fuel pumps for internal combustion engines

Family Cites Families (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE723144C (de) * 1937-04-05 1942-07-31 Scintilla Ag Hydraulische Verstellvorrichtung fuer den Einspritzzeitpunkt bei Brennstoffeinspritzpumpen von Brennkraftmaschinen
US2190900A (en) * 1937-04-05 1940-02-20 Scintilla Ltd Motion transmitting mechanism
DE895995C (de) * 1940-01-20 1953-11-09 Friedrich Wilhelm Deckel Dipl Einrichtung zur selbsttaetigen Spritzbeginnverstellung an Einspritzpumpen fuer Brennkraftmaschinen
US2372180A (en) * 1941-06-12 1945-03-27 Timken Roller Bearing Co Angularly adjustable coupling
DE1055878B (de) * 1954-07-29 1959-04-23 Bosch Gmbh Robert Kraftstoffeinspritzpumpe fuer mehrzylindrige Brennkraftmaschinen
US2756725A (en) * 1954-10-21 1956-07-31 Woodward Governor Co Compensated condition control regulator

Patent Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US1736242A (en) * 1924-01-25 1929-11-19 Andre C Attendu Fuel pump
US2177120A (en) * 1936-09-09 1939-10-24 Scintilla Ltd Fuel injection apparatus
US2305308A (en) * 1939-02-17 1942-12-15 Fischlmayr Hans Automatic timing mechanism for fuel injection pumps
US2624327A (en) * 1950-03-30 1953-01-06 American Bosch Corp Fuel injection apparatus
US2910975A (en) * 1957-02-22 1959-11-03 Cav Ltd Liquid fuel pumps for internal combustion engines
US2902019A (en) * 1957-04-13 1959-09-01 Bosch Gmbh Robert Fuel supply system for internal combustion engines

Cited By (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE1295311B (de) * 1963-07-19 1969-05-14 United States Steel Corp Vorrichtung zum Herstellen von Metallueberzuegen durch Vakuumaufdampfen
US3557764A (en) * 1967-12-08 1971-01-26 Cav Ltd Liquid fuel pumping apparatus
US3726263A (en) * 1970-03-18 1973-04-10 K Kemp Liquid fuel pumping apparatus
US3777731A (en) * 1973-02-14 1973-12-11 Diesel Kiki Co Fuel injection system in a distributor-type injection pump for internal combustion engine
US3930480A (en) * 1974-05-02 1976-01-06 Yanmar Diesel Engine Co., Ltd. Fuel-injection pump for an internal combustion engine
DE2754152A1 (de) * 1976-12-13 1978-06-15 Stanadyne Inc Kraftstoffeinspritzpumpe mit umlaufendem verteiler

Also Published As

Publication number Publication date
FR1251425A (fr) 1961-01-20
FR78863E (fr) 1962-09-21
CH373224A (fr) 1963-11-15
ES263109A1 (es) 1961-05-01
DE1218796B (de) 1966-06-08
GB963069A (en) 1964-07-08

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