US2937637A - Injection pump - Google Patents

Injection pump Download PDF

Info

Publication number
US2937637A
US2937637A US800159A US80015959A US2937637A US 2937637 A US2937637 A US 2937637A US 800159 A US800159 A US 800159A US 80015959 A US80015959 A US 80015959A US 2937637 A US2937637 A US 2937637A
Authority
US
United States
Prior art keywords
cylinder
piston
fuel
housing
opening
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
US800159A
Other languages
English (en)
Inventor
Heiser Joachim
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Robert Bosch GmbH
Original Assignee
Robert Bosch GmbH
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Robert Bosch GmbH filed Critical Robert Bosch GmbH
Application granted granted Critical
Publication of US2937637A publication Critical patent/US2937637A/en
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

Links

Images

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
    • 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
    • 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
    • F02M41/124—Throttling of fuel passages to or from the pumping chamber
    • 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
    • F02M41/126—Variably-timed valves controlling fuel passages valves being mechanically or electrically adjustable sleeves slidably mounted on rotary piston

Definitions

  • injection pumps are used with in.- ternal combustion engines in order to control the supply of-v fuel to the cylinders of the internal combustion engines.
  • Such pumps will deliver a certain amount of fuel to the cylinders of the engine when the engine is opero ating under usual full load conditions.
  • the structures used for providing this greater delivery of fuel in excess of that required for full load operating conditions are extremely complex and do not operate with the best possible reliability and efficiency.
  • One of the objects of the present invention is to provide an injection pump capable of providing the excess amount of fuel delivery to the cylinders of the engine necessary vfor starting purposes, -for example, with a structure which is exceedingly simple and reliable in operation as well as highly eflicient.
  • Another object of the present invention is to provide an injection pump which can be conveniently adjusted so as to regulate the amount of fuel delivered to the cylinders during full load normal operating conditions.
  • a further object of the present invention is to provide an injection pump where the structure which is used for providing the excess amount of fuel necessary for starting purposes, for example, is also capable of being used to regulate the maximum amount of fuel delivered to the engine during full load normal operating conditions.
  • the present invention includes in an injection pumpy a cylinder means having a closed end and an opposite open end and ⁇ formed between its ends with an overflow passage extending through a wall portion of the cylinder means 'from the interior 50 to the exterior thereof.
  • a hollow piston extends slidably into the cylinder means through the open end thereof and has an open end directed toward the closed end of the cylinder means so that the interior of the piston forms part of a pumping chamber with the cylinder means, this piston having a side wall portion formed with an opening passing therethrough and communicating with the overflow passage of the cylinder means when the latter and the piston have a given axial position with respect to each other.
  • a means cooperates with the cylinder means for automatically maintaining the overflow passage thereof beyond the opening of the piston when the latter reciprocates at a relatively low speed in the cylinder means and for automatically advancing the cylinder means along its axis to place the overflow passage of the cylinder means in a position where it will communicate with the opening of the piston during reciprocation of the latter at speeds which are higher than the abovementioned relatively low speed, so that at such higher speeds less fuel is pumped than at the'relatively low 70 speed.
  • the drawing shows in an axial sectional elevational view an injection pump constructed according to the present invention.
  • the injection pump illustrated includes a housing 1.
  • the injection pump illustrated is adapted to cooperate with an unillustrated internal combustion engine having four cylinders.
  • the housing 1 is formed with an elongated bore into which a pump cylinder 2 is pressed so as to be xedly connected in this way with the housing 1, and in the bore'of the housing 1 which receives the pump cylinder 2 there is arranged an additional pump cylinder 3 which-is axiallyshiftable in the housing 1 and which has a fluid-tight sliding fit with the surface of the bore of the housing 1 in which the cylinder 3 is axially slidable.
  • the injection pump illustrated includes a combined pumping and distributing member composed of the parts 4 and 5.
  • the part 4 is an elongated tubular element which is axially slidable in the stationary cylinder 2 and at its top end, as viewed in the drawing, the part 4 is in engagement with the second part 5 which has a smaller diameter than the part 4 and which extends slidably into the cylinder 3 through the bottom open end thereof, as viewed in the drawing, this part 5 forming a hollow piston which cooperates with the cylinder 3 in aA manner described below.
  • the element 4 is provided at its bottom end, as viewed in the drawing, with a ange 6, and this lower end of the part 4 extends into a recess formed in the top end portion of a cam 7' which is driven so as to rotate about its axis, this cam 7 lbeing driven by the engine itself and being coaxial with the parts 2 5.
  • a pin 8 is xedly carried 'by the cam 7 and extends into a cutout of the flange 6 so that lthe part 4 is constrained to rotate together with the cam 7, and in the recess of the cam 7 which receives the bottom end portion of the part 4 is located a snap ring 9 which ⁇ constrains the part 4 to move axially with the'cam 7.
  • a coil spring 11 bears at its top end, as viewed in the drawing, against a ball thrust bearing 12 which cooperates with the housing-1 in the manner shownin'the drawing, and at its bottom end the coil spring 11 bears directly against the cam 7 so as to maintain the latter against the rollers 13 which are turnably supported for rotation about their axes by the housing 1 in the manner illustrated in the drawing.
  • the cam 7 is provided a't.
  • the part 4 is essentiallyvan elongated hollow tube, and the bottom end of thistube is closed by a plug member 14 in the form of a stepped pin having between its ends a shoulder which is directed away from the cam 7.
  • a coil spring 15 engages this shoulder, and the top end of this coil spring 1S engages a valve 16 to urge the latter into engagement with a valve seat 17 formed in the interior of the part 4.
  • the part of the valve 16 above its frusto-conical valve portion which engages the valve seat 17 is provided with elongated tins which extend axially along the interior of the part 4 and engage the inner surface thereof, as shown in the drawing, so that in this way the valve 16 is guided for axial movement with respect to the part 4.
  • the bore of the housing 1 which receives the stationary cylinder 2 and the slidable cylinder 3 is closed at its top end, as viewed in the drawing, by a plug 21, and a spring 20 engages the top end of the stationary cylinder 2 and presses against the bottom end of the cylinder 3, as viewed in the drawing, so as to urge this cylinder 3 into engagement with the plug 21 so that the latter acts as a stop for limiting the movement of the cylinder 3 in one direction.
  • the plug 21 is provided at its bottom end, as viewed in the drawing, with a peripheral portion of a smaller diameter than the remainder of the plug 21 and in direct engagement with the top end of the cylinder 3 so that this peripheral annular portion of the plug 21 at its bottom end, as viewed in the drawing, acts as a stop means for the cylinder 3.
  • An axially stationary piston 22 extends slidably into the cylinder 3 through its top open end, as viewed in the drawing.
  • This axially stationary piston 22 is in the form of a stepped solid pin, as illustrated.
  • the element 22 has a head end the underside of which is engaged by a snap ring 23 carried by the plug 21, so that in this way the piston element 22 is maintained axially stationary while at the same time it is free to turn about its axis.
  • This axially stationary piston 22 is formed between its ends with a shoulder directed downwardly toward the hollow axially reciprocable piston 5, and a spring 24 presses with its top end against the latter shoulder and with its bottom end against the bottom end wall of the axially reciprocable piston so as to maintain the latter in engagement with the top end of the element 4, in fluid-tight engagement with the latter, as illustrated in the drawing.
  • the bottom end wall of the piston 5 is formed with an opening passing therethrough so that the parts 4 and 5 form an elongated hollow combined pumping and distributing means which is axially bored throughout its entire length.
  • the piston member 5 is formed in a side wall portion thereof with an opening 25 passing therethrough, and the cylinder 3 is formed in its interior with an annular groove 26 which communicates with a passage 27 extending from the groove 26 to the exterior of the cylinder 3, the groove 26 and passage 27 combining together to form an overow passage formed in the cylinder 3 between its ends, as shown in the drawing.
  • the overflow passage 26, 27 of the cylinder 3 communicates with the chamber 28 in which the spring 20 is located, and this chamber 28 in turn communicates through the passage 29 formed in the housing 1 with the chamber 30 in which the spring 11 is located.
  • the cylinder 3 together with the axially stationary piston 22 cooperate together to form a cylinder means in which the hollow piston 5 is axially slidable, and the piston 5 forms with the cylinder means 3, 22 a pumping chamber 31 which is separated from the pressure charnber 32 in the part 4 by the valve 16.
  • the element 4 is formed lwith an opening 33 extending from the chamber 32 to the exterior surface of the part 4, and the housing 1 is formed with four passages 34 one of which is shown in dotted lines in the drawing.
  • the opening 33 communicates in succession with these four passages 34, and these passages 34 respectively communicate with the outlets 35 which are in turn placed in communication with the several cylinders of the engine, respectively, so
  • the fuel which is delivered to the pumping chamber 31 is derived from a fuel reservoir 37 and the fuel is pumped from the reservoir 37 by a fuel supply pump 38 which is driven by the engine itself.
  • the fuel flows,
  • a tumable transversely bored valve member 41 is turnably carried by the housing 1 in a position extending across the passage 40 with the bore of the valve 41 capable of being turned with. respect to the passage 40 so as to control the cross section through which the fuel ows to the opening 42 of the stationary cylinder 2.
  • This opening 42 of the stationary cylinder 2 is placed in successive communication with four open ings 43 formed in the part 4, and these openings 43 which are displaced by from each other around the axis of the member 4 and two of which are shown in the drawing successively communicate with the opening 42 during axial reciprocation and rotation of the member 4, the several openings 43 forming inlets into the pumping chamber 31 through which the fuel ows into this pumping chamber during the suction strokes of the pump.
  • the housing 1 together with the plug 21 form a housing means which provides the bore in which the cylinder 3 is axially slidable with a closed end directed toward the closed end of the cylinder means 3, 22 formed by the axially stationary piston 22 which extends into the cylinder 3.
  • These closed ends namely, the closed end of the cylinder means 3, 22 and the closed end of the bore of the housing means 1, 21, dene between themselves a pressure chamber 46.
  • the annular lip at the bottom end of the plug 21, as viewed in the drawing, which forms a stop means for the cylinder 3, is formed with a notch 45 passing radially therethrough, and the housing 1 is formed with a passage 44 extending from the passage 40 at a point thereof upstream of the valve 41 to the space in the bore of the housing 1 which surrounds the bottom annular lip of the plug 21.
  • the fuel supply pump 38 which delivers fuel to the pumping chamber 31 also delivers fuel to the pressure chamber 46.
  • An overflow valve 48 communicates with the discharge conduit leading from the fuel supply pump 38 so that the excess fuel which is delivered by the pump 38 can ow through the overflow valve 48 back to the reservoir 37. Moreover, this overflow valve will guarantee that the pressure of the fuel pumped by the supply pump 38 will be proportional to the speed of the engine which drives the pump 38.
  • the chamber 30 of the housing 1 in which the spring 11 is located communicates through an opening 49 of the housing 1 and a suitable conduit with the fuel reservoir 37.
  • the cylinder 3 is formed in its outer surface with an elongated axially extending recess 51 into which a pin 52 extends.
  • This pin is xed to a rod 53 and the axis of the pin 52 is spaced from but ⁇ parallel to the axis of the rod 53 and the latter is turnably supported by the housing 1 so that due to the eccentric mounting of the pin 52 the position of the latter along the axis of the cylinder 3 can be regulated.
  • a tubular member 54 surrounds a portion of the rod 51 and is threaded into a bore of the housing 1 for clamping the rod 51 to the housing 1 in an adjusted angular position.
  • the cam 7 is illustrated in the drawing at the end of a suction stroke.
  • the -part 4 Wlll IS move upwardly as viewed in the drawing so as to close the opening 42 of the stationary cylinder 2.
  • the pressure stroke starts.
  • the cylinder 3 is illustrated in the drawing in the position it takes when the engine is started. In this position of the cylinder 3 the pressure stroke ends before the opening 25 can reach the overow passage 26, 27.
  • the valve 16 closes and the pumping chamber 31 is placed under vacuum so as to produce a suction. This results from the increased volume of the pumping chamber 31 produced by movement of the piston member 5 away from the stationary piston member 22. As soon as the member 4 has moved in a downward direction, as viewed in the drawing, through a distance sufcient to place the opening 42 in communication with one of the openings 43, the fuel flows into the pumping chamber under the pressure provided by the fuel supply pump 38.
  • the amount of fuel which ows into the pumping chamber 31 depends upon the position of the valve 41 which controls the cross section of flow through the passage 40, the supply pressure of the pump 38 which supply pressureV is proportional to the speed of the engine which Adrives the fuel supply pump 38, and also the time during which the particular opening 43 remains in communication with the opening 42, this latter time also depending upon the speed of the engine which drives the cam 7.
  • this cylinder 3 will remain at this position during the entire subsequent operation of the engine.
  • the operating position of the cylinder 3 can be regulated andin this way it is possible to regulate the maximum amount of fuel delivered by the injection pump to the engine during normal full load operation thereof.
  • This latter maximum amount of fuel is of course less than the amount of fuel delivered during starting of the engine when the pressure in the chamber 46 cannot hold the cylinder 3 against the stop means 52 so that the opening 25 does not reach the overflow passage 26, 27. It will be noted that with this construction because the piston 22 remains axially stationary the volume of the pumping chamber 31 does not change as a result of axial shifting. of the cylinder 3.
  • cylinder means having a closed end and an opposite open end and formed between said ends with an overow passage extending through a wall portion of said cylinder means from the interior to the exterior thereof; a hollow piston extending slidably into said cylinder means through said open end thereof and having an open end directed toward said closed end of said cylinder means so that the interior of said piston forms part of a.
  • said piston having a side wall portion formed with an opening passing therethrough and communicating with said overflow passage when said cylinder means and piston have a given axial position with, respect to each other; and means cooperating with said cylinder for automatically maintaining said overflow passage thereof beyond said opening of said piston when the latter reciprocates at a relatively low speed in said cylinder means and for automatically advancing said cylinder means along its axis to place said overflowl passage of said cylinder means in a position where it will communicate with said opening during reciprocation of said piston at speeds higher than said relatively low speed, so that at said higher speeds less fuel is pumped than at said relatively low speed.
  • cylinder means having a closed end and an opposite open end and formed between said ends with an overow passage extending through a wall portion of said cylinder means from the interior to the exterior thereof; a hollow piston extending slidably into said cylinder means through said open end thereof and having an open end directed toward said closed end of said cylinder means so that the interior of the piston forms part of a pumping chamber with said cylinder means, said piston having a side ⁇ wall portion formed with an opening passing therethrough and communicating with said overow passage when said cylinder means and piston have a given axial position with respect to each other; housing means formed with an elongated bore in which said cylinder means is axially slidable, said bore of said housing means having a closed end toward which said closed end of said cylinder means is directed, and said closed end of said bore forming with said closed end of said cylinder means a pressure chamber so that when fuel from a fuel supply pump which delivers fuel to said pumping chamber is also delivered to said pressure chamber the pressure of the fuel in the
  • cylinder means having a closed end and an opposite open end and formed between said ends with an overow passage extending through a wall portion of said cylinder means from the interior to the exterior thereof; a hollow piston extending slidably into said cylinder means through said open end thereof and having an open end directed toward said closed end of said cylinder means so that the interior of the piston forms part of a pumping chamber with said cylinder means, said piston having a side wall portion formed with an opening passing therethrough and communicating with said overflow passage when said cylinder means and piston have a given axial position with respect to each other; housing means formed with an elongated bore in which said cylinder means is axially slidable, said bore of said housing means having a closed end toward which said closed end of said cylinder means is directed, and said closed end of said bore forming with said closed end of said cylinder means a pressure chamber so that when fuel from a fuel supply pump which delivers fuel to said pumping chamber is also delivered to said pressure chamber the pressure of the fuel in the pressure chamber
  • cylinder means having a closed end and an opposite open end and formed between said ends with an overow passage extending through a wall portion of said cylinder means from the interior to the exterior thereof; a hollow piston extending slidably into said cylinder means through said open end thereof and having an open end directed toward said closed end of said cylinder means so that the interior of the piston forms part of a pumping chamber with said cylinder means, said piston having a side wall portion formed with an opening passing therethrough and communicating with said overflow passage when said cylinder means and piston have a given axial position with respect to each other; housing means formed with an elongated bore in which said cylinder means is axially slidable, said bore of said housing means having a closed end toward which said closed end of said cylinder means is directed, and said closed end of said bore forming with said closed end of said cylinder means a pressure chamber so that when fuel from a fuel supply pump which delivers fuel to said pumping chamber is also delivered to said pressure chamber the pressure of the fuel inthe pressure chamber
  • an elongated hollow cylinder having a pair of opposed open ends and formed between said ends with an overflow passage extending through a wall portion of said cylinder from the interior to the exterior thereof; an axially stationary solid piston extending slidably into said cylinder through one of said open ends thereof so that said cylinder can move axially along said axially stationary piston; and an axially reciprocable hollow piston extending slidably into said cylinder through the other of said open ends thereof, said hollow piston having an open end directed toward said solid piston so that the latter together with said hollow piston define a pumping chamber in said cylinder, said hollow piston being formed with an opening passing through a wall portion thereof so that when said opening communicates with said overow passage fuel in said pumping chamber will ow through said overflow passage, whereby the position of said cylinder along its axis can be regulated to control the point when said opening communicates with saidvoverow passage without changing the volume of said pumping chamber.
  • an elongated hollow cylinder having a pair of opposed open ends and formed between said ends with an overow passage extending through a wall portion of said cylinder from the interior to the exterior thereof; an axially stationary solid piston extending slidably into said cylinder through one of said open ends thereof so that said cylinder can move axially along said axially stationary piston; an axially reciprocable hollow piston extending slidably into said cylinder through the other of said open ends thereof, said hollow piston having an open end directed toward said solid piston so that the latter together with said hollow piston define a pumping chamber in said cylinder, said hollow piston being formed with an opening passing through a wall portion thereof so that when said opening communicates with said overow passage fuel in said pumping chamber will flow through said overtiow passage, whereby the position of said cylinder along its axis can be regulated to control the point when said opening communicates with said overow passage without changing the volume of said pumping chamber; a housing formed with an elongated bore in which said cylinder

Landscapes

  • Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Fuel-Injection Apparatus (AREA)
US800159A 1958-03-26 1959-03-18 Injection pump Expired - Lifetime US2937637A (en)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
DEB48333A DE1058790B (de) 1958-03-26 1958-03-26 Kraftstoffeinspritzpumpe fuer mehrzylindrige Brennkraftmaschinen

Publications (1)

Publication Number Publication Date
US2937637A true US2937637A (en) 1960-05-24

Family

ID=6968540

Family Applications (1)

Application Number Title Priority Date Filing Date
US800159A Expired - Lifetime US2937637A (en) 1958-03-26 1959-03-18 Injection pump

Country Status (5)

Country Link
US (1) US2937637A (de)
CH (1) CH368342A (de)
DE (1) DE1058790B (de)
FR (1) FR1219057A (de)
GB (1) GB863698A (de)

Cited By (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3139875A (en) * 1961-08-22 1964-07-07 Cummins Engine Co Inc Fuel supply apparatus for internal combustion engine
US3630643A (en) * 1969-02-28 1971-12-28 Bosch Gmbh Robert Fuel injection pump
US3927654A (en) * 1973-08-22 1975-12-23 Cummins Engine Co Inc Fuel supply system
US4036326A (en) * 1974-08-02 1977-07-19 Mikuni Kogyo Kabushiki Kaisha Lubricating oil pump
US4060350A (en) * 1975-03-27 1977-11-29 Vysoke Uceni Technicke Cylinder head mounting arrangement for a diesel injection pump
US4537171A (en) * 1983-02-28 1985-08-27 Nippondenso Co., Ltd. Fuel injection device
US5220894A (en) * 1989-11-13 1993-06-22 Robert Bosch Gmbh Fuel injection pump for internal combustion engines

Families Citing this family (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE1109955B (de) * 1960-02-24 1961-06-29 Bosch Gmbh Robert Kraftstoffeinspritzpumpe an einer Brennkraftmaschine
DE1189795B (de) 1961-04-29 1965-03-25 Maschf Augsburg Nuernberg Ag Brennstoffeinspritzpumpe fuer Brennkraftmaschinen mit zwei koaxialen Pumpenkolben
DE1156605B (de) * 1961-08-25 1963-10-31 Bosch Gmbh Robert Kraftstoffeinspritzpumpe fuer mehrzylindrige Brennkraftmaschinen

Citations (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CH265005A (de) * 1947-06-20 1949-11-15 Cav Ltd Brennstoffkolbenpumpe.
US2810376A (en) * 1954-07-29 1957-10-22 Bosch Gmbh Robert Injection pump

Patent Citations (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CH265005A (de) * 1947-06-20 1949-11-15 Cav Ltd Brennstoffkolbenpumpe.
US2810376A (en) * 1954-07-29 1957-10-22 Bosch Gmbh Robert Injection pump

Cited By (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3139875A (en) * 1961-08-22 1964-07-07 Cummins Engine Co Inc Fuel supply apparatus for internal combustion engine
US3630643A (en) * 1969-02-28 1971-12-28 Bosch Gmbh Robert Fuel injection pump
US3927654A (en) * 1973-08-22 1975-12-23 Cummins Engine Co Inc Fuel supply system
US4036326A (en) * 1974-08-02 1977-07-19 Mikuni Kogyo Kabushiki Kaisha Lubricating oil pump
US4060350A (en) * 1975-03-27 1977-11-29 Vysoke Uceni Technicke Cylinder head mounting arrangement for a diesel injection pump
US4537171A (en) * 1983-02-28 1985-08-27 Nippondenso Co., Ltd. Fuel injection device
US5220894A (en) * 1989-11-13 1993-06-22 Robert Bosch Gmbh Fuel injection pump for internal combustion engines

Also Published As

Publication number Publication date
DE1058790B (de) 1959-06-04
GB863698A (en) 1961-03-22
FR1219057A (fr) 1960-05-16
CH368342A (de) 1963-03-31

Similar Documents

Publication Publication Date Title
US4134549A (en) Injectors of a fuel supply system for an internal combustion engine
US3859973A (en) Timing device for fuel injector
US3058455A (en) Injection pump
US2810376A (en) Injection pump
US2937637A (en) Injection pump
US1993759A (en) Fuel injection pump
US4241714A (en) Solenoid valve controlled fuel injection pump
US2869529A (en) Injection pump assembly
US4052971A (en) Fuel injection pump and timing control therefor
US2697007A (en) Fuel injection device for internalcombustion engines
US3314406A (en) Liquid fuel pumping apparatus for internal combustion engines
JPH03264761A (ja) 自己着火式の内燃機関用の燃料噴射ポンプ
US2935062A (en) Injection pumps
US2005008A (en) Fuel injection pump
US2572118A (en) Fuel injector
US2059759A (en) Liquid fuel pressure regulator
US3267865A (en) Fuel injection pump
US3967612A (en) Lubricating oil pump for use in an internal combustion engine
US2503458A (en) Fuel injection pump
US3059579A (en) Regulating devices for reciprocating action pumps and in particular fuel injection pumps
US3123061A (en) figure
US2071237A (en) Fuel injector for diesel engines
US3507262A (en) Fuel injection system
US2462854A (en) Fuel injection system
US4509491A (en) Overflow valve for distributor-type fuel injection pumps