US3908619A - Fuel injection pumps for internal combustion engines - Google Patents

Fuel injection pumps for internal combustion engines Download PDF

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Publication number
US3908619A
US3908619A US364543A US51153274A US3908619A US 3908619 A US3908619 A US 3908619A US 364543 A US364543 A US 364543A US 51153274 A US51153274 A US 51153274A US 3908619 A US3908619 A US 3908619A
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US
United States
Prior art keywords
chamber
intake
pump
exhaust
exhaust pipe
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
US364543A
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English (en)
Inventor
Hans Bittelmeyer
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
Honda Motor Co Ltd
Original Assignee
Robert Bosch GmbH
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Filing date
Publication date
Application filed by Robert Bosch GmbH filed Critical Robert Bosch GmbH
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Publication of US3908619A publication Critical patent/US3908619A/en
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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
    • F02M41/126—Variably-timed valves controlling fuel passages valves being mechanically or electrically adjustable sleeves slidably mounted on rotary piston

Definitions

  • a fuel injection pump mechanism employing a simul- Oct. 3, 1973 Germany 23495810 taneously reciprocating and rotating metering piston is provided with relief channels which permit the S- 123/139 139 139 AL equalization of the residual pressures in the various, [51] Int. Cl.2 F02M 39/00 sequentially addressed fuel delivery lines leading to 1 Fie fSearCh... 123/139 R, 13 F, the engine cylinders.
  • the pump 123/13 13 E 1 139 AL piston is provided with a partial annular groove which connects the idle fuel delivery channels with one [5 6] References Cited another.
  • a longitudinal groove further connects UNITED STATES P TENT these channels to the working pressure chamber of 2,784,670 3/1957 High et al 123/ 139 BD the fuel lnlectlon Pump- 3,194,225 7/1965 Kemp 123/139 R 1 Claim, 3 Drawing Figures US. Patent Sept. 30,1975
  • the invention relates to a fuel injection pump for internal combustion engines, and more particularly to a fuel injection pump for internal combustion engines having a metering piston which simultaneously rotates and reciprocates within a pump cylinder and which, during its rotation, sequentially connects a fuel distributing aperture located on the periphery of the pump cylinder with delivery channels terminating about the circumference of the pump cylinder.
  • the fuel delivery channels lead to the individual cylin' ders of the internal combustion engine.
  • the pump piston is equipped with a partial annular groove through which at least two of the delivery channels communicate with one another while fuel delivery takes place through one of the other delivery channels.
  • a connecting channel is provided as a longitudinal channel within the pump which leads from the pump working chamber and terminates in a longitudinal fuel distributing groove.
  • this groove sequentially communicates with one of the delivery channels disposed about the circumference of the pump cylinder.
  • a majority of the remaining delivery channels is in mutual communication due to a partial annular groove disposed on the periphery of the pump piston in 'the same plane as the longitudinal distributing groove.
  • the presence of the partial annular groove keeps the residual pressure in the individual delivery channels constant and a spread of the magnitudes of the injected fuel quantities is prevented.
  • the connecting channel within the pump piston constantly communicates with the working chamber of the pump and cannot be closed off, so that a spread of the magnitudes of the injected fuel quantity, due to different levels of the residual pressure, cannot occur.
  • This object is achieved, according to the invention, by embodying the distributing aperture as a longitudinal distributing groove extending from an annular groove in the periphery of the pump piston, and by embodying the connecting channel as a channel extending within the pump housing, with a check valve being located where the connecting channel exits from the pump working chamber.
  • This connecting channel has a first outletaperture in the pump cylinder, located in the vicinity of the effective region of the annular groove in the piston.
  • the connecting channel also has a second outlet aperture leading into the pump cylinder which may be opened during the suction stroke of the piston by one or several longitudinal grooves distributed around the pump piston periphery and corresponding in number to the number of fuel distributing channels.
  • One of the longitudinal grooves extends to and terminates in the partial annular groove.
  • FIG. 1 is a longitudinal view, partly in cross section, through a schematic representation of the injection pump according to the invention
  • FIG. 2 is a section through the injection pump depicted in FIG. 1, taken along the plane IIII;
  • FIG. 3 is a section through the injection pump according to FIG. 1, taken along the plane III-III.
  • a housing 1 of a fuel injection pump includes a pump cylinder 4 formed by a bushing 3, fixedly inserted into the housing of the fuel injection pump.
  • a pump piston 2 driven by means (not shown) in such a way that it simultaneously executes an axial reciprocating motion and a rotational motion about its longitudinal axis. Due to its rotational motion, the piston 2 serves 'as a fuel distributor in that, during its pressure stroke, it delivers the fuel sequentially to individual delivery channels 5 which are spaced uniformly about the pump cylinder 4.
  • the delivery channels 5 lead to the fuel injection valves of the engine (not shown) and are present in the same number as there are cylinders in the internal combustion engine to be supplied with fuel.
  • the cylinder 4 and the face of the pump piston 2 together define a pump working chamber 6 which is supplied with fuel during the time that the pump piston 2 executes its suction stroke or occupies its bottom dead center position.
  • This fuel is admitted from a pump suction chamber 9 through a supply channel 8 and through longitudinal recesses 7.
  • the number of longitudinal recesses 7 is the same as the number of delivery channels 5 located around the periphery of the pump piston 2; these recesses terminate in the pump working chamber 6.
  • a fuel pump 11 delivers fuel from a fuel tank 12 to to the pump suction chamber 9.
  • a pressure control valve 13 controls the pressure within the suction chamber 9, in a known manner, so that the pressure in the suction chamber increases with increasing rpm.
  • a bore 15 leads from the pump working chamber 6 to a chamber 16.
  • a connecting channel 21 extends from the chamber 16, parallel to the axis of the pump within the bushing 3 and has a first outlet aperture 22 and a second outlet aperture 23, both of which terminate in the wall of the pump cylinder 4.
  • the first outlet aperture 22 is located within the effective working region of an annular groove 25 disposed on the periphery of the pump piston 2 and communicates with this groove during the entire delivery stroke of the pump piston.
  • a longitudinal distributing groove 26 also communicates with the annular groove 25 and, when the pump piston is rotated during its delivery stroke, the longitudinal distributing groove 26 sequentially communicates with one of the several delivery channels 5 terminat ing in the pump cylinder 4.
  • the opening of the second outlet aperture 23 is controlled by longitudinal grooves 27 disposed in the periphery of the pump piston, whose number is equal to the number of fuel distributing channels.
  • the longitudinal grooves 27 are in mutual communication by means of an annular groove 28 disposed on the pump piston.
  • One of the longitudinal grooves 27 is embodied as an extended connecting groove 30 which connects the annular groove 28 with a partial annular groove 31 disposed on the pump piston.
  • the partial annular groove 21 is located in the region of the termini of the delivery channels 5 and remains in communication with several different ones of these delivery channels 5 during the reciprocating motion of pump piston 2, but, as may be seen by comparing FIGS. 2 and 3, it has no communication to that particular delivery channel which is, at any one time, communicating with the longitudinal distributing groove 26.
  • the pump piston 2 also includes a longitudinal channel 33, starting at the pump working chamber 6 and embodied as a blind bore which communicates with the suction chamber 9 through a transverse bore 34 located in that part of the pump piston extending into the suction chamber.
  • the terminus of the transverse bore 34 in the pump piston can be opened and closed by an annular slide 35, slidably and sealingly disposed on the pump piston.
  • the annular slide 35 is displaced by an intermediate lever 37 which pivots about a pivotal axis 38 under the control of an rpm regulator (not shown), depending on the rpm and the load of the engine.
  • the intermediate lever is provided with a spherical head 39 which engages a recess 40 in the annular slide 35.
  • the method of operation of the injection pump according to the invention is as follows: during the downward motion of the pump piston 2, i.e. during its suction stroke, the pump piston draws fuel through longitudinal grooves 7 and the supply channel 8 into the pump working chamber 6. The rotation of the pump piston then interrupts the communication to the supply channel 8 so that, during the upward motion, i.e. during the delivery stroke of the piston, fuel is delivered from the working chamber 6 through the check valve 19 into the chamber 16 for as long as the transverse bore 34 is obturated by the control slide 35. Fuel flows from chamber 16 through the connecting channel 21 and through the first outlet aperture 22 into the annular groove 25 on the pump piston. Thence, the fuel flows through the longitudinal distributing groove 26 into one of the delivery channels 5.
  • the longitudinal distributing groove 26 communicates with one of the delivery channels 5 whereas the remaining delivery channels, as may be seen in FIG. 3, communicate with one another via the partial annular groove 31. If the distributing groove 26 were to close off the various delivery channels at different pressure levels, different residual pressures would then prevail in the several delivery channels 5. This would result in different quantities of fuel being delivered to the channels in subsequent cycles because, in each case, a certain amount of fuel is required in order to equalize the pressure difference at the onset of each delivery stroke. In the present case, however, several delivery channels are in mutual communication via the partial annular groove 31 for the purpose of equalizing their residual pressures and preventing such pressure differences.
  • the second outlet aperture 23 is opened by one of the longitudinal grooves 27.
  • a communication is created between the chamber 16 and the partial annular groove 31, namely through connecting channel 21, the longitudinal groove 27, the annular groove 28 and the connecting groove 30.
  • both a majority of the delivery channels as well as the connecting channel 21 and the chamber 16 can be placed in mutual communication for the purpose of pressure equalization. It may be seen from FIGS. 2 and 3 that, when one of the longitudinal grooves 27 communicates with the second outlet aperture 23 of the connecting channel 21, then the longitudinal distributing groove 26 is closed off, i.e. does not communicate with any distribution channel 5.
  • the result of this arrangement is that, at the beginning of fuel delivery into one of the delivery into one of the delivery channels, the pressure in that channel is the same as that in the connecting channel 21 and, thus, variations or a quantitative spread of the magnitudes of the delivered fuel quantities due to different residual pressure levels is reliably prevented.
  • a fuel injection pump for internal combustion engines comprising! a. a housing including a plurality of fuel delivery channels formed therein;
  • a cylindrical bushing with a central bore, said .bushing being contained within the housing and provided with an internal connecting channel having a first outlet aperture and a second outlet aperture, and a plurality of radial channels communicating with said fuel delivery channels in said housing;
  • a pump piston slidingly disposed within the central bore of said bushing so as to be capable of simultaneous rotational and reciprocating motion, said pump piston including:

Landscapes

  • Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Fuel-Injection Apparatus (AREA)
US364543A 1973-10-03 1974-10-03 Fuel injection pumps for internal combustion engines Expired - Lifetime US3908619A (en)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
DE2349581A DE2349581C2 (de) 1973-10-03 1973-10-03 Kraftstoffverteilereinspritzpumpe für Brennkraftmaschinen

Publications (1)

Publication Number Publication Date
US3908619A true US3908619A (en) 1975-09-30

Family

ID=5894366

Family Applications (1)

Application Number Title Priority Date Filing Date
US364543A Expired - Lifetime US3908619A (en) 1973-10-03 1974-10-03 Fuel injection pumps for internal combustion engines

Country Status (8)

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US (1) US3908619A (es)
JP (1) JPS5744820B2 (es)
AR (1) AR200220A1 (es)
CS (1) CS169777B2 (es)
DE (1) DE2349581C2 (es)
FR (1) FR2246744B1 (es)
GB (1) GB1483906A (es)
IT (1) IT1022518B (es)

Cited By (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4059369A (en) * 1975-01-28 1977-11-22 Robert Bosch G.M.B.H. Fuel injection pump
US4112902A (en) * 1975-08-09 1978-09-12 Talleres Diesel, S.A. Hydraulic speed control systems for internal combustion engines
US4229148A (en) * 1978-12-22 1980-10-21 Ambac Industries, Incorporated Fuel injection pump
US4233002A (en) * 1978-05-09 1980-11-11 Benjamin Birenbaum Fuel injection system
US4463726A (en) * 1980-12-29 1984-08-07 Spica S.P.A. Distributor pump for injecting fuel into internal combustion engines
US4788959A (en) * 1984-11-06 1988-12-06 Nissan Motor Company, Limited Fuel injection pump
US5127381A (en) * 1988-12-22 1992-07-07 Robert Bosch Gmbh Fuel injection pump for internal combustion engines
EP0846856A3 (en) * 1991-07-16 2002-07-17 Stanadyne Automotive Corp. Fuel system for rotary distributor fuel injection pump
CN105525989A (zh) * 2016-01-26 2016-04-27 江苏盛源燃气动力机械有限公司 一种使用天然气的车用双燃料系统

Families Citing this family (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
ES477347A1 (es) * 1978-03-21 1979-10-16 Lucas Industries Ltd Sistema de combustible para un motor de combustion interna policilindrico.
JPS603981Y2 (ja) * 1979-04-05 1985-02-04 株式会社ボッシュオートモーティブ システム 分配型燃料噴射ポンプ
JPS5627060A (en) * 1979-08-08 1981-03-16 Toyota Motor Corp Fuel injection controller for internal combustion engine
JPH05272429A (ja) * 1992-03-25 1993-10-19 Mitsubishi Motors Corp 燃料噴射装置
CN114688560B (zh) * 2022-03-09 2023-06-16 中国联合重型燃气轮机技术有限公司 分级燃烧室掺混器

Citations (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US1342159A (en) * 1918-10-30 1920-06-01 Donald K Champaign Intake-manifold
US1670550A (en) * 1924-11-11 1928-05-22 James B Putnam Combined intake and exhaust manifold
US1744319A (en) * 1926-12-18 1930-01-21 Studebaker Corp Internal-combustion engine
US2232413A (en) * 1939-03-30 1941-02-18 Steskal Rudolph Internal combustion engine
US2821182A (en) * 1955-06-07 1958-01-28 Gen Motors Corp Throttle riser heat applicator means
US3543736A (en) * 1967-11-18 1970-12-01 Toyoda Chuo Kenkyusho Kk Internal combustion engine with subcombustion chamber
US3741180A (en) * 1971-04-09 1973-06-26 B Eichbaum Apparatus for vaporizing a fuel air mixture in the induction system of an combustion engine
US3780715A (en) * 1972-11-30 1973-12-25 Gen Motors Corp Early fuel evaporation intake manifold

Family Cites Families (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CH349124A (de) * 1956-05-30 1960-09-30 Cav Ltd Brennstoffeinspritzpumpe
DE2142704C3 (de) * 1971-08-26 1974-04-25 Robert Bosch Gmbh, 7000 Stuttgart Kraftstoffeinspritzpumpe für mehrzylindrige Brennkraftmaschinen

Patent Citations (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US1342159A (en) * 1918-10-30 1920-06-01 Donald K Champaign Intake-manifold
US1670550A (en) * 1924-11-11 1928-05-22 James B Putnam Combined intake and exhaust manifold
US1744319A (en) * 1926-12-18 1930-01-21 Studebaker Corp Internal-combustion engine
US2232413A (en) * 1939-03-30 1941-02-18 Steskal Rudolph Internal combustion engine
US2821182A (en) * 1955-06-07 1958-01-28 Gen Motors Corp Throttle riser heat applicator means
US3543736A (en) * 1967-11-18 1970-12-01 Toyoda Chuo Kenkyusho Kk Internal combustion engine with subcombustion chamber
US3741180A (en) * 1971-04-09 1973-06-26 B Eichbaum Apparatus for vaporizing a fuel air mixture in the induction system of an combustion engine
US3780715A (en) * 1972-11-30 1973-12-25 Gen Motors Corp Early fuel evaporation intake manifold

Cited By (10)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4059369A (en) * 1975-01-28 1977-11-22 Robert Bosch G.M.B.H. Fuel injection pump
US4112902A (en) * 1975-08-09 1978-09-12 Talleres Diesel, S.A. Hydraulic speed control systems for internal combustion engines
US4233002A (en) * 1978-05-09 1980-11-11 Benjamin Birenbaum Fuel injection system
US4229148A (en) * 1978-12-22 1980-10-21 Ambac Industries, Incorporated Fuel injection pump
US4463726A (en) * 1980-12-29 1984-08-07 Spica S.P.A. Distributor pump for injecting fuel into internal combustion engines
US4788959A (en) * 1984-11-06 1988-12-06 Nissan Motor Company, Limited Fuel injection pump
US5127381A (en) * 1988-12-22 1992-07-07 Robert Bosch Gmbh Fuel injection pump for internal combustion engines
EP0846856A3 (en) * 1991-07-16 2002-07-17 Stanadyne Automotive Corp. Fuel system for rotary distributor fuel injection pump
CN105525989A (zh) * 2016-01-26 2016-04-27 江苏盛源燃气动力机械有限公司 一种使用天然气的车用双燃料系统
CN105525989B (zh) * 2016-01-26 2018-01-12 江苏盛源燃气动力机械有限公司 一种使用天然气的车用双燃料系统

Also Published As

Publication number Publication date
DE2349581A1 (de) 1975-04-10
AR200220A1 (es) 1974-10-24
CS169777B2 (es) 1976-07-29
FR2246744B1 (es) 1978-09-15
DE2349581C2 (de) 1983-10-13
IT1022518B (it) 1978-04-20
JPS5061517A (es) 1975-05-27
JPS5744820B2 (es) 1982-09-24
FR2246744A1 (es) 1975-05-02
GB1483906A (en) 1977-08-24

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