US3759235A - Injection devices for internal combustion engines - Google Patents

Injection devices for internal combustion engines Download PDF

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Publication number
US3759235A
US3759235A US00204442A US3759235DA US3759235A US 3759235 A US3759235 A US 3759235A US 00204442 A US00204442 A US 00204442A US 3759235D A US3759235D A US 3759235DA US 3759235 A US3759235 A US 3759235A
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United States
Prior art keywords
valve
cylinder
chamber
pump
passage
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Expired - Lifetime
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US00204442A
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English (en)
Inventor
A Vuaille
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Sigma
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Sigma
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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
    • 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
    • F02M59/44—Details, components parts, or accessories not provided for in, or of interest apart from, the apparatus of groups F02M59/02 - F02M59/42; Pumps having transducers, e.g. to measure displacement of pump rack or piston
    • F02M59/46—Valves
    • F02M59/462—Delivery valves
    • 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
    • F02M2700/13—Special devices for making an explosive mixture; Fuel pumps
    • F02M2700/1317—Fuel pumpo for internal combustion engines

Definitions

  • the invention relates to injection devices, for internal combustion engines, which comprise, immediately downstream of each cylinder of an injection pump wherein a piston moves, a delivery and reaspirating valve biased by a spring and adapted to open, on one hand, during the active portion of the delivery stroke of the piston to allow the liquid fuel to arrive from'the cylinder pump at an injector by means of a linking passage and, on the other hand, when the difference in pressures between the linking passage and the cylinder of the pump exceeds a given limit, to allow the fuel to flow back towards this cylinder, which valve cooperates, on one hand, through a terminal sealing collar, with a seat arranged between the cylinder of the pump and an annular chamber connected permanently to the linking passage, said collar and seat being in contact through an annular zone when the valve is closed, and, on the other hand, through a cylindrical portion of greater diameter than the maximum diameter of the said annular zone, with a cylindrical guide bore
  • the delivery valve is arranged as a reaspirating valve (or relief valve) to allow the fuel to flow back under the effect of the reflected pressure wave.
  • the delivery and reaspirating valve thus opens, on the arrival of the pressure wave, under the efiect of the pressure existing on the abovesaid annular chamber and which exerts, in the sense of opening, over a surface equivalent to the difference between the crosssection of the abovesaid cylindrical portion of the valve and the surface of the circle having for diameter the maximum diameter defined above.
  • the calibration of the abovesaid spring is such that the delivery and reaspirating valve closes again in time to allow the persistance, in the linking passage, of a sufficient pressure at the end of an injection period for the injector to be able to reopen without delay at the beginning of the subsequent injection period.
  • the delivery and reaspirating valve comprises, in addition, a second cylindrical portion which is arranged with a slight spacing in the abovesaid bore, which is closed beyond this second cylindrical portion to constitute a fuel chamber, linking means being provided to connect this chamber to the suction side of the pump as long as the separation between the valve and its seat has not exceeded a predetermined value.
  • FIGS. 1 and 2 show in diagrammatic axial section, the essential elements of an injection device constructed according to the invention, In the positions corresponding respectively to the bottom dead center and to the top dead center of the pump piston;
  • FIG. 3 shows on a larger scale a detail of this embodiment.
  • the injection device as a whole, it is constructed in any way such that it comprises, downstream (the direction of flow being shown diagrammatically by the arrows of FIG. 2) of each cylinder 1 of an injection pump 2 wherein a piston 3 moves, on one hand, a delivery valve 4 biased by a spring 5 and adapted to open during the active portion of the delivery stroke of the piston 3 to allow liquid fuel to arrive at an injector (not shown) by means of a linking passage 6 and, on the other hand, reaspirating means situated between the said passage 6 and the pump cylinder l and adapted to allow the fuel to flow back towards the said cylinder 1 when the difierence of pressures between the passage 6 and the cylinder 1 exceeds a given limit.
  • the cylinder 1 is housed inside a sleeve 7 with which it defines an annular supply chamber 8.
  • This chamber receives fuel from a supply pump (not shown) and can communicate with the delivery chamber 9, which is bounded by the piston 3 in the cylinder 1, by p o r t s 10 which are obturated by the said piston when the latter has travelled from the beginning of its delivery stroke, to a position intermediate between those of FIGS. 1 and 2.
  • the ports B0 are obturated, the fuel imprisioned in the chamber 9 is delivered towards the injector which it reaches by passing through passage 6 after having lifted the delivery valve 4 against the effect of its spring 5.
  • the end of the active portion of the delivery stroke of the piston 3 corresponds to the moment when the latter connects the delivery chamber 9 to the supply chamber 8 by means of ports 10 and a passage arranged in the piston and bounded by a ramp 11, the rotation of the piston on itself enabling the volume of fuel injected per cycle to be regulated.
  • the abovesaid reaspirating means are constituted by the delivery valve 4 itself which, at this end, cooperates on one hand, through a terminal sealing collar 40, with a seat 12 arranged between the pump cylinder 1 and an annular chamber 13 permanently connected to the linking passage 6, the said collar 4a and the seat 12 being in contact through an annular zone (limited by two circles indicated by dot-dash lines in FIG. 3, namely a circle of large diameter D and a circle of small diameter d) when the valve 4 is closed and, on the other hand, by a cylindrical portion 4b of diameter D, greater than the maximum diameter D of the said annular zone with a cylindrical guide bore 14 in which this portion 4b slides with fluid-tightness.
  • the single valve 4 comprises in addition a second intermediate cylindrical portion 4c which is arranged with slight spacing a in the bore 14, which is closed beyond the valve by a transverse wall 15 to constitute a fuel chamber 16.
  • Linking means are also provided to connect this chamber 16 to the supply chamber 8 of the pump as long as the separation between the valve 4 and its seat 12 has not exceeded a predetermined value.
  • these linking means are constituted by a groove 17, arranged around the valve 4 against its cylindrical portion 4c, which is connected permanently to the chamber 16 by a passage channel 18 traversing the top of the valve 4 and which communicates, in the first part of the lifting stroke of this valve, with a channel 19 permanently connected to the supply chamber 8.
  • the bore 14 and the chamber 16 are preferably ar-' ranged in a single part 20 housed inside a tubular connector 21 on which the passage 6 is formed.
  • the part 20 can be supported on the connector 21 by the cylinder 1 which is held by-a shoulder 7a on the sleeve 7, the sleeve 7 and the connector 21 being in their turn as Sild by screwing together by means of threads 22.
  • the annular chamber 13 is defined externally by a groove 23, arranged in the part 20, and communicates with the central passage of the connector 21 through at least one passage 24 also formed in the part 20.
  • the transverse wall 15 is constituted by the terminal surface of a threaded plug 25, screwed into the part 20 and serving as adjustable support for the spring 5.
  • the channel 19 traverses the part 20 radially and opens externally into an annular space 26 left free between the outer wall of the part 20 and the inner wall of the connector 21.
  • the piston 3 In the course of its upward movement, the piston 3 reaches a position when it starts to connect the delivery chamber 9 to the supply chamber 8 through its ramp passage 11 and ports 10.
  • the placing in communication of the delivery chamber 9 with the supply chamber 8, which is at moderate pressure, -causes the closing not only of the injector placed at the end of the passage 6, which creates a pressure wave in this passage towards the pump 2, but also of the valve 4 which is opposed to the propagation of this pressure wave.
  • This wave is manifested, in the annular chamber 13, by an increase of the pressure which, in acting on the valve a through an annular surface limited by circles of diameters I) and 1),, causes possibly the opening of this valve against the effect of the spring 5, as shown in H6. 2.
  • the valve 4 In the two successive opening movements (injection and attentuation of the reflected pressure wave), the valve 4 is moved firstly rapidly thereby overcoming the resistance of the spring 5, since the liquid contained in the chamber 16 can escape freely through the channel 18, the groove 17 and the channel 19 towards the supply chamber 8. Then, when the separation between the valve 4 and its seat 12 exceeds a predetermined value, the movement of the valve is damped due to the fact that the liquid contained in the chamber 16 can no longer escape except through the small spacing 4 existing between its cylindrical portion 40 and the bore 14. Similarly, the closing movement is firstly slowed by the reintroduction of the liquid into the chamber 16 through the spacing a, then un-slowed.
  • the opening of the valve 4 is free, which enables the beginning of the injection to be effected normally, and its closing is equally free, which ensures a clean cut-off of the injection.
  • the rest of the movement of the valve is damped, which offers as an advan-- tage a control of the speed of the valve 4 at the moment it contacts, at the end of its stroke, the transverse wall 15.
  • Injection device for an internal combustion engine, which comprises an injection pump having a cylinder wherein a piston moves, and immediately downstream of said cylinder a delivery and reaspirating valve biased by a spring and adapted to open, on one hand, on the active portion of the delivery stroke of the piston to allow liquid fuel to arrive from the cylinder to an injector through a linking passage and, on the other hand, when the difference in pressures between the linking passage and the cylinder of the pump exceeds a given limit, to allow the fuel to flow back towards the cylinder, for which purpose said valve cooperates, on one hand, through a terminal sealing collar with a seat arranged between the cylinder and an annular chamber connected permanently to the linking passage, said collar and seat being in contact through an annular zone when the valve is closed, and, on the other hand, through a cylindrical portion of greater diameter than the maximum diameter of the said annular zone, with a cylindrical guide bore in which this cylindrical portion slides with fluid-tightness, the valve comprising, in addition, a second cylindrical portion which is arranged with slight
  • Injection device wherein the single part is supported on the connector by the cylinder which is held by a shoulder forming part of a sleeve, the sleeve and the connector being in their turn assembled by screwing by means of threads, and the sleeve bounding an annular supply chamber around the pump cylinder.

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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)
US00204442A 1970-12-04 1971-12-03 Injection devices for internal combustion engines Expired - Lifetime US3759235A (en)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
FR7043751A FR2116728A5 (enrdf_load_stackoverflow) 1970-12-04 1970-12-04

Publications (1)

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US3759235A true US3759235A (en) 1973-09-18

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Application Number Title Priority Date Filing Date
US00204442A Expired - Lifetime US3759235A (en) 1970-12-04 1971-12-03 Injection devices for internal combustion engines

Country Status (4)

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US (1) US3759235A (enrdf_load_stackoverflow)
DE (1) DE2159356C2 (enrdf_load_stackoverflow)
FR (1) FR2116728A5 (enrdf_load_stackoverflow)
GB (1) GB1367337A (enrdf_load_stackoverflow)

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3965876A (en) * 1973-12-13 1976-06-29 Sigma Diesel Fuel injection pumps for internal combustion engines
US6116217A (en) * 1998-09-29 2000-09-12 Stanadyne Automotive Corp. Full authority rail pressure-reduction valve

Families Citing this family (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
AT407429B (de) * 1986-04-01 2001-03-26 Friedmann & Maier Ag Einspritzpumpe für brennkraftmaschinen
DE4008071A1 (de) * 1990-03-14 1991-09-19 Kloeckner Humboldt Deutz Ag Kraftstoffeinspritzpumpe
DE4022226A1 (de) * 1990-07-12 1992-01-16 Man Nutzfahrzeuge Ag Brennstoffeinspritzvorrichtung fuer luftverdichtende brennkraftmaschinen

Citations (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2628570A (en) * 1946-04-26 1953-02-17 American Bosch Corp Fuel injection device
US3117524A (en) * 1959-10-20 1964-01-14 Weatherhead Co Pump damping means

Family Cites Families (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
AT169225B (de) * 1947-11-27 1951-10-25 Anton Dipl Ing Dr T Pischinger Brennstoffeinspritzpumpe für Einspritzbrennkraftmaschinen
DE865404C (de) * 1951-05-27 1953-02-02 Bosch Gmbh Robert Druckventil fuer Kraftstoffeinspritzpumpen
NL125952C (enrdf_load_stackoverflow) * 1964-04-21

Patent Citations (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2628570A (en) * 1946-04-26 1953-02-17 American Bosch Corp Fuel injection device
US3117524A (en) * 1959-10-20 1964-01-14 Weatherhead Co Pump damping means

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3965876A (en) * 1973-12-13 1976-06-29 Sigma Diesel Fuel injection pumps for internal combustion engines
US6116217A (en) * 1998-09-29 2000-09-12 Stanadyne Automotive Corp. Full authority rail pressure-reduction valve

Also Published As

Publication number Publication date
GB1367337A (en) 1974-09-18
FR2116728A5 (enrdf_load_stackoverflow) 1972-07-21
DE2159356A1 (de) 1972-06-22
DE2159356C2 (de) 1984-05-24

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