US2946287A - Self-regulating piston pumps, in particular fuel injection pumps for internal combustion engines - Google Patents

Self-regulating piston pumps, in particular fuel injection pumps for internal combustion engines Download PDF

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Publication number
US2946287A
US2946287A US788801A US78880159A US2946287A US 2946287 A US2946287 A US 2946287A US 788801 A US788801 A US 788801A US 78880159 A US78880159 A US 78880159A US 2946287 A US2946287 A US 2946287A
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piston
conduit
chamber
auxiliary
pumps
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US788801A
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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
    • 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
    • F02M59/32—Varying fuel delivery in quantity or timing fuel delivery being controlled by means of fuel-displaced auxiliary pistons, which effect injection
    • 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
    • F02M59/34—Varying fuel delivery in quantity or timing by throttling of passages to pumping elements or of overflow passages, e.g. throttling by means of a pressure-controlled sliding valve having liquid stop or abutment

Definitions

  • the present invention relates to self-regulating piston pumps, in particular to fuel injection pumps for internal combustion engines, which include a main piston reciprocable in a main cylinder in communication with a source of liquid, this piston being reciprocated at a rate the value of which constitutes the factor of regulation, an auxiliary piston reciprocable in an auxiliary cylinder divided by it into two chambers, the first of said chambers being connected with said main cylinder by a conduit provided with a check-valve opening toward said first chamber, whereby the outward strokes of the auxiliary chamber take place under the driving action of the liquid delivered by the main piston and cause liquid to be delivered from the second of said chambers, resilient means being provided for producing the return strokes of the auxiliary piston, while driving out liquid from said first chamber, at a flow rate limited by throttling means, through a transfer conduit leading to said second chamber, whereby, for speeds of operation exceeding a given value, the length of every return stroke of the auxiliary piston, and therefore
  • the object of the present invention is to provide a pump of this kind which is better adapted to meet the requirements of practice than those known up to the present time.
  • My invention is characterized by the fact that the auxiliary piston and cylinder include a portion of larger diameter on the side of the first chamber and a portion of smaller diameter on the side of the second chamber, whereby the amount of liquid delivered from the first chamber is greater than that capable of being received into the second chamber during every return stroke of the auxiliary piston, the above mentioned throttling means being provided in a discharge conduit branching off from said transfer conduit, for evacuating the excess of liquid.
  • Fig. 1 shows, in diagrammatic section, a pump made according to a first embodiment of the invention.
  • Fig. 2 shows a modification of a portion of the pump of Fig. l.
  • the pumps shown by the drawing are fuel injection pumps for use in particular with diesel engines.
  • the pump includes a main piston 11 reciprocable in a main cylinder 13 under the action of a cam 10 driven at a speed proportional to that of the engine to be fed by ice with a source of fuel for the feed of said fuel to cylin-' der 13.
  • An auxiliary piston 1, 3 is movable in an auxiliary cylinder which is divided by said piston into two chambers 2 and 4.
  • the first chamber 2 is connected with the main cylinder 13 of the pump through a conduit 15 provided with a check-valve 16 opening toward chamber 2.
  • the other chamber, 4, is provided with a delivery conduit 7, with the interposition of a check-valve 8, said delivery conduit 7 leading to the injector or injectors of the engine fed with fuel by the pump.
  • the auxiliary piston 1, 3 is subjected to the action of return means constituted by a spring 22 which tends'to reduce the volume of chamber 2.
  • auxiliary piston 1, 3 The outward (upward) strokes of auxiliary piston 1, 3 are effected under the thrust of the liquid delivered by piston 11 through conduit 15, Whereas the return strokes of said auxiliary piston 1, 3 are produced by spring 22.
  • a transfer conduit 5 extends between the two chambers 2 and 4 of the auxiliary cylinder during the return stroke of the auxiliary piston, valve means being provided to prevent the communication between these two chambers through said conduit during the outward stroke of said auxiliary piston.
  • auxiliary piston 1, 3 In order to limit the displacements of auxiliary piston 1, 3 during its outward stroke, there is provided a discharge conduit 17 which places chamber 2 in communication with the outside after the lower edge of the auxiliary piston has cleared said discharge conduit.
  • abutment 2a On the other hand, the return strokes of the auxiliary piston are limited by an abutment 2a.
  • the auxiliary piston 1, 3 is made in the form of a stepped piston, its portion 1 of larger diameter (D) being on the side of the first chamher 2 and its portion of smaller diameter (d) being on the side ofthe second chamber 4.
  • the corresponding portions of the auxiliary cylinder are made of corresponding diameters, respectively.
  • the discharge conduit 9 might be connected as well to chamber 2 as to chamber 4, but it seems more advantageous to connect it with transfer conduit 5 as shown by Fig. 1.
  • spring 22 is constituted with a helical spring surrounding the portion 3 of small diameter of the auxiliary piston and bearing upon the end face of the portion 1 of larger diameter.
  • valve means are constituted by a double slide valve 18moving in a cylindrical housing 19 through which pass the respective portions of conduit 5 located respectively upstream and downstream of conduit 9 and this slide valve is actuated in one direction by the pressure existing in cylinder 13, for ing stance through the intermediate of a conduit 20, and
  • slide valve 18 into two elementary slide valves each comprising one'of the grooves 18a and 18b and. individually controlled in the same manner as the double slide valve 18. It would also be possible to have one of the grooves 18a and 18b cooperating with only one of the portions of conduit 5 and the other one with conduit 9. I might also provide a check-valve at the inlet of chamber 4 and a slide valve between chamber 2 and discharge conduit 9.
  • throttling means 23 which form a passage of restricted cross-section 6 in conduit 9, it is advantageous to make them adjustable.
  • such means are preferably constituted by a screw adapted to be adjusted eithermanually (as shown by Fig. l), or automatically under the action of a governor, i.e. a centrifugal or another governor, responsive tovariations of the speed at which the pump is being driven.
  • governor includes a piston 24 reciprocable in a cylinder 25 and subjected in one direction to the action of a pressure which increases when the speed of the engine increases and in the other direction to the action of a return spring 26.
  • Piston 24 carries a rack 27 in mesh with a pinion 2.3a fixed to the upper end of screw 23.
  • screw 23 In the embodiment shown by Fig. 2, where the rack is located behind pinion 23a and moves from the right toward the left when the speed increases, screw 23 must have a left handed thread so that said displacement decreases the area of the throttled passage '6.
  • the pressure acting upon piston 24 is supplied by a pump 28, for instance a gear pump, driven at a speed proportional to that of the engine suppiied with fuel by the pump and the delivery of which is connected with a conduit 29 provided with a throttled passage 3i
  • a pump 28 for instance a gear pump
  • the throttled passage is advantageously constituted by the, groove 31% of a slide valve 31 moving transversely to a portion of conduit 29, said slide valve 31 being subjected to.
  • piston 11 When piston 11 is in the position shown by the drawing, its cylinder 13 is filled with fuel flowing in through conduit 14. Then piston 11 moves upwardly and closes the opening 12 of conduit 14. This causes the fuel present in cylinder 13 to be driven out therefrom.
  • First slide valve 18 is moved upwardly closing both branches of transfer conduit 5, then piston 1, 3 is driven upwardly against the action of spring '22, until discharge conduit 17 is opened. During this movement, chamber 2 is filled with liquid.
  • the portion 3 of the auxiliary piston causes liquid to be delivered, through conduit 7, toward the injector or injectors of the engine. As soon as discharge conduit 17 is opened, piston 1, 3 stops whereas piston 11 keeps moving upwardly.
  • check-valve 16 closes and the grooves 18a and 18b -the flow toward the outside of the difference between the volumes displaced respectively by the portions 1 and 3 of the auxiliary piston, which causes a braking of the downward movement of said'piston.
  • Spring 22 is chosen relatively Weak so that, in view of the small cross-sectional area of the throttled passage 6, the time taken by piston 1", 3. to reach its abutment 2a exceeds, for speeds of operation of the pump above a given value, the time elapsing between the end of the upward movement of piston 11 and the beginning of the next upward movement thereof. Consequently, if the speed of the engine increases, there happens a time where the portion 1 of the auxiliary piston isstruck by the fresh fuel delivered by piston 11 moving upwardly, before said piston 1, 3 has reached its abutment 2a, which reduces the return stroke of the auxiliary piston and therefore the volume delivered by the portion 3 of this piston during the next cycle of the pump. The length of this return stroke is the shorter as the speed of the pump is higher.
  • This regulating elfect may be combined with that due to the variable throttling means 23 controlled by a governor such as that shown by Fig. 2, which is capable of reducing the speed of the downward movement of the auxiliary piston as the speed of operation of the pump increases.
  • a self-regulating reciprocating action pump which comprises, in combination, a main cylinder, a main piston reciprocable in said cylinder, an auxiliary cylinder rigid with the first one, one end of said auxiliary cylinder being in communication with the delivery end of said main cylinder, an auxiliary piston reciprocable in said auxiliary cylinder, said auxiliary cylinder being divided by said auxiliary piston into two chambers, to wit a first chamber located at said above mentioned end of said auxiliary cylinder and a second chamber located at the other end of said auxiliary cylinder, at liquid delivery conduit leading out from said second chamber, a check-valve interposed between said main cylinder and said first chamber of said auxiliary cylinder to prevent liquid from flowing back from said first chamber to said main cylinder, resilient means interposed between said auxiliary cylinder and said auxiliary piston for exerting on said auxiliary piston a return force opposed to that exerted thereon by the liquid pressure from said main cylinder during the delivery stroke of said main piston, a transfer conduit leading from said first chamber to said second chamber, valve means in, said transfer

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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)
US788801A 1958-01-28 1959-01-26 Self-regulating piston pumps, in particular fuel injection pumps for internal combustion engines Expired - Lifetime US2946287A (en)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
FR1139325X 1958-01-28

Publications (1)

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US2946287A true US2946287A (en) 1960-07-26

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ID=9641663

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US788801A Expired - Lifetime US2946287A (en) 1958-01-28 1959-01-26 Self-regulating piston pumps, in particular fuel injection pumps for internal combustion engines

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US (1) US2946287A (fr)
CH (1) CH350502A (fr)
DE (1) DE1139325B (fr)
FR (1) FR1197989A (fr)
GB (1) GB850151A (fr)

Cited By (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3016835A (en) * 1958-01-28 1962-01-16 Bessiere Pierre Etienne Self-regulating reciprocating action pumps
US3174432A (en) * 1960-08-12 1965-03-23 Eickmann Karl Combustion engine for conveying a hydraulic pressure medium
US3269321A (en) * 1961-08-01 1966-08-30 Eickmann Karl Combustion engine for conveying a hydraulic pressure medium
US4293286A (en) * 1979-01-22 1981-10-06 Hawkins Joel W Double action pump

Families Citing this family (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR2480356A1 (fr) * 1980-04-14 1981-10-16 Lucas Industries Ltd Appareil de pompage et d'injection de combustible
AT392122B (de) * 1981-12-23 1991-01-25 List Hans Kraftstoffeinspritzpumpe fuer brennkraftmaschinen

Citations (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2281045A (en) * 1936-02-19 1942-04-28 Prec Mecanique Soc Pump

Family Cites Families (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB782844A (en) * 1955-01-03 1957-09-11 Cav Ltd Liquid fuel pumps for internal combustion engines

Patent Citations (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2281045A (en) * 1936-02-19 1942-04-28 Prec Mecanique Soc Pump

Cited By (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3016835A (en) * 1958-01-28 1962-01-16 Bessiere Pierre Etienne Self-regulating reciprocating action pumps
US3174432A (en) * 1960-08-12 1965-03-23 Eickmann Karl Combustion engine for conveying a hydraulic pressure medium
US3269321A (en) * 1961-08-01 1966-08-30 Eickmann Karl Combustion engine for conveying a hydraulic pressure medium
US4293286A (en) * 1979-01-22 1981-10-06 Hawkins Joel W Double action pump

Also Published As

Publication number Publication date
FR1197989A (fr) 1959-12-03
DE1139325B (de) 1962-11-08
CH350502A (fr) 1960-11-30
GB850151A (en) 1960-09-28

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