US3444849A - Hydraulic regulator particularly for fuel injection pumps of internal combustion engines - Google Patents

Hydraulic regulator particularly for fuel injection pumps of internal combustion engines Download PDF

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Publication number
US3444849A
US3444849A US693885A US3444849DA US3444849A US 3444849 A US3444849 A US 3444849A US 693885 A US693885 A US 693885A US 3444849D A US3444849D A US 3444849DA US 3444849 A US3444849 A US 3444849A
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United States
Prior art keywords
accumulator
control element
piston
chamber
conduit
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
US693885A
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English (en)
Inventor
Pierre Etienne Bessiere
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Robert Bosch GmbH
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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 US3444849A publication Critical patent/US3444849A/en
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Classifications

    • G—PHYSICS
    • G05—CONTROLLING; REGULATING
    • G05D—SYSTEMS FOR CONTROLLING OR REGULATING NON-ELECTRIC VARIABLES
    • G05D13/00—Control of linear speed; Control of angular speed; Control of acceleration or deceleration, e.g. of a prime mover
    • 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
    • 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
    • F02D1/02—Controlling fuel-injection pumps, e.g. of high pressure injection type not restricted to adjustment of injection timing, e.g. varying amount of fuel delivered
    • F02D1/08—Transmission of control impulse to pump control, e.g. with power drive or power assistance
    • F02D1/12—Transmission of control impulse to pump control, e.g. with power drive or power assistance non-mechanical, e.g. hydraulic
    • F02D1/122—Transmission of control impulse to pump control, e.g. with power drive or power assistance non-mechanical, e.g. hydraulic control impulse depending only on engine speed
    • F02D1/127—Transmission of control impulse to pump control, e.g. with power drive or power assistance non-mechanical, e.g. hydraulic control impulse depending only on engine speed using the pressure developed in a pump
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02D—CONTROLLING COMBUSTION ENGINES
    • F02D2700/00—Mechanical control of speed or power of a single cylinder piston engine
    • F02D2700/02—Controlling by changing the air or fuel supply
    • F02D2700/0269—Controlling by changing the air or fuel supply for air compressing engines with compression ignition
    • F02D2700/0282—Control of fuel supply
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02D—CONTROLLING COMBUSTION ENGINES
    • F02D2700/00—Mechanical control of speed or power of a single cylinder piston engine
    • F02D2700/02—Controlling by changing the air or fuel supply
    • F02D2700/0269—Controlling by changing the air or fuel supply for air compressing engines with compression ignition
    • F02D2700/0282—Control of fuel supply
    • F02D2700/0284—Control of fuel supply by acting on the fuel pump control element
    • F02D2700/0292—Control of fuel supply by acting on the fuel pump control element depending on the speed of a centrifugal governor

Definitions

  • an accumulator into which liquid is displaced by the control element during each pressure stroke, a spring-biased accumulator piston which, during each suction stroke of the control element, Vforces the liquid out from the accumulator; conduit means which are opened and closed by the control element in such a coordinated manner that during each suction stroke, provided the frequency of reciprocation of the control element exceeds a predetermined rpm., the liquid displaced frorn the accumulator is allowed to expand into a cylinder displacing to a varying extent a regulating piston connected to the fuel quantity control members of the fuel injection pump.
  • the invention relates to a hydraulic regulator particularly for fuel injection pumps of internal combustion engines.
  • the regulator has a piston-operated accumulator including a spring which urges the accumulator piston against an abutment into its position of rest and wherein the force of the spring varies with its excursion.
  • the accumulator is adapted, lirst to be hydraulically connected with a liquid source under pressure, causing the accumulator spring to be compressed so that its force increases and secondly, to be hydraulically connected with a regulating device including a spring-biased regulating piston that is periodically exposed to the pressure prevailing in the accumulator.
  • a principal object of the invention is to provide an improved hydraulic regulator which is adapted to adjust the quantity control member of a multi-cylinder pump, such as the quantity control rod of a serially connected pump.
  • the aforenoted hydraulic connections are made and broken by a control element in such a coordinated manner that the accumulator, after being cut olf from the liquid source and before being connected to the regulator, is in communication with a r ICC chamber of lower pressure for a duration which is a function of the r.p.rn. to be regulated.
  • the conduit connecting the accumulator with said chamber of lower pressure includes a throttle passage to dampen the motion of the accumulator piston.
  • the control element driven with a speed depending upon the r.p.m. to be regulated, is a piston which executes alternating pressure strokes and suction strokes.
  • the bore in which the control element reciprocates defines a pump work chamber which, during said pressure strokes performs the function of the aforenoted liquid source and during said suction strokes is transformed into the aforenoted chamber of lower pressure.
  • FIGS 1-4 are axial sectional views of an embodiment of the invention is different operational positions.
  • a control element 1 which serves both as a pump piston and as a control shuttle.
  • the control element reciprocates to and fro with a frequency proportion to the r.p.m. of an internal combustion engine to which fuel is delivered by an injection pump associated with the regulator according to the invention.
  • the pressure stroke or inward motion of the control element 1 is effected by means not shown, such as a cam
  • the return force for the suction stroke or return motion of element 1 is supplied by a spring 2.
  • the outer cylindrical face of the control element 1 in the vicinity of the upper end thereof is provided with a circumferential annular groove 3 which is connected with a pump work chamber 5 through a conduit 4 extending within the control element 1. Chamber 5 forms the upper terminal section of bore 1a.
  • the pump work chamber 5 is supplied with liquid through a conduit 6 which is in continuous communication with a liquid supply tank, schematically indicated at 7. Communication is established between conduit 6 and chamber 5 through conduit 4 and groove 3 as the latter registers with conduit 6 when the control element 1 is in, or adjacent, its lower dead center.
  • a bore 8a of housing H there is slidably disposed an accumulator piston 8 which delimits an accumulator chamber 9.
  • a spring 22 which urges the accumulator piston 8 into a position of rest against an abutment 21 fixedly held at the lower end of bore 8a.
  • the tension of, or the force exerted by, spring 22 is at a minimum value.
  • the hydraulic pressure in accumulator chamber 9 also increases as it will become apparent later.
  • the pump Work chamber 5 communicates with the accumulator chamber 9 through a conduit 10 in which there is disposed a check valve 11 permitting a liquid ow only from the pump work cha-mber 5 to the accumulator chamber 9 while 'blocking any ow in the opposite direction.
  • the control element 1 displaces a ⁇ determined quantity ⁇ of liquid into the accumulator chamber 9 lso that the accumulator piston 8 is displaced from its position of rest into a new position where it opens a transfer port 23 which is connected to the low-pressure liquid tank 7. This condition is shown in FIG. 2.
  • the position of accumulator piston 8 represented by this figure thus places an upper limit for the maximum possible ypretensioning of spring 22 and consequently for the maximum possible hydraulic pressure in the accumulator chamber 9.
  • conduits 12 and 16 From accumulator chamber 9 there extend two conduits 12 and 16, merging into bore 1a at ⁇ different heights thereof.
  • control element 1 subsequent to a pressure stroke, performs the initial or first part of its return or suction stroke, at least part of the liquid, displaced into accumulator chamber 9 during the preceding pressure stroke, will flow therefrom through conduit 12 and its throttle passage 13, the sectional area of which is adjustable ⁇ by means of a throttle needle 13a.
  • the accumulator piston 8 moves in the direction of its position of rest toward abutment 21 and is dampened in its motion by virtue of the throttle passage 13.
  • the duration .of lliquid ilow through conduit 12 is dependent upon the r.p.m. of the engine as it will become more apparent ⁇ as the specilication progresses.
  • the conduit 12 is opened by registry with the annular groove 3 when the control element 1 approaches its upper dead center.
  • the conduit 12 will tbe connected with the pump work chamber 5 through conduit 4, so that the liquid displaced by the control element 1 will be forced finto the accu-mulator chamber 9 not only through conduit 10, but also partially through conduit 12.
  • the accumulator piston 8 driven by its spring 22, starts its return stroke during which it displaces liquid from the accumulator chamber 9 into the pump work chamber '5 through conduit 12, throttle passage 13, annular groove 3 ⁇ and conduit 4.
  • the throttle 13 causes a braking of the return motion of the accumulator piston 8. This return motion is interrupted at the moment when the conduit 12 is closed as the groove 3 shifts out of registry therewith.
  • a second annular groove 14 which is of such a ⁇ dimension that the conduit 16 is in communication therewith -at all times during the operation of control element 1.
  • a port 17 which is arranged in such a manner with respect to the annular circumferential groove 14 that it will register therewith only after the conduit 12 is closed by the upper section of the control element 1. The port 17 remains open in the time period in which the control element 1 reaches its low dead center and will be closed again before the control element 1 begins to displace liquid ⁇ from the pump work chamber 5 into the :accumulator chamber 9.
  • pistons 8 and 18 and the strength of springs 22 and 19 are selected such that the hydraulic pressure which is necessary to lift the accumulator piston 8 from its abutment 21 yis somewhat larger than the hydraulic pressure which is required to displace the regulating piston 18 from its abutment 20.
  • the spaces -for receiving Isprings 19 and 22 are connected to the ambient atmosphere through openings 28 and 27, respectively.
  • the cross-section ⁇ of the discharge port 24 is adjustable by means now shown.
  • the function of the discharge port 24 is to slow down the motion of the accumulator piston 8 during the terminal part of its upward movement and serves, during the first period of the return motion of the accumulator piston 8, as an additional drain conduit. By these means the degree of non-uniformity of the regulator device may he affected. A similar result may be reached by changing the elasticity of the spring 22.
  • IPort 17, which connects the cylinder 15 with the bore 1a may be provided with ya throttle passage 25 in order ⁇ to delay the establishment of a -balanced pressure condition Ibetween the accu-mulator chamber 9 and the cylinder 15.
  • an additional drain conduit 26 which, by means of the circuferential annular groove 3 of the control element 1, is opened shortly before the control element 1 reaches its upper dead center. In any other positions of the control element 1 the drain conduit 26 is closed.
  • the return motion of the accumulator piston 8 in case of a significant drop in the r.p.m. of the engine, is accelerated and, consequently, the regulator piston 18 is also allowed to rapidly move into its position of rest.
  • the abutments 20 and 21 may be adjusted by means not shown.
  • FIG. l shows the control element 1 in its lower dead center -while the pistons 8 and 18 are in their position of rest at their respective abutments 21 and 20.
  • the pressure of the liquid which now ows from the liquid supply tank 7 to the pump work chamber 5, is not suicient to ⁇ lift the accumulator piston 8 from its abutment 21.
  • FIG. 2 shows the control element 1 at the end of its pressure stroke, that is, in its upper dead center after the liquid from the pump work chamber 5 has been displaced into the accumulator chamber 9.
  • the accumulator piston 8 has been displaced into a position in which it opens at least the discharge port 24 but normally also the transfer port 23.
  • the accumulator piston 8 moves in the direction of its abutment 21.
  • the accumulator piston 8 attains its position of rest against abutment 21 before an interconnection is established between the accumulator chamber 9 and the cylinder 15 by opening the port 17 by control element 1 towards the end of its suction stroke.
  • the liquid displaced from the accumulator chamber 9 by the returning accumulator piston 8 cannot, under the aforestated r.p.m.
  • the uppermost position that the accumulator piston 8 may assume is determined by the location of the transfer port 23. In this position the spring 22 is compressed to a maximum eX- tent, that is, the pressure in the accumulator chamber 9 has reached its highest value. This highest pressure is just suflicient to displace the regulating piston 18 into a position in which the fuel injection pump delivers a minimum amount of fuel.
  • the r.p.m. of the driving means for the control element 1 again drops, then the location which the accumulator piston 8 reaches at the moment when the conduit 12 closes, shifts in the direction of the abutment 21.
  • the conforming pressure in the accumulator chamber 9 also decreases so that the regulating piston 18 is, during the open position of port 17, displaced by spring 19 in the direction of its abutment 20 which results in an increase in the fuel quantity delivered by the fuel injection pump.
  • the drain conduit 26 causes an accelerated discharged of the accumulator chamber 9 and, consequently, the regulating piston 18 will move rapidly into its position of rest with the end result of an accelerated increase in the fuel quantity delivered by the fuel injection pump.
  • the number of strokes may be determined which is necessary to move the regulating piston 18 from one position of equilibrium into another.
  • the invention provides a regulator which may be set to maintain a desired r.p.m. anywhere between an idling speed and a maximum revolution per minute.
  • Conduit 12 may lead directly into a chamber of lower pressure such as the liquid supply tank 7.
  • a control element should keep the conduit 12 open during the first part of the suction stroke and should shut ol the ⁇ same during the second part thereof.
  • a hydraulic regulator adapted to be associated with fuel injection pumps for varying the quantities of fuel delivered by said fuel injection pumps to internal combustion engines, said regulator operating as a function of the r.p.m. of said engine and comprising,
  • (E) means urging said accumulator piston against the force of said liquid of relatively high pressure and exerting to said accumulator piston a force increasing as a function of the displacement of said accumulator piston caused by said liquid of relatively high pressure
  • control element for causing an opening and closing of said hydraulic conduits in a coordinated manner, said control element adapted, in sequence, to establish a first communication between said accumulator chamber and said chamber containing liquid of relatively high pressure, to establish a second communication between said accumulator chamber and said regulating means after breaking off said rst communication and to establish a third communication between said accumulator chamber and said chamber containing liquid of relatively low pressure in a time period after breaking off said vfirst communication and before establishing said second communication, said control element adapted to maintain said third communication for a duration being the function of the r.p.m. of said engine.
  • a hydraulic regulator as defined in claim 2 including a housing having a bore, said control element is formed as a piston and is slidably received in said bore, during said pressure strokes said bore constitutes said chamber containing liquid of relatively high pressure and during said suction strokes said bore constitutes said chamber containing liquid of relatively low pressure.
  • a hydraulic regulator as dened in claim 1 including an abutment disposed in said accumulator chamber and constituting said position of rest for said accumulator piston and adapted to be engaged thereby, said regulating means includes (A) a cylinder,
  • a hydraulic regulator as defined in claim 1 including a transfer port leading from said accumulator chamber, said transfer port adapted to -be opened by said accumulator piston when displaced to a maximum extent by said liquid of relatively high pressure, said relatively high pressure which is present in said accumulator chamber when said accumulator piston is displaced to said maximum extent is at least as large as the pressure necessary to displace said regulating means to a maximum extent.
  • a hydraulic regulator as dened in claim 6 including a throttle passage leading from said accumulator chamber, said last named throttle passage is adapted to be opened by said accumulator piston before the latter opens said transfer port.
  • a hydraulic regulator as defined in claim 3 including a drain conduit leading from said bore, said control element adapted to maintain said drain conduit open upon completion of a pressure stroke and until starting a subsequent suction stroke.

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  • Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • General Physics & Mathematics (AREA)
  • Automation & Control Theory (AREA)
  • Fuel-Injection Apparatus (AREA)
US693885A 1967-01-02 1967-12-27 Hydraulic regulator particularly for fuel injection pumps of internal combustion engines Expired - Lifetime US3444849A (en)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
FR89726A FR1525077A (fr) 1967-01-02 1967-01-02 Perfectionnements apportés aux régulateurs hydrauliques de vitesse

Publications (1)

Publication Number Publication Date
US3444849A true US3444849A (en) 1969-05-20

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US693885A Expired - Lifetime US3444849A (en) 1967-01-02 1967-12-27 Hydraulic regulator particularly for fuel injection pumps of internal combustion engines

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US (1) US3444849A (de)
AT (1) AT288782B (de)
DE (1) DE1576293A1 (de)
FR (1) FR1525077A (de)
GB (1) GB1207979A (de)

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4014304A (en) * 1974-09-02 1977-03-29 Fiat Societa Per Azioni Injection pumps for diesel engines
US20160319812A1 (en) * 2015-05-01 2016-11-03 Graco Minnesota Inc. Pneumatic timing valve

Citations (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR717944A (fr) * 1931-03-10 1932-01-16 Magnetos R B Soc D Dispositif de régulation de moteurs diesel sans compresseur
DE716865C (de) * 1938-04-10 1942-01-31 Kloeckner Humboldt Deutz Ag Brennstoffeinspritzvorrichtung fuer Brennkraftmaschinen
DE1000633B (de) * 1951-05-11 1957-01-10 Fiat Spa Hydraulischer Regler
US2821926A (en) * 1954-06-28 1958-02-04 Cessna Aircraft Co Variable volume reciprocating pump
US2905457A (en) * 1956-04-05 1959-09-22 Bryce Berger Ltd Hydraulic speed governing mechanism for prime movers
US2928376A (en) * 1954-02-19 1960-03-15 Keelavite Co Ltd Apparatus for the speed of regulation of hydraulic motors
US3141414A (en) * 1961-07-25 1964-07-21 Expl Des Procedes Chimiques Et Self-regulating reciprocating piston pumps
US3267865A (en) * 1964-12-24 1966-08-23 Bosch Gmbh Robert Fuel injection pump

Patent Citations (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR717944A (fr) * 1931-03-10 1932-01-16 Magnetos R B Soc D Dispositif de régulation de moteurs diesel sans compresseur
DE716865C (de) * 1938-04-10 1942-01-31 Kloeckner Humboldt Deutz Ag Brennstoffeinspritzvorrichtung fuer Brennkraftmaschinen
DE1000633B (de) * 1951-05-11 1957-01-10 Fiat Spa Hydraulischer Regler
US2928376A (en) * 1954-02-19 1960-03-15 Keelavite Co Ltd Apparatus for the speed of regulation of hydraulic motors
US2821926A (en) * 1954-06-28 1958-02-04 Cessna Aircraft Co Variable volume reciprocating pump
US2905457A (en) * 1956-04-05 1959-09-22 Bryce Berger Ltd Hydraulic speed governing mechanism for prime movers
US3141414A (en) * 1961-07-25 1964-07-21 Expl Des Procedes Chimiques Et Self-regulating reciprocating piston pumps
US3267865A (en) * 1964-12-24 1966-08-23 Bosch Gmbh Robert Fuel injection pump

Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4014304A (en) * 1974-09-02 1977-03-29 Fiat Societa Per Azioni Injection pumps for diesel engines
US20160319812A1 (en) * 2015-05-01 2016-11-03 Graco Minnesota Inc. Pneumatic timing valve
US10914304B2 (en) * 2015-05-01 2021-02-09 Graco Minnesota Inc. Pneumatic timing valve

Also Published As

Publication number Publication date
GB1207979A (en) 1970-10-07
AT288782B (de) 1971-03-25
DE1576293A1 (de) 1970-05-06
FR1525077A (fr) 1968-05-17

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