US3719435A - Safety means for a differential pressure valve associated with a fuel injection apparatus - Google Patents

Safety means for a differential pressure valve associated with a fuel injection apparatus Download PDF

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Publication number
US3719435A
US3719435A US00195151A US3719435DA US3719435A US 3719435 A US3719435 A US 3719435A US 00195151 A US00195151 A US 00195151A US 3719435D A US3719435D A US 3719435DA US 3719435 A US3719435 A US 3719435A
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United States
Prior art keywords
valve
differential pressure
chamber
fuel
pressure valve
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Expired - Lifetime
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US00195151A
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English (en)
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F Eheim
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Robert Bosch GmbH
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Robert Bosch GmbH
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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02C—GAS-TURBINE PLANTS; AIR INTAKES FOR JET-PROPULSION PLANTS; CONTROLLING FUEL SUPPLY IN AIR-BREATHING JET-PROPULSION PLANTS
    • F02C7/00—Features, components parts, details or accessories, not provided for in, or of interest apart form groups F02C1/00 - F02C6/00; Air intakes for jet-propulsion plants
    • F02C7/22—Fuel supply systems

Definitions

  • ABSTRACT In order to protect against excessive loads the mem- Forei n A cation Prior Data brane of a differential pressure valve associated with a g pp y fuel metering valve of a fuel injection apparatus, there Nov. 7, 1970 Germany ..P 20 54 910.4 is provided a second differential pressure valve which is connected parallel with the first-named differential 123/139 123/140 MC pressure valve and which opens to discharge pres- [51] Int. Cl "1 04b 49/08 Surized fluid therefrom when the differential pressure [58] Field of Search ..417/307, 308, 302, 303;
  • This invention relates to a continuously operating fuel injection apparatus for vehicle-type gas turbines and is of the type which has a continuously operating fuel injection pump and control means for determining the injected fuel quantities. It further has a fuel quantity setting mechanism affecting the position of a control plunger which forms part of a fuel metering valve and which meters the fuel quantities admitted to the fuel injection nozzles. In order to ensure a constant pressure drop across the fuel metering valve regardless of the flow passage section of the latter, there is provided a differential pressure valve disposed in the fuel flow.
  • the fuel injection apparatus is further provided with means for an rpm-dependent control of the fuel quantities, means for limiting the pressure within the hydraulic system and means for protecting against excessive rpm and excessive temperature.
  • the fuel injection apparatus is further of the type wherein the flow passage section of the fuel metering valve is variable by means of an electromagnetic system directly connected to the control plunger.
  • a first differential pressure valve which is formed as a flat seat valve and which has a membrane as the movable valve member, there is associated in parallel arrangement a second differential pressure valve.
  • FIG. 1 is a longitudinal sectional view of a fuel injection apparatus incorporating the first embodiment of a second differential pressure valve and FIG. 2 is a fragmentary sectional view of a second embodiment of the second differential pressure valve.
  • FIG. 1 there is shown a regulator housing 1 in which there is disposed a gear pump 3 which serves as a fuel injection pump and which is driven by a drive shaft 2 and which supplies fuel through a bore 4 to an annular groove 5 of a guide sleeve 6. From the groove 5 the fuel flows through the bores 7 into an annular chamber 8 which is formed by a circumferential annular groove of a control plunger 11 and the inner bore 14 of the guide sleeve 6. The control plunger 11 is rotatably held in the bore 14 of the guide sleeve 6.
  • the two diametrically opposite control edges 12 of the control plunger 11 and the associated control slots 15 provided in the guide sleeve 6 form a fuel metering valve, the flow passage section 21 of which is variable directly by means of a fuel quantity setting mechanism connected with the control plunger 1 1.
  • the fuel quantity setting mechanism includes a magnet 18 which is rotatably held between two solenoids 19 (only one seen in FIG. 1) which, in turn, are mounted on a core 20 so that across the rotary magnet 18 and the core 20 a closed magnetic circuit may be established.
  • the rotary magnet 18 is affixed to the control plunger 11, the axial immobilization of which is effected by means of a setting screw 24. The latter urges the control plunger 1 1 against a movable abutment member 25 which is resiliently supported in a closure 27 with the interposition of a spring 26.
  • cam disc 30 which, as a function of the rotation of the control plunger 11, operates an inductive transducer or position sensor 32 through a follower 31 in contact with the cam disc 30.
  • the fuel metered by means of the control slots 15 flows through an annular groove 16 provided in the guide sleeve 6 and a channel 34 into a first chamber 35 of a first differential pressure valve 36 which is formed as a flat seat valve and the membrane 37 of which is clamped between the regulator housing 1 and a valve housing 38 coplanar with the stationarily supported valve seat 39.
  • the valve housing 38 is engaged, with the interposition of a ring 40, by a coil spring 41 which has a relatively flat spring characteristic.
  • the coil spring 41 urges the membrane 37, through an interposed spring seat disc 42, in the opening direction, so that the first differential pressure valve 36 is in an open position when not in operation.
  • From the annular groove 5 the fuel flows in an unthrottled manner through the bore 9 into a second chamber 10 of the first differential pressure valve 36.
  • the first chamber 35 and the second chamber 10 are separated from one another by the membrane 37. 1
  • a second differential pressure valve 70 Parallel with the first differential pressure valve 36, there is arranged a second differential pressure valve 70, the movable valve member of which is constituted by a valve piston 71 which is guided in a bore 72 and which is engaged by a spring 73. At its other end, the
  • a chamber 76 of the second differential pressure valve communicates with the chamber 35 of the first differential pressure valve 36 through a bore 75.
  • the valving face of the valve piston 71 is provided on a member 77 which is made of synthetic material such as fluorelastomer and which is fixedly secured to the piston 71.
  • the second difierential pressure valve 70 is urged in the opening direction against the force of the spring 73 by the fuel pressure prevailing in chamber 10. The fuel is admitted from the chamber 10 to the piston 71 through a channel 78. If the differential pressure valve 70 is in an open position, the fuel may flow from the chamber 10 through the channel 78 and a return conduit 79 into a fuel tank 80.
  • the differential pressure valve 70' constituting a second embodiment differs from the differential pressure valve 70 of the first embodiment merely in that the valve piston 71 exerts a force on a valve ball 81.
  • the fuel is supplied by the gear pump 3 to the fuel metering valve 12, where the metering is effected while maintaining a constant pressure drop by means of the first differential pressure valve 36.
  • the fuel pressure prevailing upstream of the fuel metering valve 12, 15 is communicated to the chamber 10
  • the fuel pressure prevailing downstream of the fuel metering valve 12, 15 is communicated to the chamber 35.
  • the valving membrane 37 is moved as a function of the pressure drop across the fuel metering valve 12, 15.
  • the flow passage section 21 is a measure for the volum of the throughgoing fuel quantities.
  • the membrane 37 operating as the moving valve component of the first differential pressure valve 36 is exposed to very high loads. They assume a critical value particularly during rapid changes of the engine load. Thus, for example, a high dynamic pressure is generated when the flow passage section 21 of the fuel metering valve 12, 15 approaches zero and also when the turbine is stopped. In such cases the membrane 37 is exposed to the entire delivery pressure of the gear pump 3. Such loads may lead to permanent deformations and even to a destruction of the membrane 37 and thus to a total breakdown of the fuel injection apparatus.
  • the second differential pressure valve 70 (FIG. 1) or 70' (FIG. 2) prevents the aforenoted excessive loads from being applied to the membrane 37 of the first differential pressure valve 36.
  • the closing spring 73 urges the piston 71 into its closed position with a force that is predetermined based on the maximum possible pressure difference in chambers 10 and 35 and on a proper safety factor.
  • the second differential pressure valve 70 In normal operation, the second differential pressure valve 70 is closed, but as soon as the pressure difference in chambers 10, 35 exceeds a predetermined maximum permissible value, the pressure in chamber 10 applied to the piston 71 through channel 78 overcomes the combined force of the spring 73 and the pressure in chamber 76 and shifts the piston 71 into its open position. Thus, the difi'erential pressure valve 70 is now open and permits fuel to flow through the bore 78 and the conduit 79 back into the fuel tank 80 until (b) a fuel metering valve disposed downstream of said pump and having a variable flow passage section to control the fuel quantities to be injected into a power plant for combustion, the improvement comprising,
  • A. a first difierential pressure valve having 1. a first chamber, 2. channel means for introducing the metered fuel from said fuel metering valve into said first chamber; 3. a second chamber,
  • channel means for introducing pressurized fuel from upstream of said metering valve into said second chamber
  • a second difi'erential pressure valve havin 1. a movable valve member,
  • valve piston is made of a synthetic material.

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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)
US00195151A 1970-11-07 1971-11-03 Safety means for a differential pressure valve associated with a fuel injection apparatus Expired - Lifetime US3719435A (en)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
DE19702054910 DE2054910A1 (de) 1970-11-07 1970-11-07 Kraftstoffeinspritzanlage, bei der ein Differenzdruckventil durch ein zweites Differenzdruckventil gesichert ist

Publications (1)

Publication Number Publication Date
US3719435A true US3719435A (en) 1973-03-06

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Family Applications (1)

Application Number Title Priority Date Filing Date
US00195151A Expired - Lifetime US3719435A (en) 1970-11-07 1971-11-03 Safety means for a differential pressure valve associated with a fuel injection apparatus

Country Status (9)

Country Link
US (1) US3719435A (OSRAM)
BR (1) BR7107366D0 (OSRAM)
DD (1) DD97711A6 (OSRAM)
DE (1) DE2054910A1 (OSRAM)
ES (1) ES396756A2 (OSRAM)
FR (1) FR2085622B2 (OSRAM)
IT (1) IT969058B (OSRAM)
PL (1) PL81716B1 (OSRAM)
SE (1) SE419883B (OSRAM)

Cited By (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4132201A (en) * 1973-10-03 1979-01-02 Eaton Corporation Metering valve for fuel injection
US4168688A (en) * 1973-10-03 1979-09-25 Eaton Corporation Metering valve for fuel injection
US4216752A (en) * 1978-06-30 1980-08-12 The Bendix Corporation Spill valve for a fluid control system
US5529460A (en) * 1993-07-28 1996-06-25 Coleman Powermate, Inc. Pressure washer with flow control switch

Citations (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3204623A (en) * 1963-05-20 1965-09-07 Continental Aviat & Eng Corp Fuel viscosity control device

Patent Citations (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3204623A (en) * 1963-05-20 1965-09-07 Continental Aviat & Eng Corp Fuel viscosity control device

Cited By (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4132201A (en) * 1973-10-03 1979-01-02 Eaton Corporation Metering valve for fuel injection
US4168688A (en) * 1973-10-03 1979-09-25 Eaton Corporation Metering valve for fuel injection
US4216752A (en) * 1978-06-30 1980-08-12 The Bendix Corporation Spill valve for a fluid control system
US5529460A (en) * 1993-07-28 1996-06-25 Coleman Powermate, Inc. Pressure washer with flow control switch

Also Published As

Publication number Publication date
FR2085622A2 (OSRAM) 1971-12-24
FR2085622B2 (OSRAM) 1973-02-02
DD97711A6 (OSRAM) 1973-05-14
ES396756A2 (es) 1974-10-16
DE2054910A1 (de) 1972-05-10
PL81716B1 (OSRAM) 1975-08-30
BR7107366D0 (pt) 1973-04-17
IT969058B (it) 1974-03-30
SE419883B (sv) 1981-08-31

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