EP1247976A2 - Überdruckentlastungsventil in einem Kraftstoffsystem - Google Patents

Überdruckentlastungsventil in einem Kraftstoffsystem Download PDF

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Publication number
EP1247976A2
EP1247976A2 EP02252327A EP02252327A EP1247976A2 EP 1247976 A2 EP1247976 A2 EP 1247976A2 EP 02252327 A EP02252327 A EP 02252327A EP 02252327 A EP02252327 A EP 02252327A EP 1247976 A2 EP1247976 A2 EP 1247976A2
Authority
EP
European Patent Office
Prior art keywords
fuel
high pressure
pressure
valve
pump
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.)
Granted
Application number
EP02252327A
Other languages
English (en)
French (fr)
Other versions
EP1247976A3 (de
EP1247976B1 (de
Inventor
Anthony John Williams
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.)
Delphi Technologies Inc
Original Assignee
Delphi Technologies Inc
Priority date (The priority date 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 date listed.)
Filing date
Publication date
Application filed by Delphi Technologies Inc filed Critical Delphi Technologies Inc
Publication of EP1247976A2 publication Critical patent/EP1247976A2/de
Publication of EP1247976A3 publication Critical patent/EP1247976A3/de
Application granted granted Critical
Publication of EP1247976B1 publication Critical patent/EP1247976B1/de
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

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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
    • F02M59/48—Assembling; Disassembling; Replacing
    • 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
    • F02M55/00—Fuel-injection apparatus characterised by their fuel conduits or their venting means; Arrangements of conduits between fuel tank and pump F02M37/00
    • F02M55/02—Conduits between injection pumps and injectors, e.g. conduits between pump and common-rail or conduits between common-rail and injectors
    • 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
    • F02M59/36—Varying fuel delivery in quantity or timing by variably-timed valves controlling fuel passages to pumping elements or overflow passages
    • F02M59/366—Valves being actuated electrically
    • 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
    • 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
    • F02M59/466—Electrically operated valves, e.g. using electromagnetic or piezoelectric operating means
    • 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
    • F02M63/00—Other fuel-injection apparatus having pertinent characteristics not provided for in groups F02M39/00 - F02M57/00 or F02M67/00; Details, component parts, or accessories of fuel-injection apparatus, not provided for in, or of interest apart from, the apparatus of groups F02M39/00 - F02M61/00 or F02M67/00; Combination of fuel pump with other devices, e.g. lubricating oil pump
    • F02M63/02—Fuel-injection apparatus having several injectors fed by a common pumping element, or having several pumping elements feeding a common injector; Fuel-injection apparatus having provisions for cutting-out pumps, pumping elements, or injectors; Fuel-injection apparatus having provisions for variably interconnecting pumping elements and injectors alternatively
    • F02M63/0205—Fuel-injection apparatus having several injectors fed by a common pumping element, or having several pumping elements feeding a common injector; Fuel-injection apparatus having provisions for cutting-out pumps, pumping elements, or injectors; Fuel-injection apparatus having provisions for variably interconnecting pumping elements and injectors alternatively for cutting-out pumps or injectors in case of abnormal operation of the engine or the injection apparatus, e.g. over-speed, break-down of fuel pumps or injectors ; for cutting-out pumps for stopping the engine
    • F02M63/0215—Fuel-injection apparatus having several injectors fed by a common pumping element, or having several pumping elements feeding a common injector; Fuel-injection apparatus having provisions for cutting-out pumps, pumping elements, or injectors; Fuel-injection apparatus having provisions for variably interconnecting pumping elements and injectors alternatively for cutting-out pumps or injectors in case of abnormal operation of the engine or the injection apparatus, e.g. over-speed, break-down of fuel pumps or injectors ; for cutting-out pumps for stopping the engine by draining or closing fuel conduits

Definitions

  • the present invention relates to a fuel system for delivering fuel under high pressure to a cylinder of an associated compression ignition internal combustion engine.
  • the invention relates to a fuel pump arranged to deliver fuel to an injector for delivering fuel to a cylinder or other combustion space of the associated engine.
  • a fuel pump for pressurising fuel to high pressure is arranged to deliver fuel through a high pressure fuel line to a fuel injector.
  • the fuel pump may take the form of a unit pump in which a spill valve for controlling communication between a pump chamber and a low pressure drain is integrally formed within a main pump housing.
  • the injector may be integrally formed with the fuel pump in a unit pump/injector arrangement.
  • the injector typically includes a valve needle which is engageable with a valve seating to control the injection of fuel into the engine. In use, movement of the valve needle away from its seating permits fuel to flow from an injector delivery chamber, through an injector outlet opening, into a cylinder of the associated engine.
  • a fuel system which is arranged to deliver fuel at high pressure to a fuel injector through a high pressure fuel line, the fuel system including a pressure relief valve arrangement for relieving fuel pressure within the high pressure fuel line, wherein the pressure relief valve arrangement includes:
  • the fuel system may take the form of a fuel pump for delivering fuel to the injector.
  • the fuel system may take the form of a unit fuel pump.
  • the fuel system may also include the injector.
  • the fuel system may include a fuel pump and a fuel injector which are integrally formed in a unit pump/injector arrangement. It will be appreciated, however, that the fuel system need not include the injector.
  • At least one of the first and second valve surfaces is provided with a relief which is sealingly engageable with the other of the first and second surfaces upon application of the clamping load, the relief being separable from said other of the first and second valve surfaces in the event that fuel pressure within the high pressure fuel line exceeds the predetermined amount.
  • the relief on the surface may take the form of a projection of annular form or may comprise two or more annular projections.
  • the relief is preferably shaped to define a first area which is exposed to fuel pressure within the high pressure fuel line, the first area being selected to ensure separation of the first and second valve surfaces occurs at the required, maximum fuel pressure for a given clamping load.
  • the first valve surface is provide with a first relief and the second valve surface is provided with a second relief, the first and second reliefs being shaped to sealingly engage one another upon application of the clamping load and being separable in the event that fuel pressure within the high pressure fuel line exceeds the predetermined amount.
  • This arrangement is particularly advantageous if it is necessary for drillings, passages or other components to be accommodated within the first and/or second housing parts.
  • the relief provided on the first or second valve surface defines, together with the other of the first and second valve surfaces, a restricted clearance through which fuel flows from the high pressure fuel line to a region of low pressure at a restricted rate when the first and second valve surfaces are caused to separate.
  • the clamping load is applied by means of a cap nut.
  • the cap nut preferably forms at least a part of the clamping means for applying the clamping load to the second housing part.
  • the second housing part may take the form of an adapter plate forming part of the fuel pump.
  • a pressure relief valve arrangement for use in a fuel system as herein described, comprising first and second housing parts which define, at least in part, a high pressure fuel line, first and second valve surfaces being defined by the first and second housing parts respectively and being shaped for sealing engagement with one another upon application of the clamping load by the clamping means, and being separable from one another in the event that fuel pressure within the high pressure fuel line exceeds the predetermined amount.
  • a fuel pump arranged to deliver fuel at high pressure to a fuel injector through a high pressure fuel line, the fuel pump comprising a pressure relief valve arrangement for relieving fuel pressure within the high pressure fuel line, including:
  • a unit fuel pump referred to generally as 10, forming part of a fuel system for delivering fuel under high pressure to an associated compression ignition internal combustion engine.
  • the fuel pump has an outlet which communicates through a high pressure fuel line 12 with the inlet of a fuel injector (not shown) forming part of the fuel system.
  • the fuel injector is of the type comprising a valve needle which is slidable within a bore provided in a nozzle body and engageable with a valve seating to control fuel delivery through a fuel injector outlet into an engine cylinder or other combustion space of an associated engine.
  • the fuel system is conveniently controlled electronically by means of an engine control unit which receives signals from a plurality of sensors associated with the engine and which monitor various engine operating parameters such as, for example, engine speed, position and temperature.
  • the signals supplied to the control unit by the sensors are used to control the operation of the fuel system to control the pressure of fuel supplied to the injector and the timing at which the injection of fuel into the engine cylinder takes place.
  • the pump 10 includes a pump housing 14 defining a first bore 16 within which a pumping plunger 18 is reciprocable under the action of a cam and tappet arrangement, referred to generally as 20, which acts against the action of a return spring 22.
  • the first bore 16 and an end surface of the pumping plunger 18 define a pump chamber 24 within which fuel is pressurised, in use, upon reciprocal movement of the pumping plunger 18 within the bore 16, as will be described in further detail hereinafter.
  • the pump housing 14 is provided with a first recess 25 of generally cylindrical form within which a valve housing 26 is arranged.
  • the valve housing 26 is provided with a through bore 28 within which a pressure control valve member 30 is slideable.
  • the through bore 28 provided in the valve housing 26 is shaped to define a seating surface with which a region of the pressure control valve member 30 is engageable to control communication between a first passage 32 defined within the valve housing 26 and a low pressure fuel reservoir or drain (not shown).
  • the first passage 32 communicates, at one end, with the pump chamber 24 and forms part of a high pressure fuel line through which fuel is delivered from the pump chamber 24 to the outlet of the fuel pump 10, as will be described in further detail hereinafter.
  • a further spring 34 is engaged between the pressure control valve member 30 and a surface of the first recess 25 provided in the pump housing 14, the further spring 34 being arranged to bias the pressure control valve member 30 towards a position in which the pressure control valve member 30 is spaced away from the seating surface to permit communication between the first passage 32 and the low pressure drain.
  • the end of the pressure control valve member 30 remote from the further spring 34 carries an armature 36 which is movable under the influence of a magnetic field generated, in use, by an actuator 38.
  • the actuator 38 and the armature 36 are arranged such that energisation of the actuator 38 causes movement of the pressure control valve member 30 into engagement with the seating surface, against the action of the further spring 34, so as to break communication between the first passage 32 and the low pressure drain.
  • the pump housing 14 is provided with a pump chamber outlet passage 52 which communicates, at one end, with the pump chamber 24, the other end of the passage 52 communicating with the first passage 32 provided in the valve housing 26.
  • the end of the valve housing 26 remote from the pump housing 14 abuts an adapter plate 40 within which a second passage 42 is defined.
  • the second passage 42 communicates, at one end, with the first passage 32 provided in the valve housing 26 and, at its other end, with a further passage 44 provided in a cap nut 46.
  • the further passage 44 delivers fuel to the outlet of the pump 10.
  • the outlet passage 52 provided in the pump housing 14, the first passage 32 provided in the valve housing 26, the second passage 42 provided in the adapter plate 40 and the further passage 44 provided in the cap nut 46 therefore together define a high pressure fuel line through which fuel at high pressure flows from the pump chamber 24 to the outlet of the pump 10, and hence to the inlet of the injector, when the pressure control valve member 30 is in engagement with its seating to break communication between the high pressure fuel line and the low pressure drain.
  • the cap nut 46 is received within the first recess 25 defined in the pump housing 14 and is in screw threaded engagement with the pump housing 14 through a screw thread connection 60.
  • the cap nut 46 is arranged to apply a clamping load to the adapter plate 40, the valve housing 26 and the pump housing 14 which serves to secure the components in position.
  • the cap nut 46 defines a recessed surface 48 of part-cylindrical form which defines, in part, a chamber or region 62 at low pressure.
  • Appropriate seals 63 are provided to provide a substantially fluid tight seal between the pump housing 14 and the outer surface of the cap nut 46.
  • the recessed surface 48 of the cap nut 46 is in abutment with an upper surface (in the illustration shown) of the adapter plate 40 to define a first interface 50.
  • a second interface 54 is defined between the valve housing 26 and the pump housing 14 in the region of communication between the outlet passage 52 and the first passage 32.
  • a third interface 56 is defined between an end surface of the valve housing 26 remote from the outlet passage 52 and a surface of the adapter plate 40 in the region of communication between the first and second passages 32, 42.
  • the upper surface of the adapter plate 40 is provided with a relief which defines a projection 58 of annular form.
  • the inner diameter of the annular projection 58 defines a surface area, A, and the projection 58 has a surface area, B which is engageable with the opposing surface of the recessed surface 48 defined by the cap nut 46 in the region of the interface 50.
  • the clamping load applied by the cap nut 46 serves to urge the cap nut 46 into engagement with the projection 58 provided on the adapter plate 40, the adapter plate 40 into engagement with the valve housing 26 and the valve housing 26 into engagement with the pump housing 14 such that substantially fluid tight seals are formed in the region of the first, second and third interfaces 50, 54, 56.
  • the pressure control valve member 30 occupies a position in which it is spaced away from the seating surface defined by the through bore 28 to permit communication between the region of the high pressure fuel line defined by the first passage 32 and the low pressure drain.
  • movement of the cam and tappet arrangement 20 to cause reciprocal movement of the plunger member 18 within the first bore 16 will cause fuel to be drawn into the pump chamber 24 from the low pressure reservoir, and displaced from the pump chamber 24 to the low pressure reservoir, in a manner which would be familiar to a person skilled in the art.
  • the pressure control valve member 30 is urged into engagement with the seating surface to break communication between the region of the high pressure fuel line defined by the first passage 32 and the low pressure drain.
  • movement of the cam and tappet arrangement 20 causes the plunger member 18 to perform a pumping stroke, thereby causing fuel within the pump chamber 24 to be pressurised to a high level.
  • the cap nut 46 and the adapter plate 40 form a pressure relief valve arrangement which serves to limit the pressure of fuel within the high pressure fuel line to an acceptable, predetermined level.
  • the cap nut 46 and the adapter plate 40 define respective valve surfaces of the pressure relief valve which, in normal circumstances, are sealingly engaged with one another but which separate in circumstances in which the pressure of fuel within the high pressure fuel line between the pump chamber 24 and the outlet for the pump 10 exceeds an acceptable level. This may occur, for example, if a fault, blockage or failure in the fuel system occurs.
  • the provision of the pressure relief valve ensures any damage to the component parts of the pump and/or the injector which may otherwise occur in the event of such a fault, blockage or failure can be avoided.
  • the predetermined maximum pressure at which the projection 58 on the surface of the adapter plate 40 separates from the cap nut 46 to open the restricted clearance 61 will be largely determined by the surface area, A, exposed to fuel pressure within the high pressure fuel line and the clamping load exerted by the cap nut 46.
  • the surface area, B, of the projection 58 may affect this predetermined maximum pressure as a result of variable exposure to fuel pressure due to surface irregularities on the recessed surface 48 of the cap nut 46 and/or on the surface of the adapter plate 40.
  • the inner diameter of the annular projection 58 i.e.
  • the periphery of area A) and the stiffness of the cap nut/adapter plate interface 46, 40 will determine the flow area through the restricted clearance 61 and, together with the additional effect of the length of the restricted clearance 61 (determined by the shape of the surface area B), will determine the rate at which fuel is able to leak from the high pressure fuel line to low pressure.
  • the characteristics of the pressure control arrangement are such that the relationship between leakage flow and fuel line pressure is therefore defined by the surface area A, the periphery of area A, surface area B, the shape of surface area B, the stiffness of the cap nut/adapter plate 46, 40 interface and the clamping load.
  • the relief need not be provided on the surface of the adapter plate 40, but may alternatively be formed on the recessed surface 48 of the cap nut 46.
  • the recessed surface 48 of the cap nut 46 may also be provided with a corresponding relief which is cooperable with the projection 58 provided on the surface of the adapter plate 40. It may also be convenient to provide reliefs on one or two of the two engageable surfaces at the second and third interfaces 54, 56 between the valve housing 26 and the pump housing 14 and between the adapter plate 40 and the valve housing 26 respectively in view of the other components and/or passages in the vicinity of the second and third interfaces 54, 56. Fuel pressure within the high pressure fuel line is reduced due to flow through restricted flow paths from two or more regions of the high pressure line, in the event that fuel pressure within the high pressure fuel line exceeds the maximum amount.
  • a pressure control arrangement as hereinbefore described may be provided within any part of a fuel system and is not limited to use in a unit fuel pump, as shown in Figures 1 and 2.
  • the pressure control arrangement may be provided within a unit pump/injector or within a fuel injector itself.
  • the relief provided on the surface of the adapter plate 40, or on any one or more of the other surfaces of the pump housing 14 and the valve housing 26, need not take the form of a single annular projection, but may take any form, for example a multiple-lobe form or a multiple area form, which defines the appropriate surface area, A, exposed to fuel pressure within the high pressure fuel line and the appropriate surface area, B, required to give the necessary pressure relief characteristics of the pressure control arrangement.
  • A exposed to fuel pressure within the high pressure fuel line
  • B appropriate surface area
  • the clamp arrangement used to provide the clamping load to the adapter plate 40 need not be applied by means of a cap nut, and other clamping means may be employed to provide the required clamping load.

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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)
  • Electromagnetism (AREA)
  • Fuel-Injection Apparatus (AREA)
  • Safety Valves (AREA)
EP02252327A 2001-04-02 2002-03-28 Überdruckentlastungsventil in einem Kraftstoffsystem Expired - Lifetime EP1247976B1 (de)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
GBGB0108216.3A GB0108216D0 (en) 2001-04-02 2001-04-02 Fuel Injector
GB0108216 2001-04-02

Publications (3)

Publication Number Publication Date
EP1247976A2 true EP1247976A2 (de) 2002-10-09
EP1247976A3 EP1247976A3 (de) 2004-02-11
EP1247976B1 EP1247976B1 (de) 2006-11-15

Family

ID=9912071

Family Applications (1)

Application Number Title Priority Date Filing Date
EP02252327A Expired - Lifetime EP1247976B1 (de) 2001-04-02 2002-03-28 Überdruckentlastungsventil in einem Kraftstoffsystem

Country Status (4)

Country Link
EP (1) EP1247976B1 (de)
AT (1) ATE345441T1 (de)
DE (1) DE60215994T2 (de)
GB (1) GB0108216D0 (de)

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP1707799A1 (de) * 2005-03-30 2006-10-04 Denso Corporation Kraftstoffpumpe mit einem Plunger und dieselbe verwendendes Kraftstoffversorgungssystem

Families Citing this family (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102013220768A1 (de) * 2013-10-15 2015-04-16 Continental Automotive Gmbh Ventilanordnung

Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US5673853A (en) * 1995-09-13 1997-10-07 Cummins Engine Company, Inc. Electromagnetic fuel injector control valve
EP0856661A2 (de) * 1997-01-30 1998-08-05 Lucas Industries Public Limited Company Brennstoffpumpe
DE19822671A1 (de) * 1998-05-20 1999-11-25 Bosch Gmbh Robert Druckbegrenzungsventil
US6003497A (en) * 1994-10-31 1999-12-21 Caterpillar Inc. Mechanically actuated hydraulically amplified fuel injector with electrically controlled pressure relief
US6125822A (en) * 2000-02-04 2000-10-03 Stanadyne Automotive Corp. Two stage pressure relief valve

Patent Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US6003497A (en) * 1994-10-31 1999-12-21 Caterpillar Inc. Mechanically actuated hydraulically amplified fuel injector with electrically controlled pressure relief
US5673853A (en) * 1995-09-13 1997-10-07 Cummins Engine Company, Inc. Electromagnetic fuel injector control valve
EP0856661A2 (de) * 1997-01-30 1998-08-05 Lucas Industries Public Limited Company Brennstoffpumpe
DE19822671A1 (de) * 1998-05-20 1999-11-25 Bosch Gmbh Robert Druckbegrenzungsventil
US6125822A (en) * 2000-02-04 2000-10-03 Stanadyne Automotive Corp. Two stage pressure relief valve

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP1707799A1 (de) * 2005-03-30 2006-10-04 Denso Corporation Kraftstoffpumpe mit einem Plunger und dieselbe verwendendes Kraftstoffversorgungssystem

Also Published As

Publication number Publication date
GB0108216D0 (en) 2001-05-23
EP1247976A3 (de) 2004-02-11
ATE345441T1 (de) 2006-12-15
DE60215994D1 (de) 2006-12-28
DE60215994T2 (de) 2007-09-20
EP1247976B1 (de) 2006-11-15

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