EP0939222A2 - Pompe à carburant - Google Patents

Pompe à carburant Download PDF

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Publication number
EP0939222A2
EP0939222A2 EP99300524A EP99300524A EP0939222A2 EP 0939222 A2 EP0939222 A2 EP 0939222A2 EP 99300524 A EP99300524 A EP 99300524A EP 99300524 A EP99300524 A EP 99300524A EP 0939222 A2 EP0939222 A2 EP 0939222A2
Authority
EP
European Patent Office
Prior art keywords
bores
fuel pump
eccentric cam
fuel
bore
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.)
Withdrawn
Application number
EP99300524A
Other languages
German (de)
English (en)
Other versions
EP0939222A3 (fr
Inventor
Peter Alban George Collingborn
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
Lucas Industries Ltd
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 Lucas Industries Ltd filed Critical Lucas Industries Ltd
Publication of EP0939222A2 publication Critical patent/EP0939222A2/fr
Publication of EP0939222A3 publication Critical patent/EP0939222A3/fr
Withdrawn legal-status Critical Current

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B1/00—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders
    • F04B1/04—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders having cylinders in star- or fan-arrangement
    • F04B1/047—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders having cylinders in star- or fan-arrangement with actuating or actuated elements at the outer ends of the cylinders
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B1/00—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders
    • F04B1/04—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders having cylinders in star- or fan-arrangement
    • F04B1/0404—Details or component parts
    • F04B1/0413—Cams

Definitions

  • This invention relates to a fuel pump, and in particular to a fuel pump suitable for use in supplying fuel under pressure to charge an accumulator or common rail of a common rail fuel injection system to permit the delivery of fuel under pressure to the cylinders of a compression ignition internal combustion engine.
  • EP-A-0809023 describes a fuel pump for use in charging a common rail, the pump comprising a plurality of pumping plungers driven by an eccentric cam arrangement mounted upon a drive shaft.
  • the supply of fuel by one or more of the pumping plungers may be terminated, in use, in order to control the quantity of fuel delivered by the pump at any particular operating speed without applying excessive torque fluctuations to the drive shaft.
  • a fuel pump comprising a plurality of pumping plungers reciprocable within bores provided in a pump body under the influence of an eccentric cam arrangement having an eccentric cam surface, wherein the eccentric cam surface encircles the part of the pump body within which the bores are provided, and bearings for supporting the eccentric cam arrangement whilst permitting rotation thereof, the bearings being located radially outward of the eccentric cam surface in a plane generally aligned with the pumping plungers.
  • the eccentric cam arrangement may form part of or be carried by a drive member which is conveniently driven from the cam shaft of an associated engine.
  • a drive member which is conveniently driven from the cam shaft of an associated engine.
  • Such an arrangement is advantageous in that the axial length of the fuel pump can be reduced as the drive member bearings are located in the same plane as the pumping plungers. Further, the application of side loads to the drive member and cam shaft is reduced.
  • the bores communicate with a common inlet passage located adjacent an inner end of each of the bores.
  • Inlet and outlet valves are associated with each bore, the inlet valves conveniently being located within each respective bore.
  • the fuel pump illustrated in the accompanying drawings comprises a pump body 10 which comprises a region 10 a of generally triangular cross-section which is integral with a region 10 b defining a generally circular flange.
  • the region 10 a is provided with three upstanding projections 12, blind bores 14 extending through the projections 12, along the axes thereof, and extending into the main part of the region 10 a .
  • An axially extending inlet passage 16 extends from the face of the region 10 a remote from the flange 10 b , the passage 16 terminating adjacent the inner ends of the bores 14. Drillings 18 of diameter smaller than the diameter of the bores 14 interconnect the bores 14 with the passage 16.
  • the end of the passage 16 remote from the flange 10 b is closed by a plug 20.
  • the passage 16 communicates through a radially extending drilling 22, the outer end of which is closed by a plug 24, with a drilling 26 which extends in a direction parallel to the axis of the pump body 10.
  • a plug 28 closes the end of the drilling 26 remote from the flange 10 b .
  • the drilling 26 communicates with an inlet port 30 provided in the flange 10 b .
  • a pumping plunger 32 is reciprocable within each of the bores 14.
  • An inlet valve arrangement controls the supply of fuel to each bore 14 from the passage 16, the inlet valves each taking the form of a valve member 34 which is engageable with a seating defined by the step at the interconnection between each bore 14 and the associated drilling 18.
  • the valve members 34 take the form of generally circular members of diameter smaller than the diameter of the bores 14 each member including three equi-angularly spaced, radially extending arms of length sufficient to ensure that the valve member 34 remains generally coaxial with the bore 14, the arms spacing the circular part of the valve member 34 from the wall of the bore 14 to define a flow path permitting fuel to flow between the valve member 34 and wall of the bore 14 when the valve member 34 is lifted from its seating.
  • a low rate coil spring 36 is engaged between the pumping plunger 32 and the valve member 34 to bias the valve member 34 towards its seating. As illustrated, the coil springs 36 are conveniently located within axially extending blind drillings provided in the plungers 32.
  • the flange 10 b is provided with a relatively large diameter, blind bore within which a plug 38 is located, the plug 38 and bore together defining an annular chamber 40 which communicates with an outlet passage and outlet port 42.
  • Drillings 44 provide flow paths between each bore 14 and the annular chamber 40, the drillings 44 defining valve seats against which spherical valve elements 46 are engageable to permit fuel to flow from the bores 14 to the outlet port 42, but substantially prevent flow in the reverse direction.
  • the plug 38 acts as a stop to limit movement of the spherical valve elements 46 away from the seatings.
  • each plunger 32 engages a pad 48 which in turn engages an inner surface of a load transmitting member 50.
  • the load transmitting member 50 comprises a tubular member having a generally circular outer periphery, the central passage of the tubular member being of generally hexagonal cross-section.
  • the pads 48 are biased into engagement with the load transmitting member 50 by coil springs 54 which are engaged between the part 10 a of the pump body and clip members 52 which are located within grooves provided against the outer ends of the plungers 32, the clip members 52 being shaped to engage the surface of the pads 48 remote from the load transmitting member 50.
  • the load transmitting member 50 is located within a large diameter bore formed in a rotary drive member 56 which is arranged to be driven from the cam shaft of an associated engine through an Oldham coupling arrangement 58.
  • the rotary drive member 56 is supported for rotary movement by bearings 60, 62 within a pump housing 64.
  • the pump housing 64 is arranged to be bolted or otherwise secured to the engine adjacent the cam shaft thereof.
  • the bore provided in the rotary drive member 56 is offset from the axis of rotation of the rotary drive member 56.
  • the wall of the bore defines an eccentric cam surface which engages the load transmitting member 50 and, as a result, as the drive member 56 rotates about its axis, the load transmitting member 50 follows a generally circular path, the load transmitting member remaining in the orientation illustrated due to the engagement of the pads 48 therewith, thus it will be appreciated that sliding movement occurs between the eccentric cam surface of the rotary drive member 56 and the load transmitting member 50.
  • the uppermost one of the pumping plungers 32 occupies its innermost position.
  • the movement of the eccentric cam surface defined by the bore formed in the rotary drive member 56 allows the uppermost pumping plunger 32 to move under the influence of the spring 54 drawing fuel into the bore 14 from the inlet passage 16 through the inlet valve.
  • the movement of the load transmitting member 50 results in sliding movement of the pad 48 on the inner surface of the load transmitting member 50.
  • the outward movement of the uppermost plunger continues until the rotary drive member 56 has rotated through an angle of 180°.
  • the uppermost pumping plunger 32 occupies its outermost position.
  • the rotary drive member 56 causes the uppermost pumping plunger 32 to be pushed inwards, pressurizing the fuel within the bore 14 to a sufficient extent to cause the valve member 46 of the outlet valve to lift from its seating, thus permitting the supply of fuel under pressure to the outlet port 42.
  • the fuel pressure within the bore 14 assists the spring 36 in ensuring that the inlet valve remains closed.
  • the other two plungers move in a like manner, but out of phase with each other and the uppermost plunger.
  • the pumping plungers 32 are arranged to be withdrawn from the bores 14 under the action of the springs 56, it will be appreciated that the provision of a separate, low pressure transfer pump may be avoided.
  • bearings 60 are located radially outward of the eccentric cam surface, and in generally the same plane as that containing the bores 14 and pumping plungers 32, it will be appreciated that a fuel pump of relatively short axial length can be provided. Further, the forces applied to the pumping plungers 32 to cause inward movement thereof, in use, are transmitted through the bearings 60 to the housing 64 without applying a significant side load to the rotary drive member 56 or cam shaft.
  • the arrangement may be modified by replacing the pads 48 with bucket tappet arrangements which ride on the outer surfaces of the projections 12 thus avoiding the application of side loads to the pumping plungers 32.
  • the springs 54 are located radially outward of the skirts of the bucket tappet arrangements. If the fuel pump is used in conjunction with a fuel metering arrangement, then in order to permit partial filling of the bores 14, and hence movement of the plungers 32 outward to a limited extent whilst ensuring that the bucket tappet arrangements remain in permanent contact with the load transmitting member 50, the clips 52 must be omitted.
  • the arrangement may further be modified by replacing the springs 36 with spring arrangements which engage in grooves provided in the walls of the bores 14 rather than in drillings formed in the pumping plungers 32.
  • the rotary drive member 56 may be rigidly secured to and carried by the cam shaft, in which case the provision of the bearings 60, 62 may be omitted.
  • a conventional taper drive arrangement may be used between the cam shaft and the rotary drive member 56.
  • the outer diameter of the pump may be reduced.
  • the outward movement of the plungers 32 may be controlled by appropriately controlling the fuel or fluid pressure within the housing 64.
  • the Oldham coupling arrangement 58 and the bearing 62 may be lubricated advantageously using engine oil, fuel being used to lubricate the bearing 60, and an appropriate seal 66 being used to contain the fuel.
  • an opening 68 is provided between the seal 66 and the bearing 62 to permit monitoring of whether either seal is leaking.
  • the bearing 62 is an interference fit with both the housing 64 and the drive member 56.
  • the bearing 62 incorporates a dynamic seal between its races.
  • the seal of the bearing 62 and the seal 66 separated from one another by a region which is vented to the atmosphere through the opening 68, reliably isolate the engine oil from the fuel.
  • the use of a dynamic seal rather than an additional seal separate from the bearing 62 saves space.
  • the bearing 60 is conveniently free to slide relative to the housing 64, the bearing 62 serving to locate the drive member 56 axially.
  • the bearing 60 could take the form of a cylindrical roller bearing arrangement.
  • the bearing 60 could be fixed relative to the housing 64, the bearing 62 being free to slide to accommodate such expansion. In such an arrangement, an additional seal may be required.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Fuel-Injection Apparatus (AREA)
EP99300524A 1998-02-27 1999-01-25 Pompe à carburant Withdrawn EP0939222A3 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
GBGB9804113.0A GB9804113D0 (en) 1998-02-27 1998-02-27 Fuel pump
GB9804113 1998-02-27

Publications (2)

Publication Number Publication Date
EP0939222A2 true EP0939222A2 (fr) 1999-09-01
EP0939222A3 EP0939222A3 (fr) 2000-06-07

Family

ID=10827656

Family Applications (1)

Application Number Title Priority Date Filing Date
EP99300524A Withdrawn EP0939222A3 (fr) 1998-02-27 1999-01-25 Pompe à carburant

Country Status (2)

Country Link
EP (1) EP0939222A3 (fr)
GB (1) GB9804113D0 (fr)

Citations (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP0809023A2 (fr) 1996-05-23 1997-11-26 Lucas Industries Public Limited Company Pompe à pistons radiaux

Family Cites Families (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4108130A (en) * 1977-05-18 1978-08-22 Caterpillar Tractor Co. Fuel injection pump
DE3431158A1 (de) * 1984-08-24 1986-03-06 Alfred Teves Gmbh, 6000 Frankfurt Radialkolbenmaschine, insbesondere kugelkolbenpumpe
DE3542938A1 (de) * 1985-12-04 1987-06-11 Rexroth Mannesmann Gmbh Kraftstoffeinspritzpumpe
DE4123669C2 (de) * 1991-07-17 1995-02-16 Bosch Gmbh Robert Saugseitig gedrosselte Kolbenpumpe
US5190447A (en) * 1992-03-23 1993-03-02 The United States Of America As Represented By The Secretary Of The Navy Hydraulic pump with integral electric motor
DE69720603T2 (de) * 1996-07-05 2004-03-04 Nippon Soken, Inc., Nishio Hochdruckpumpe

Patent Citations (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP0809023A2 (fr) 1996-05-23 1997-11-26 Lucas Industries Public Limited Company Pompe à pistons radiaux

Also Published As

Publication number Publication date
GB9804113D0 (en) 1998-04-22
EP0939222A3 (fr) 2000-06-07

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