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
  • F04B43/00—Machines, pumps, or pumping installations having flexible working members
  • F04B43/08—Machines, pumps, or pumping installations having flexible working members having tubular flexible members
  • F04B43/10—Pumps having fluid drive
  • F04B43/107—Pumps having fluid drive the fluid being actuated directly by a piston
• • 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
  • F04B49/00—Control, e.g. of pump delivery, or pump pressure of, or safety measures for, machines, pumps, or pumping installations, not otherwise provided for, or of interest apart from, groups F04B1/00 - F04B47/00
  • F04B49/16—Control, e.g. of pump delivery, or pump pressure of, or safety measures for, machines, pumps, or pumping installations, not otherwise provided for, or of interest apart from, groups F04B1/00 - F04B47/00 by adjusting the capacity of dead spaces of working chambers
• • 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
  • F04B43/00—Machines, pumps, or pumping installations having flexible working members
  • F04B43/0009—Special features
  • F04B43/0081—Special features systems, control, safety measures
• • 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
  • F04B49/00—Control, e.g. of pump delivery, or pump pressure of, or safety measures for, machines, pumps, or pumping installations, not otherwise provided for, or of interest apart from, groups F04B1/00 - F04B47/00
  • F04B49/10—Other safety measures
• • 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
  • F04B49/00—Control, e.g. of pump delivery, or pump pressure of, or safety measures for, machines, pumps, or pumping installations, not otherwise provided for, or of interest apart from, groups F04B1/00 - F04B47/00
  • F04B49/12—Control, e.g. of pump delivery, or pump pressure of, or safety measures for, machines, pumps, or pumping installations, not otherwise provided for, or of interest apart from, groups F04B1/00 - F04B47/00 by varying the length of stroke of the working members
• • 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
  • F04B49/00—Control, e.g. of pump delivery, or pump pressure of, or safety measures for, machines, pumps, or pumping installations, not otherwise provided for, or of interest apart from, groups F04B1/00 - F04B47/00
  • F04B49/22—Control, e.g. of pump delivery, or pump pressure of, or safety measures for, machines, pumps, or pumping installations, not otherwise provided for, or of interest apart from, groups F04B1/00 - F04B47/00 by means of valves

Definitions

• the present invention relates to the supply of high pressure gasoline injectors for internal combustion engines.
• pumps such as transfer pumps have been used to provide such a power supply in which an elastically deformable member resistant to the attacks of modern fuels (containing chemically aggressive additives), the deformations of this member being caused by a hydraulic pump. high pressure.
• the present invention also aims to achieve the regulation of the gasoline flow by performing this regulation in the oil part, but by other means much simpler than those described in the patents cited above.
• the present invention relates to a transfer pump for injection of high-pressure gasoline of the type comprising a piston displacing oil in a deformable element such as a bellows; the longitudinal deformations of said bellows in a cylindrical chamber filled with fuel causing a pumping effect of said fuel to a rail supplying high-pressure injectors, characterized in that means are provided for wholly or partly diverting the oil pumped by the piston towards a chamber without putting it under pressure so as to determine at will the useful stroke said piston and therefore the amount of fuel pumped at high pressure to the rail.
• Figure 1 a schematic sectional view of a first embodiment of the invention
• Figure 2 a schematic sectional view of a second embodiment of the invention.
• Figure 3 a schematic view corresponding to Figure 2 illustrating an alternative embodiment of the electro control valve.
• the transfer pump according to the invention is constituted by a piston 1, socio-reduction pump 1 and actuated by a cam 3 so as to have a movement back and forth.
• the cam 3 has three lobes but this is not limiting.
• This piston 1 moves in the bore 4 of a cylinder 5.
• This cylinder 5 is placed in a cylindrical chamber 6 formed in a pump body 7.
• the cylinder 5 is surrounded by a deformable bellows 8, which maintains a volume 9 between the outer walls of the bellows 8 and the inner walls of the cylindrical chamber 6.
• an orifice 10 which communicates the bore 4 of the cylinder 5 with the volume 11 between the inner wall of the bellows 8 and the outer wall of the cylinder 5.
• the bellows 8 is fixed at its upper end to a flange 8a integral with the pump body 7 and at its lower end to a plate 12 controlled by a spring 13.
• a yoke 14 fixed to the pump body 7, defining therewith a chamber 15, which communicates via a pipe 16 with the volume 11, which communicates through the orifice 10 with the base of the bore 4.
• a solenoid valve 17, controlled by a solenoid 18 is interposed between the chamber 15 and the pipe 16 which connects the chamber 15 and the volume 11.
• This solenoid valve 17 is subjected to the action of a spring 17a which tends to keep it open; and the action of the solenoid 18.
• the action of the spring 17a and the solenoid 18 has the effect of keeping open the electro valve 17 in the open position.
• the base of the chamber 6 comprises a supply pipe 20 and a delivery pipe 21.
• the supply pipe 20 is connected to a fuel tank 30 via a pipe 31 comprising a booster pump 32 and a non-return valve 22.
• the discharge pipe 21 comprises a non-return valve 24 at the outlet of the pump.
• the oil discharged by the piston 1 pushes the plate 12 against its spring 13 by lengthening the bellows 8.
• the plate 12 lowers the gasoline contained in 6 is pushed through the non-return valve 24; when the plate 12 returns to its starting position, the gasoline is admitted into the chamber 6 by passing through the nonreturn valve 22.
• the electro valve 17 is normally open; so that the oil discharged at 4 by the piston 1 passes through the orifice 10, passes through the volume 11 and through the pipe 16 returns to the chamber 15 without increasing pressure; the plate 12 remains stationary and the rail 40 does not receive fuel.
• the solenoid valve 17 is closed, the oil discharged by the piston 1 can no longer flow through the pipe 16, the plate 12 is pushed back and high pressure fuel is sent into the rail 40.
• the function of the solenoid 18 is to keep the solenoid valve 17 open when it is activated. When not activated, it is the difference in pressure of the oil between the pipe 16 and the chamber 15 which causes it to close.
• the amount of fuel sent into the rail 40 is therefore determined by the amount of oil that is displaced by the piston 1 when the solenoid valve 17 is closed.
• the total stroke of the piston 1 determines the maximum possible amount of fuel sent to the rail 40 when all the oil in the bore 4 is moved, the solenoid valve 17 is closed. By decreasing more or less the amount of oil displaced the amount of fuel sent to the rail 40 is correspondingly reduced. This reduction is obtained by keeping the solenoid valve 17 open for the time necessary to eliminate the excess oil.
• the solenoid valve 17 is deactivated, which causes it to close and therefore the pumping action to the rail 40.
• the entire volume of surplus oil is directly discharged into the chamber 15, without being pressurized and re-mixed with the oil in this chamber, which prevents any heating of the oil.
• the pump thus described is analogous to a variable displacement pump.
• a non-return valve 25, perfectly sealed is disposed on the pipe supplying the rail 40.
• This perfectly tight valve is made by overmolding a material such as rubber on a metal part.
• the perfect seal is provided by the rubber and the metal part prevents the extrusion of the rubber under the effect of pressure.
• the position of the valve 25 must be determined so that the gas volume between said non-return valve 25 and the chamber 6, in which the bellows is located, is small enough to prevent deformation of the bellows 8 during high pressure engine shutdown.
• the fuel supply pipe 31 may comprise a device 33 intended to avoid the pulsations caused by the pump.
• This device is constituted by the combination of a nonreturn valve 34 and a calibrated passage 35 in derivation of said valve 34.
• Figure 2 shows a variant of Figure 1, the identical elements bearing the same references.
• the transfer pump is constituted by a piston 1, cortenu by a spring 2 and actuated by a cam 3 (which has four lobes in this example).
• This piston 1 moves in a bore 41 formed in a pump body 41a.
• This piston 1 moves inside a deformable bellows 8, which is placed in a cylindrical chamber 6 and which communicates with the bore 41.
• the bore 41 comprises a circular chamber 45, which will fulfill the role of the chamber 15 of FIG.
• the internal volume of the bellows 8 is connected by a pipe 46 to a solenoid valve
• This duct 46 has a bypass 46a which, through a pressure relief valve 49, communicates with a duct 47.
• This pipe 47 connects the solenoid valve 42 with the accumulator 26, which acts as a heat compensator and volume compensator.
• valve 48 remains closed and at the beginning, a maximum flow rate is sent to the rail 40. This has the effect that the pressure valve 49 opens: all the flow then goes into the accumulator 26 and the pump is no longer supplied with hydraulic fluid, defuses; so that the engine operates in low pressure injection.
• valve 48 is biased in the open position by the spring 44; but the hydraulic fluid, arriving through the pipe 46 acts on said valve and closes it, which has the effect that the pumping function continues, that the rail 40 remains fed and that the engine continues to operate in high pressure injection.

Landscapes

• Engineering & Computer Science (AREA)
• Mechanical Engineering (AREA)
• General Engineering & Computer Science (AREA)
• Fuel-Injection Apparatus (AREA)
• Reciprocating Pumps (AREA)

Applications Claiming Priority (2)

Publications (1)

Family

ID=36822395

Family Applications (1)

Country Status (6)

Families Citing this family (5)

Family Cites Families (12)

• 2006
  • 2006-03-24 FR FR0602594A patent/FR2898942B1/fr not_active Expired - Fee Related
• 2007
  • 2007-03-05 US US12/294,242 patent/US8025488B2/en not_active Expired - Fee Related
  • 2007-03-05 EP EP07731087A patent/EP1999372A1/de not_active Withdrawn
  • 2007-03-05 KR KR1020087025894A patent/KR20080102318A/ko not_active Application Discontinuation
  • 2007-03-05 JP JP2009500884A patent/JP4887421B2/ja not_active Expired - Fee Related
  • 2007-03-05 WO PCT/FR2007/000388 patent/WO2007110492A1/fr active Application Filing

Non-Patent Citations (1)

Also Published As

Similar Documents

Legal Events