EP1183467B1 - Pompe a haute pression a etancheite perfectionnee - Google Patents

Pompe a haute pression a etancheite perfectionnee Download PDF

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Publication number
EP1183467B1
EP1183467B1 EP00936967A EP00936967A EP1183467B1 EP 1183467 B1 EP1183467 B1 EP 1183467B1 EP 00936967 A EP00936967 A EP 00936967A EP 00936967 A EP00936967 A EP 00936967A EP 1183467 B1 EP1183467 B1 EP 1183467B1
Authority
EP
European Patent Office
Prior art keywords
housing
pump
liquid
valve
cover
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
EP00936967A
Other languages
German (de)
English (en)
French (fr)
Other versions
EP1183467A1 (fr
Inventor
Christian Hervault
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.)
Continental Automotive France SAS
PSA Automobiles SA
Original Assignee
Peugeot Citroen Automobiles SA
Siemens VDO Automotive SAS
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 Peugeot Citroen Automobiles SA, Siemens VDO Automotive SAS filed Critical Peugeot Citroen Automobiles SA
Publication of EP1183467A1 publication Critical patent/EP1183467A1/fr
Application granted granted Critical
Publication of EP1183467B1 publication Critical patent/EP1183467B1/fr
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
    • F02M37/00—Apparatus or systems for feeding liquid fuel from storage containers to carburettors or fuel-injection apparatus; Arrangements for purifying liquid fuel specially adapted for, or arranged on, internal-combustion engines
    • F02M37/04—Feeding by means of driven pumps
    • F02M37/12—Feeding by means of driven pumps fluid-driven, e.g. by compressed combustion-air
    • 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
    • F04B1/12—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders having cylinder axes coaxial with, or parallel or inclined to, main shaft axis
    • F04B1/14—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders having cylinder axes coaxial with, or parallel or inclined to, main shaft axis having stationary cylinders
    • F04B1/141—Details or component parts
    • F04B1/145—Housings
    • 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
    • F04B43/02—Machines, pumps, or pumping installations having flexible working members having plate-like flexible members, e.g. diaphragms
    • F04B43/06—Pumps having fluid drive
    • F04B43/067—Pumps having fluid drive the fluid being actuated directly by a piston

Definitions

  • the present invention relates to a high pressure sealing pump perfected.
  • the liquid transferred is the fuel.
  • a high pressure pump for pumping of a first liquid, called transferred liquid of the type comprising a unit main pumping of the transferred liquid operated by a secondary unit of pumping a second liquid, called working liquid, and of the type comprising a housing general cylindrical shape in which the main and secondary units are arranged, the main unit comprising at least two suction and return valves respectively delivery of the transferred liquid, carried by a valve body housed in the housing, each valve communicating with two suction and discharge chambers respectively of the transferred liquid, delimited by facing surfaces of generally cylindrical shape, axis substantially coinciding with that of the housing, formed in the valve body and the housing.
  • a pump of this type is described for example in WO 97/47883.
  • the suction and outlet connected to the valves are separated by an O-ring seal rubber.
  • This seal housed in an annular groove formed in a surface device of the valve body, is relatively bulky.
  • the object of the invention is in particular to propose a high pressure pump, aforementioned type, provided with means for separating the suction and discharge chambers efficient and space-saving.
  • the invention relates to a high pressure pump, of the type cited above, characterized in that the facing surfaces comprise two shoulders complementary support between them so as to form a watertight joint plane separating the suction and discharge chambers.
  • FIG. 1 to 3 a high pressure pump according to the invention, designated by the general reference 12.
  • the pump 12 is intended for supplying high pressure fuel to an internal combustion engine of motor vehicle.
  • the pump 12 is therefore intended to pump a first liquid, to know fuel in the example described, called transferred liquid.
  • Figure 1 we recognize a connector 14 for connecting the pump 12 to a Fuel tank.
  • the pump 12 comprises a housing 16 of generally cylindrical shape, of axis X, in which are arranged a main unit 18 for pumping fuel and a secondary unit 20 for pumping a second conventional liquid, for example a mineral oil, called liquid job.
  • the main unit 18 is operated by the secondary unit 20 according to principles general operating methods described for example in WO 97/47883.
  • the housing 16 comprises a body 22, of generally cylindrical shape, surrounding the secondary unit 20, and a cover 24, of generally cylindrical shape, surrounding the unit main 18.
  • the body 22 of the housing and the cover 24 respectively form two opposite ends of the housing 16.
  • the housing body 22 is connected to the cover 24 by at least one screw 26, by example three screws 26.
  • a screw 26 will be described in more detail later.
  • the main unit 18 is separated from the unit secondary 20 by a separation disc 28 centered substantially on the X axis.
  • This disc 28 is preferably made of steel or cast iron.
  • the main unit 18 comprises at least one flexible membrane 30 of pumping fuel, for example three membranes 30 as in the example illustrated. It will be noted that only two membranes 30 are shown in the figures, especially in Figure 3.
  • the membrane 30 separates a fuel pumping chamber 32, arranged in the main unit 18, a working liquid compression chamber 34, arranged in the secondary unit 20.
  • the volume of the pumping chamber 32 is variable.
  • the compression chamber 34 is partially provided in the separation disc 28.
  • Each pumping chamber 32 is associated with a suction valve 36 for fuel and a fuel delivery valve 38.
  • These valves 36, 38, of structure and conventional operating systems, are carried by a body 40 housed in the cover 24 between a bottom of the latter and the separation disc 28.
  • the body 22 of the housing, the cover 24 and the valve body 40 are made of aluminum or an aluminum-based alloy or yet another equivalent light metal.
  • valves 36, 38 are connected in a manner known per se to the pumping 32 corresponding to a safety valve 42 of structure and conventional operation.
  • each membrane 30 is movable between a first maximum volume position of the pumping chamber 32, as shown in particular in FIGS. 2 and 3, and a second position of minimum volume of this pumping chamber (not shown in the figures).
  • the displacements of the membrane 30 are imposed in particular by the secondary unit 20 and control the opening and closing fuel suction and delivery valves 36, 38.
  • Each membrane 30 is constantly spring-loaded towards its first position by a spring 44, called a membrane spring.
  • Each valve 36, 38 communicates, on the one hand, with a chamber 46 fuel suction and, on the other hand, a fuel delivery chamber 48.
  • the suction chamber 46 is connected in a manner known per se to the connection 14 for supplying fuel.
  • the fuel suction 46 and discharge 48. chambers are delimited, at least in part, by facing surfaces 50, 52, of general shape cylindrical, with an axis substantially coinciding with the axis X.
  • a first surface 50 forms an inner surface of the cover 24.
  • the second surface 52 forms a surface device of the valve body 40.
  • the facing surfaces 50, 52 include two shoulders complementary 50E, 52E in contact with each other so as to form a watertight joint plane separating the suction 46 and discharge 48 chambers. This parting line is substantially perpendicular to the X axis.
  • the shoulders 50E, 52E form a seal effective metal-to-metal seal.
  • suction chamber 46 in which the pressure is more weak than in the discharge chamber 48, is delimited by the bottom of the cover 24 whose thickness is relatively small.
  • discharge chamber 48 is delimited by a peripheral wall of the cover 24 thicker than the bottom of this cover, so as to resist the high pressure reached by the fuel circulating in this delivery chamber.
  • the secondary unit 20 comprises a piston 54 for compressing liquid of work associated with each membrane 30 and intended to move this membrane 30 between its two positions.
  • the secondary unit 20 has three pistons 54 only two of which are visible in the figures, in particular in FIG. 3.
  • the piston 54 is slidably mounted in a body 56, preferably of steel or cast iron, so as to be movable substantially parallel to the axis X.
  • the piston 54 extends between the working liquid compression chamber 34, partly arranged in the piston body 56, and a reservoir 58 of working liquid.
  • the end of the piston 54, external to the body 56 of the piston, is recalled elastically by a spring 59 in contact with a rolling stop, for example a stop with needles 60, carried by a bias plate 62 for actuating the pistons 54.
  • This plate bias is carried by a hub 64 of the secondary unit 20.
  • This hub 64 is rotatably mounted around the X axis in the housing body 22 forming a bearing.
  • the bias plate 62 turns around the X axis jointly with the hub 64, the latter being connected to means classic drives by an Oldham type 66 seal.
  • the liquid tightness of work between the housing body 22 and the hub 64 is ensured by conventional means comprising in particular an annular seal 67 made of elastomer.
  • the hub 64 will be described more in detail later.
  • each screw 26 is provided with a head 26T and a threaded body 26C.
  • the 26T head is supported on a passing seat 68 formed in the body 22 of the housing.
  • the body 26C thread is screwed into a threaded hole 70 formed in an ear 72 integral with the cover 24. Therefore, the housing body 22, the intermediate assembly EI and the body 40 valves are clamped between the head 26T of the screw and the joint plane materialized by the shoulders 50E, 52E.
  • the axial dimension L1 of the intermediate assembly EI is substantially equal to the length L2 of the part of the body 26C of the screw extending between the 26T head of this screw and the tapped hole 70.
  • the expansions of the different materials namely, on the one hand, aluminum or light metal and, on the other hand, steel or cast iron, are substantially identical inside and outside of the housing 16.
  • the piston 54 is provided an axial bore 74 through which the working liquid can circulate between the reservoir 58 and the compression chamber 34.
  • the bore 74 is stepped and comprises a section 74A of large diameter, opening into the compression chamber 34, and a section 74B of small diameter, opening into the tank 58.
  • a ball, forming a valve 76 is housed in the section 74A of large diameter so as to be movable, on the one hand, between an E74 shoulder, separating the sections 74A and 74B, forming a seat for closing the valve 76, and on the other hand, a stop 78 for limiting the opening stroke of this valve 76.
  • the valve 76 opens as soon as the pressure of the working liquid in the tank 58 exceeds that of the working liquid in the compression chamber 34. In the case on the contrary, the valve 76 closes so as to close the bore 74.
  • the stiffness of the return spring 44 of the membrane 30 associated with the piston 54 is dimensioned so that this spring 44 maintain the working liquid contained in the compression chamber 34 in overpressure relative to the working liquid contained in the reservoir 58, this as long as the membrane 44 has not reached its first position of maximum volume of the pumping 32.
  • main unit 18 operating according to the principles of a positive displacement pump.
  • the membrane spring 44 allows the automatic return of the membrane 30 in its first position, this even in the absence of fuel in the main pumping unit 18. Furthermore, when the piston 54 moves towards the left considering Figures 2 and 3, given the leakage of working liquid between the compression chamber 34 and the reservoir 58, the membrane 30 reaches its first position before the piston 54 completes its stroke to the left. Therefore, once as the membrane 30 reaches its first position, the pressure of the working liquid in the compression chamber 34 drops compared to that of the working liquid in the tank 58, which opens the valve 76 and replenishes the compression chamber 34 in working liquid so as to compensate for leaks.
  • These filling means comprise a filling neck 80, connected to reservoir 58, closable by a plug 82.
  • the plug 82 is intended to cooperate by screwing with the neck 80.
  • the plug 82 has a blind hole 84, substantially axial, communicating via a hole 86 in the plug, substantially radial, with a peripheral recess 88 of the plug extended axially by a sealing surface 90 of this plug intended to cooperate with a seat shutter 92 formed in the end of the neck 80 near the reservoir 58.
  • the shutter surface 90 and the shutter seat 92 have general conical shapes, the sealing surface 90 converging towards the seat shutter 92.
  • the plug 82 is movable in the neck 80, by screwing, between a position pre-sealing of the reservoir 58, in which the sealing surface 90 is spaced from the seat 92, above this seat 92, as shown in FIG. 5, and a the closed position of this reservoir 58, in which the closed surface 90 is in tight contact with the seat 92, as shown in FIG. 3.
  • the neck 80 is likely to contain an overflow of working liquid in excess of the reservoir, the level N of this overflow extending into the neck 80 above the seat 92.
  • the plug 82 when the plug 82 is in its pre-sealing position, the peripheral recess 88 of this plug communicates with the reservoir 58, so that the blind hole 84 forms a receptacle for the overflow of working liquid. Otherwise, in the presence of the overflow in the neck 80, the plug 82 is movable in this neck between its pre-shutter and shutter positions.
  • the plug 82 To move the plug 82, the latter is provided with an 82T operating head. through which the open end of the blind hole 84 opens.
  • the head 82T is bounded by a polygonal inner surface 82I allowing the operation of the plug 82 using a conventional tool.
  • the 82T operating head can be delimited by a surface polygonal exterior 82E as shown in FIG. 6, for the maneuver plug 82 using a conventional tool.
  • the plug 82 carries an O-ring peripheral seal 93 positioned axially between the head 82T and the recess 88. This seal 93 provides sealing between the neck 80 and the plug 82 above the recess 88.
  • the plug 82 makes it possible to fill the reservoir 58 under vacuum of the following way.
  • the plug 82 is screwed into the neck 80 in its pre-sealing position as shown in Figure 5.
  • the filling of the reservoir 58 is continued until too much remains full in the neck 80 and the blind hole 84, as shown in FIG. 5.
  • the plug 82 is moved by screwing up its closed position as shown in Figure 3.
  • the reservoir 58 is then isolated of the filling neck 80, the quantity of working liquid remaining in the blind hole 84 being easily evacuated by the end of the blind hole 84 emerging through the head of maneuver 82T.
  • the reservoir 58 is connected to conventional means 94 for compensating for the expansion of the working liquid contained in the reservoir 58.
  • These means comprise a flexible membrane 96 separating a channel 98 of communication of the membrane 96 with the working liquid of the reservoir 58 and a space 100 for release of the membrane 96 protected by a shell 102 of shape general hemispherical.
  • the membrane 96 deforms according to the variations of the volume of working liquid contained in the reservoir 58.
  • FIG. 7 an alternative embodiment of the plug 82 has been shown.
  • the plug 82 comprises a ball 104 that can be moved forcibly between a pre-sealing position of the reservoir 58, as shown in dashed lines on the Figure 7, and a closed position of the reservoir 58, as shown in solid lines in this figure 7.
  • the surface of the ball 104 forms the sealing surface intended to cooperate with tightly with the seat 92 of the neck.
  • the filling neck 80 is closed by means of the ball 104. the following way.
  • the hub 64 will be described below in more detail with reference to FIG. 3.
  • the hub 64 comprises a sleeve 106, with an axis coinciding with the X axis, in which the bias plate 62 is housed.
  • the hub 64 also includes a ring 108 fixed on the external surface of sleeve 106.
  • the outer surface of the sleeve 106 forms a cylindrical surface peripheral SG for guiding the hub in rotation in the body 22 of the housing.
  • a face of the ring 108 forms a shoulder FE for axial positioning of the hub 64 relative to to the body 22 of the housing.
  • the body 22 of the housing comprises a jacket 110 whose surface internal forms a cylindrical surface of range SP in sliding contact with the surface SG guide device of the hub.
  • the housing body 22 also comprises a washer 112, arranged at a end of the jacket 110, provided with a face forming a flat surface of bearing FP in sliding contact with the FE shoulder of the hub.
  • the jacket 110 and the washer 112 are fixed in a manner known per se on the body 22 of housing and are made of conventional materials, preferably low coefficient of friction.
  • the shoulder FE of the hub 64 extending the surface of SG guide of this hub, is urged to bear against the bearing face FP of the body 22 of case by the elastic return force of the pistons 54 in contact with the needle stopper 60 as well as by the pressure of the working liquid in contact with the bias plate 62.
  • the cylindrical surface SP is formed by the internal surface of a sleeve 114, carried by the body 22 of housing, provided with an end extended by a flange 116 delimiting the flat surface of FP range.
  • the peripheral surface guide SG of the hub is formed by the external surface of a sleeve 118, in which is housed the bias plate 62, provided with an end extended by a flange 120 delimiting the axial positioning shoulder FE of the hub.
  • Sleeve 118 of hub cooperates with a sleeve 114 secured to the body 22 of the housing of the type shown in figure 8.
  • the peripheral guide surface SG and the positioning shoulder axial FE of the hub are formed by the external surface of a stepped tubular member 122, in a single piece, in which the bias plate 62 is housed.
  • the stepped member 122 can be easily produced in a conventional manner, in particular by stamping, processing and rectification.
  • the stepped member 122 is in sliding contact with a cylindrical surface of SP range and a flat surface of FP range provided on elements similar to those shown in FIG. 3.
  • the surface guide device SG of the stepped member 122 is in contact with bearing 124 extending substantially parallel to the axis X, and the shoulder of axial positioning FE is in contact with rolling needles 126, extending substantially radially with respect to the X axis.
  • the needles 124, 126 are carried by cages 128, 130 fixed so known per se on the body 22 of the housing.
  • the invention makes it possible to separate the suction and delivery chambers associated with the suction and discharge valves of the high pressure pump with simple and effective means.
  • the housing and the valve body in aluminum or equivalent light metal, make it possible to lighten the pump, this without leading to problems of differential expansion between these aluminum parts and other parts of the pump steel or cast iron.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Details Of Reciprocating Pumps (AREA)
EP00936967A 1999-06-08 2000-05-29 Pompe a haute pression a etancheite perfectionnee Expired - Lifetime EP1183467B1 (fr)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
FR9907214 1999-06-08
FR9907214A FR2794811B1 (fr) 1999-06-08 1999-06-08 Pompe a haute pression a etancheite perfectionnee
PCT/FR2000/001465 WO2000075514A1 (fr) 1999-06-08 2000-05-29 Pompe a haute pression a etancheite perfectionnee

Publications (2)

Publication Number Publication Date
EP1183467A1 EP1183467A1 (fr) 2002-03-06
EP1183467B1 true EP1183467B1 (fr) 2003-04-09

Family

ID=9546514

Family Applications (1)

Application Number Title Priority Date Filing Date
EP00936967A Expired - Lifetime EP1183467B1 (fr) 1999-06-08 2000-05-29 Pompe a haute pression a etancheite perfectionnee

Country Status (7)

Country Link
US (1) US6659734B1 (es)
EP (1) EP1183467B1 (es)
JP (1) JP4527916B2 (es)
DE (1) DE60002066T2 (es)
ES (1) ES2197098T3 (es)
FR (1) FR2794811B1 (es)
WO (1) WO2000075514A1 (es)

Families Citing this family (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR2826068B1 (fr) * 2001-06-19 2004-02-13 Siemens Automotive Hydraulics Dispositif de regulation de debit pour pompe transfert a carburant
US7377757B2 (en) * 2005-09-22 2008-05-27 Graves Spray Supply, Inc. Fluid pump with enhanced seal
CN105351176A (zh) * 2014-08-18 2016-02-24 汪国伦 一种采用大功率超声波焊接密封的潜水泵
BR112017012736B1 (pt) * 2014-12-24 2022-11-01 Robert Bosch Gmbh Unidade de bomba para alimentar combustível a um motor de combustão interna

Family Cites Families (16)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR860429A (fr) * 1939-06-22 1941-01-14 Olaer Soc Nouvelle pompe pour liquides
US2664048A (en) * 1951-05-21 1953-12-29 New York Air Brake Co Hydraulic pump with by-pass flow
DE1653532A1 (de) * 1966-10-28 1971-10-07 Lindesbergs Ind Ab Vorrichtung bei Pumpen
US3692052A (en) * 1970-03-27 1972-09-19 Hamish A G Cattanach Pressure controlled variable pump output by-pass system
CA1233363A (en) * 1984-06-01 1988-03-01 Robert E. Fischell Single valve diaphragm pump with decreased sensitivity to ambient conditions
DE3631408A1 (de) * 1986-09-16 1988-03-17 Bosch Gmbh Robert Axialkolbenpumpe
US4878815A (en) * 1988-05-18 1989-11-07 Stachowiak J Edward High pressure reciprocating pump apparatus
DE3838141C2 (de) * 1988-11-10 1998-12-24 Knf Neuberger Gmbh Membranpumpe
US5241986A (en) * 1990-12-20 1993-09-07 Yie Gene G Check valve assembly for high-pressure applications
DE4327970C2 (de) * 1993-08-19 1997-07-03 Ott Kg Lewa Hydraulisch angetriebene Membranpumpe mit mechanischer Membranhubbegrenzung
US5601345A (en) * 1994-12-16 1997-02-11 Kelsey-Hayes Company Stationary seal ABS pump
US5707219A (en) * 1995-10-04 1998-01-13 Wanner Engineering Diaphragm pump
DE69732802T2 (de) 1996-06-07 2006-04-06 Hydro Leduc Flüssigkeitshochdruckpumpe
US6213096B1 (en) * 1998-03-25 2001-04-10 Sanshin Kogyo Kabushiki Kaisha Fuel supply for direct injected engine
JP2000045906A (ja) * 1998-07-29 2000-02-15 Mitsubishi Electric Corp 高圧燃料ポンプ装置
IT1308782B1 (it) * 1999-07-02 2002-01-10 Elasis Sistema Ricerca Fiat Perfezionamenti ad una pompa ad alta pressione per l'alimentazione dicombustibile ad un motore a combustione interna.

Also Published As

Publication number Publication date
DE60002066T2 (de) 2004-03-04
DE60002066D1 (de) 2003-05-15
JP4527916B2 (ja) 2010-08-18
FR2794811B1 (fr) 2003-02-07
JP2003501586A (ja) 2003-01-14
FR2794811A1 (fr) 2000-12-15
ES2197098T3 (es) 2004-01-01
WO2000075514A1 (fr) 2000-12-14
EP1183467A1 (fr) 2002-03-06
US6659734B1 (en) 2003-12-09

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