EP0831231A2 - Pompe à engrenages - Google Patents

Pompe à engrenages Download PDF

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Publication number
EP0831231A2
EP0831231A2 EP97114967A EP97114967A EP0831231A2 EP 0831231 A2 EP0831231 A2 EP 0831231A2 EP 97114967 A EP97114967 A EP 97114967A EP 97114967 A EP97114967 A EP 97114967A EP 0831231 A2 EP0831231 A2 EP 0831231A2
Authority
EP
European Patent Office
Prior art keywords
chamber
feed pump
opening
pressure
bypass channel
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
EP97114967A
Other languages
German (de)
English (en)
Other versions
EP0831231B1 (fr
EP0831231A3 (fr
Inventor
Stanislaw Bodzak
Hanspeter Mayer
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.)
Robert Bosch GmbH
Original Assignee
Robert Bosch GmbH
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 Robert Bosch GmbH filed Critical Robert Bosch GmbH
Publication of EP0831231A2 publication Critical patent/EP0831231A2/fr
Publication of EP0831231A3 publication Critical patent/EP0831231A3/fr
Application granted granted Critical
Publication of EP0831231B1 publication Critical patent/EP0831231B1/fr
Anticipated expiration legal-status Critical
Expired - Lifetime 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
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C14/00—Control of, monitoring of, or safety arrangements for, machines, pumps or pumping installations
    • F04C14/24—Control of, monitoring of, or safety arrangements for, machines, pumps or pumping installations characterised by using valves controlling pressure or flow rate, e.g. discharge valves or unloading valves
    • F04C14/26—Control of, monitoring of, or safety arrangements for, machines, pumps or pumping installations characterised by using valves controlling pressure or flow rate, e.g. discharge valves or unloading valves using bypass channels
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C14/00—Control of, monitoring of, or safety arrangements for, machines, pumps or pumping installations
    • F04C14/04—Control of, monitoring of, or safety arrangements for, machines, pumps or pumping installations specially adapted for reversible machines or pumps

Definitions

  • the invention is based on a feed pump according to the preamble of claim 1.
  • a feed pump is known from DE 44 41 505 and is used there to deliver fuel from a storage tank to a fuel injection pump of an internal combustion engine.
  • the feed pump is designed as a gear feed pump, which has a gear pair meshing in external engagement.
  • the rotatingly driven pair of gearwheels conveys fuel from an intake space connected to the storage tank along a delivery channel formed between the end faces of the gearwheels and the peripheral wall of the pumping chamber into a pressure chamber, from which a delivery line leads to the fuel injection pump.
  • a bypass channel is provided between the pressure chamber and the suction chamber in the pump housing of the feed pump, into which a pressure valve opening in the direction of the suction chamber is inserted.
  • the bypass channel is opened via the pressure valve, which releases a certain opening cross section at the bypass channel at a certain differential pressure between the pressure and suction space, depending on the spring force of the valve spring.
  • the opening time and opening stroke can be adjusted via the biasing force of the valve spring of the pressure valve, for which purpose the axial position of an adapter sleeve acting as an abutment can be adjusted.
  • the known feed pump has the disadvantage due to the fixed arrangement of the bypass channel in the pump housing that the individual feed pumps can only be used as right-hand or left-hand feed pumps, so that different feed pump types are necessary for different directions of rotation of the drive, which increases manufacturing costs and is flexible The applicability of the feed pumps is restricted.
  • the feed pump according to the invention with the characterizing features of claim 1 has the advantage that it can be used both as a right-handed pump and as a left-handed feed pump. This is made possible in a simple manner by the inventive provision of the bypass channel in the housing cover of the feed pump which closes the pump chamber.
  • the bypass channel is formed in a structurally simple manner by a longitudinal bore in the pump cover which runs transversely to the axis of the gear wheels, the open end of which can be closed by means of a plug and from which a cross bore leads into the suction chamber and a cross bore into the pressure chamber of the feed pump.
  • the longitudinal bore of the bypass channel is provided in the vicinity of the tooth engagement line (contact line) of the meshing toothed wheels in the lid, so that the transverse bores of the bypass channel still open into the pump chamber even when the lid is rotated 180 ° around the pump axis.
  • the bypass channel is shifted from the center plane of the pump formed on the line of contact of the gears, the effect occurs that, depending on the rotational position of the cover, the respective transverse bores open into the pump chamber space on the left or the pump chamber space on the right. In this way, while the direction of action of the pressure valve used in the bypass channel is maintained, a simple rotation of the pump cover allows right and left rotation with only one feed pump construction and one bypass channel.
  • the inlet and outlet openings or suction and pressure openings of the pumping chamber are advantageously arranged on the line of contact of the gearwheels and thus also lead safely into the respective pumping chamber space in both mounting positions. It is advantageous to provide the inlet line or the suction opening with a cross-sectional constriction, which forms a suction throttle to be adjusted accordingly.
  • a second bypass channel can also be provided in the pump cover, which is then arranged on the opposite side beyond the line of contact of the gearwheels in the pump cover.
  • the feed pump according to the invention is particularly suitable for delivering fuel from a storage tank to a fuel injection pump of an internal combustion engine, but can also be used for delivering other liquid delivery media.
  • FIG. 1 shows a view of the cover side of the feed pump with the bypass channel cut out and the position of the gear wheels
  • FIG. 2 shows a sectional view of the feed pump in a view rotated by 90 ° to FIG. 1.
  • the feed pump according to the invention shown in FIGS. 1 and 2 is inserted into a feed line (not shown) from a storage tank to a fuel injection pump for internal combustion engines.
  • the exemplary embodiment of the feed pump shown in FIGS. 1 and 2 has a pump chamber 3 in its housing 1, in which a rotatingly driven pair of meshing gears is arranged.
  • a first gear wheel 5, which is located in the exemplary embodiment, is rotatably driven by means of an external drive element 7, which is not shown in more detail, and transmits this rotary movement via a spur toothing to a second gear wheel 9 meshing with the first gear wheel 5.
  • the gear wheels 5, 9 divide the pump chamber 3 by their tooth engagement into two partial areas, of which a first partial area forms an intake chamber 11 and a second part forms a pressure chamber 13.
  • the suction chamber 11 is connected to the pressure chamber 13 via a delivery channel 15 formed between the tooth grooves on the end faces of the first and second gear wheels 5, 9 and the upper and lower peripheral wall of the pumping chamber 3.
  • the suction chamber 11 and the pressure chamber 13 each have a connection opening in the wall of the pump housing 1, via which the suction chamber 11 is connected to a suction line (not shown) from the storage tank and the pressure chamber 13 to a delivery line (also not shown) to the suction chamber of the fuel injection pump.
  • connection opening in the suction chamber 11 forms a suction or inlet opening 17 and the connection opening in the pressure chamber 13 forms a pressure or outlet opening 19, which are arranged in a housing cover 21 which closes the pumping chamber 3, the inlet opening not being shown in detail Has cross-sectional reduction that forms a suction throttle.
  • the gear wheels 5, 9 are mounted on housing pins which project into the interior of the pump housing 1 and which are formed in one piece with the pump housing 1.
  • a first housing pin 23 located at the bottom forms a bearing pin which receives the first gear wheel 5
  • a second housing pin 25 located at the top forms a bearing pin which receives the second gear wheel 9.
  • the first housing pin 23 has an axial through bore 27, in which a drive shaft 29 is guided, which is connected in a rotationally locking manner to the drive element 7 at its end facing away from the housing cover 21. At its end remote from the drive element 7, the drive shaft 29 protrudes from the bore 27 of the first housing pin 23 into a coupling member 31 to the first gear 5, via which the rotary movement of the drive shaft 29 is transmitted to the gear 5.
  • a bypass duct 41 is also provided for pressure control of the delivery pressure in the pressure chamber 13 and thus for the delivery rate control.
  • This bypass channel 41 which connects the pressure chamber 13 to the suction chamber 11, is arranged in the housing cover 21 and is formed by a longitudinal bore 43 in the housing cover 21 which runs perpendicular to the axis of the gear wheels 5, 9.
  • the longitudinal bore 43 is designed as a blind hole, the open end of which is closed by means of a sealing plug 45 or alternatively by means of a ball.
  • the longitudinal bore 43 is arranged close below a line of contact of the meshing gears 5, 9, at which the pump chamber 3 is separated into the suction chamber 11 and the pressure chamber 13, but does not intersect this line of contact.
  • a transverse opening leads into the pump chamber 3, a first transverse opening 47 opening into the suction chamber 11 on the left in the exemplary embodiment and a second transverse opening 49 opening into the pressure chamber 13 on the right.
  • the longitudinal bore 43 of the bypass duct 41 has a cross-sectional reduction in the direction of the pressure chamber 13 formed by a shoulder, which forms a valve seat 51 of a pressure valve 53 inserted into the bypass duct 41 and opening in the direction of the suction chamber 11.
  • a disc-shaped valve closing element 55 of the pressure valve 53 comes into sealing contact with this valve seat 51 and is acted upon by a valve spring 57 on its side facing away from the valve seat.
  • This valve spring 57 which acts as a compression spring and acts on the valve closing member 55, is supported on the annular end face of a slotted clamping sleeve 59 pressed into the end of the longitudinal bore 43 on the suction chamber side, via the axial immersion depth of which the pretensioning force of the valve spring 57 can be adjusted.
  • the first transverse opening 47 is arranged in the region of the overlap with the clamping sleeve 59 and the second transverse opening 49 is arranged in the bore region of the longitudinal bore 43 adjoining the valve seat 51 on the pressure chamber side.
  • a so-called right-hand feed pump is shown, in which the drive shaft 29 rotates clockwise (on the opposite side of the cover in the opposite direction), with the suction chamber 11 on the left and the pressure chamber 13 on the right in the cover view. If the direction of rotation of the drive shaft 29 is now reversed, the right-hand space (formerly pressure chamber) of the pumping chamber 3 now acts as a suction space and the left-hand space (formerly suction space) acts as a pressure space.
  • the housing cover 21 is now removed and rotated again by 180 ° about the pump axis, so that the longitudinal bore 43 of the bypass channel 41 is now arranged above the line of contact of the gear wheels 5,9.
  • the now transversely swapped first transverse opening 47 again opens into the suction chamber 11 and the second transverse opening 49 again into the pressure chamber 13.
  • the feed pump according to the invention works in the following way.
  • the drive shaft 29 is preferably driven to rotate in proportion to the speed of an internal combustion engine to be supplied.
  • the drive shaft 29 transmits the rotational movement via the coupling member 31 to the first gear 5, which in turn drives the second gear 9 meshing with it.
  • the delivery medium preferably fuel
  • the intake chamber 11 is conveyed from the intake chamber 11 along the delivery channels 15 into the pressure chamber 13. This creates a negative pressure in the intake space 11, which is sufficient to draw in additional fuel from the storage tank via the intake line.
  • the fuel pressure built up in the pressure chamber 13 causes fuel to be delivered via the outlet opening 19 into the delivery line to the fuel injection pump.
  • the control of the maximum delivery pressure and the maximum delivery rate at the outlet opening 17 to the delivery line via the bypass channel 41 takes place by the valve closing member 55 of the pressure valve 53 used therein lifting off from a certain pressure in the pressure chamber 13 from the valve seat 51 and thus opening an outflow cross section at the bypass channel 41 , via which a part of the pressurized flow rate flows out of the pressure chamber 13 into the suction chamber 11, the opening pressure of the pressure valve 53 being able to be set via the biasing force of the valve spring 57.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Fluid Mechanics (AREA)
  • Details And Applications Of Rotary Liquid Pumps (AREA)
  • Rotary Pumps (AREA)
EP97114967A 1996-09-19 1997-08-29 Pompe à engrenages Expired - Lifetime EP0831231B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE19638335 1996-09-19
DE19638335A DE19638335C2 (de) 1996-09-19 1996-09-19 Förderpumpe

Publications (3)

Publication Number Publication Date
EP0831231A2 true EP0831231A2 (fr) 1998-03-25
EP0831231A3 EP0831231A3 (fr) 1999-03-03
EP0831231B1 EP0831231B1 (fr) 2003-01-08

Family

ID=7806190

Family Applications (1)

Application Number Title Priority Date Filing Date
EP97114967A Expired - Lifetime EP0831231B1 (fr) 1996-09-19 1997-08-29 Pompe à engrenages

Country Status (3)

Country Link
US (1) US6116859A (fr)
EP (1) EP0831231B1 (fr)
DE (2) DE19638335C2 (fr)

Families Citing this family (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE19913406A1 (de) * 1999-03-25 2000-04-20 Bosch Gmbh Robert Kraftstoffförderpumpe
DE19913804A1 (de) * 1999-03-26 2000-09-28 Bosch Gmbh Robert Kraftstoff-Förderpumpe
DE10002613A1 (de) * 2000-01-22 2001-07-26 Volkswagen Ag Kraftstoffversorgung für eine Kraftfahrzeug-Brennkraftmaschine
DE102005042040B3 (de) * 2005-09-02 2007-05-16 Fresenius Medical Care De Gmbh Zahnradpumpe
US8360746B2 (en) * 2006-05-10 2013-01-29 Metaldyne Company, Llc Inverted pressure regulating valve for an engine oil pump
DE102010050163A1 (de) 2010-10-30 2012-05-03 Iav Gmbh Ingenieurgesellschaft Auto Und Verkehr Verdrängermaschine mit reduziertem Betriebsgeräusch
DE102022202606A1 (de) 2022-03-16 2023-09-21 Robert Bosch Gesellschaft mit beschränkter Haftung Kraftstofffördereinrichtung
US12313071B1 (en) 2024-06-14 2025-05-27 Hamilton Sundstrand Corporation Gear pump with suction housing element providing a tight seal between suction and high-pressure chamber to increase pump efficiency and method of providing tight seal

Citations (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE4441505A1 (de) 1994-11-22 1996-05-23 Bosch Gmbh Robert Kraftstoff-Förderpumpe für eine Kraftstoffeinspritzpumpe für Brennkraftmaschinen

Family Cites Families (10)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CA711046A (en) * 1965-06-08 Dresser Industries Pressure relief means for pump
US2276107A (en) * 1939-05-09 1942-03-10 John P Simons Gear pump
DE1170786B (de) * 1959-07-21 1964-05-21 Friedrich Reichert Maschf Fuer beide Drehrichtungen geeignete Zahnradpumpe
DE2254316A1 (de) * 1972-11-06 1974-05-16 Agfa Gevaert Ag Kombiniertes regel- und druckbegrenzungsventil
DE7507541U (de) * 1975-03-11 1976-09-23 Werdohler Pumpenfabrik, Rudolf Rickmeier Gmbh, 5980 Werdohl Zahnradpumpe
ES445021A1 (es) * 1976-02-10 1977-06-01 Bendiberica Sa Perfeccionamientos en bombas de engranaje.
US4902202A (en) * 1987-07-29 1990-02-20 Hydreco, Inc. Variable discharge gear pump with energy recovery
US5338161A (en) * 1991-06-19 1994-08-16 Dana Corporation Gear pump having internal bypass valve
US5236317A (en) * 1991-09-26 1993-08-17 Permco, Inc. Gear pump valving system
FR2706541B1 (fr) * 1993-06-11 1995-09-08 Renault Vehicules Ind Procédé de régulation de la pression et du débit de refoulement d'une pompe volumétrique et pompe volumétrique pour la mise en Óoeuvre du procédé.

Patent Citations (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE4441505A1 (de) 1994-11-22 1996-05-23 Bosch Gmbh Robert Kraftstoff-Förderpumpe für eine Kraftstoffeinspritzpumpe für Brennkraftmaschinen

Also Published As

Publication number Publication date
DE19638335C2 (de) 2000-07-20
DE19638335A1 (de) 1998-04-02
US6116859A (en) 2000-09-12
DE59709077D1 (de) 2003-02-13
EP0831231B1 (fr) 2003-01-08
EP0831231A3 (fr) 1999-03-03

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