EP1149244A1 - Vorrichtung zur reduzierung der axialkrafbelastung einer ein fluid fördernden pumpe - Google Patents
Vorrichtung zur reduzierung der axialkrafbelastung einer ein fluid fördernden pumpeInfo
- Publication number
- EP1149244A1 EP1149244A1 EP00988601A EP00988601A EP1149244A1 EP 1149244 A1 EP1149244 A1 EP 1149244A1 EP 00988601 A EP00988601 A EP 00988601A EP 00988601 A EP00988601 A EP 00988601A EP 1149244 A1 EP1149244 A1 EP 1149244A1
- Authority
- EP
- European Patent Office
- Prior art keywords
- shaft
- housing
- fuel according
- conveying fuel
- bores
- 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
Links
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
- F02M37/041—Arrangements for driving gear-type pumps
-
- 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
- F04C15/00—Component parts, details or accessories of machines, pumps or pumping installations, not provided for in groups F04C2/00 - F04C14/00
- F04C15/0042—Systems for the equilibration of forces acting on the machines or pump
-
- 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
- F04C2/00—Rotary-piston machines or pumps
- F04C2/08—Rotary-piston machines or pumps of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing
- F04C2/082—Details specially related to intermeshing engagement type machines or pumps
- F04C2/086—Carter
-
- 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
- F04C2/00—Rotary-piston machines or pumps
- F04C2/08—Rotary-piston machines or pumps of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing
- F04C2/10—Rotary-piston machines or pumps of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing of internal-axis type with the outer member having more teeth or tooth-equivalents, e.g. rollers, than the inner member
- F04C2/102—Rotary-piston machines or pumps of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing of internal-axis type with the outer member having more teeth or tooth-equivalents, e.g. rollers, than the inner member the two members rotating simultaneously around their respective axes
Definitions
- the invention relates to a device for reducing the axial force load of a fluid-conveying pump, such as a gear pump, which functions as a fuel delivery pump for supplying fuel to the internal combustion engine from the storage tank of a motor vehicle.
- a fluid-conveying pump such as a gear pump
- a device for delivering fuel from a storage tank of an internal combustion engine which is used to drive a motor vehicle.
- a feed pump is used in a feed line from the storage tank to the internal combustion engine, which feed pump has at least one pump chamber in its housing.
- a pair of rotatingly driven and intermeshing gearwheels Arranged in the pump chamber are a pair of rotatingly driven and intermeshing gearwheels which deliver fuel from an intake space which can be connected to the storage tank along a delivery channel formed between the end face of the gearwheels and the wall and into a pressure space which can be connected at least indirectly to the internal combustion engine.
- a further air-conveying pump is arranged in the housing of the feed pump, the suction side of which is connected to a brake booster of the motor vehicle.
- the configuration according to the invention of a fuel-delivering pump on the one hand its manufacture can be simplified and consequently made more cost-effective.
- the wall delimiting the conveying device on the suction side can now be produced without the additional operation of milling out a relief groove in the end face of the area opposite the shaft accommodated in the housing.
- a surface treatment of the groove in the boundary wall provided on the suction side to increase the surface hardness can also be omitted, so that this component is generally cheaper to manufacture.
- the solution according to the invention can be used to reduce the unilateral axial force acting on the shaft accommodated in the housing. The axial force has so far led to premature wear of one end face due to frictional contact with the seating surface of the shaft.
- a relief force acting on the shaft and counteracting the axial force can be achieved there on the end face of the shaft opposite the boundary surface.
- the relief force acts on the axial force opposite the shaft and is generated by the application of a negative pressure to a surface enlargement in the form of a concave curvature on the end face of the shaft.
- the channel system opens into the shaft below a sealing ring which is accommodated on the shaft and seals a cavity formed as a circumferential groove on the end face. This cavity is connected to the suction side of the conveyor by a channel on the housing side.
- the negative pressure is applied via the channel system to the front of the shaft, where the enlargement of the upper compartment is formed.
- the surface enlargement formed on the end face of the shaft makes it possible to provide an enlarged effective area for the application of the negative pressure.
- the end face of the shaft can be kept away from contact with the opposite boundary wall and prevent premature wear.
- Fig. 1 shows the cross section through a conveyor device according to the invention with axial force relief
- FIG. 2 shows the top view of a conveyor device according to FIG. 1,
- Fig. 3 is a view of the suction surface
- Fig. 4 shows the section according to IV-IV.
- Fig. 1 shows the cross section through the conveyor device according to the invention for axial force relief.
- the housing 2 of the conveyor 1 is closed on the suction side by a boundary surface 3.
- a flange is cast on the drive side and surrounds a coupling element 19.
- the boundary surface 3 and the housing 2 have through holes 4.
- the housing 2 and the boundary surface 3 have sealing elements 5 which enclose the displacement elements 6 accommodated in the housing 2 in the region of the contact surface with the boundary surface 3.
- a shaft 8 is received, on which a displacement element 6 is mounted at one end, which is sealed off from the outside by the boundary surface 3.
- This displacement element 6, which is accommodated on the shaft designed as a stub shaft 8, works together with a further displacement element 6 mounted on the suction side 17.
- a dog clutch is on the shaft 8 19 added, via which the shaft 8 is driven.
- the claw coupling 19 has a groove 21 so that a positive drive of the shaft 8 can take place.
- non-positive drives via suitable drive connections are also conceivable.
- the shaft 8 is in turn penetrated by a through hole 11, which on the one hand opens into a surface enlargement 10 in the end region 9 of the shaft 8 and on the other hand opens into a transverse hole 12 which runs transversely to the axis of rotation of the shaft 8 and whose openings in the peripheral surface of the shaft 8 lead.
- the transverse bore 12 opens into the outer surface of the shaft 8 in the region of a sealing ring 13 received on the shaft 8.
- the sealing ring 13 lies with a lower sealing lip 15 above the openings of the transverse bore 13 in the peripheral surface of the shaft 8 and seals a cavity 14 provided on the housing side ,
- the housing-side cavity 14 is designed as a circumferential groove. From the cavity 14 extends to the suction side 17 of the conveyor 1, a housing bore 16, which is only indicated here by a center line.
- the flange that closes the claw coupling 19 for driving the shaft can be provided with an O-ring, which in interaction with the cover cap pe encapsulates the drive of the conveyor 1.
- the housing 2 of the conveyor device 1 - manufactured as a cast part - has, for example, reinforcing ribs 18, but on the outside it can be equipped with a smooth surface similar to the boundary surface 3.
- FIG. 2 shows the top view of a conveyor device according to FIG. 1.
- the housing 2 of the conveyor 1 is provided with two through bores 4 provided in the center of the housing.
- a pressure-side and a suction-side nozzle 23 are formed, via which fuel can be drawn from the storage tank on the one hand and fuel under pressure can be directed to the injection system of an internal combustion engine on the other hand.
- the housing 2 and the sealing surface 3 sealing it are screwed to one another via four fastening elements 25, each of which is received at the corner points of the conveyor device 1. 2 that the end of the shaft 8 is positively received between the claws of the claw coupling 19. Via the claw coupling 19, a drive (not shown here) ensures the rotation of the shaft 8, on which one of the displacement elements 6 is received, by means of which the pressure build-up on the housing 2 of the conveying device 1 takes place.
- FIG. 3 shows the boundary wall of the conveying device which is still designed with a relief groove.
- the boundary surface 3 is provided with threads for the fastening elements 25, so that the housing 2 and the boundary surface 3 can be connected to one another.
- the relief groove 27, extending from the suction side 17 to the base 9 of the shaft 8, can now be dispensed with, since the channel system 11, 12 according to the invention in the shaft 8 and the bore 16 in the housing 2 and the cavity in the housing 2, a relief force can be generated on the shaft 8 receiving the displacement element 6.
- Fig. 4 shows the section according to the section IV-IV drawn in Fig. 3.
- the relief groove 27, shown here in section, has hitherto required an additional milling operation to be carried out on the surface 3 delimiting the housing 2, which milling process can now be omitted.
- the boundary surface 3 can now be produced without such an operation, so that a flat contact of the boundary surface 3 on the sealing elements 5 contained in the housing 2 of the conveying device 1 can be achieved and the displacement elements 6 can each be sealed to the outside.
Landscapes
- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Chemical & Material Sciences (AREA)
- Combustion & Propulsion (AREA)
- Details And Applications Of Rotary Liquid Pumps (AREA)
- Rotary Pumps (AREA)
Abstract
Description
Claims
Applications Claiming Priority (3)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
DE19956520 | 1999-11-24 | ||
DE19956520A DE19956520A1 (de) | 1999-11-24 | 1999-11-24 | Vorrichtung zur Reduzierung der Axialkraftbelastung einer ein Fluid fördernden Pumpe |
PCT/DE2000/004006 WO2001038739A1 (de) | 1999-11-24 | 2000-11-10 | Vorrichtung zur reduzierung der axialkrafbelastung einer ein fluid fördernden pumpe |
Publications (2)
Publication Number | Publication Date |
---|---|
EP1149244A1 true EP1149244A1 (de) | 2001-10-31 |
EP1149244B1 EP1149244B1 (de) | 2006-05-24 |
Family
ID=7930165
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
EP00988601A Expired - Lifetime EP1149244B1 (de) | 1999-11-24 | 2000-11-10 | Vorrichtung zur reduzierung der axialkraftbelastung einer ein fluid fördernden pumpe |
Country Status (5)
Country | Link |
---|---|
US (1) | US6537046B1 (de) |
EP (1) | EP1149244B1 (de) |
JP (1) | JP2003515058A (de) |
DE (2) | DE19956520A1 (de) |
WO (1) | WO2001038739A1 (de) |
Families Citing this family (3)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
WO2007128257A1 (de) * | 2006-05-06 | 2007-11-15 | Luk Lamellen Und Kupplungsbau Beteiligungs Kg | Fördereinrichtung für ein fluid |
US20120258006A1 (en) * | 2011-04-11 | 2012-10-11 | Viking Pump, Inc. | External Gear Pump for Hot Cooking Oil |
US20120269668A1 (en) * | 2011-04-19 | 2012-10-25 | Viking Pump, Inc. | Polymeric External Gear Pump for Hot Cooking Oil |
Family Cites Families (17)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
DE152393C (de) * | 1902-10-24 | |||
DE1027988B (de) * | 1953-04-17 | 1958-04-10 | Dowty Hydraulic Units Ltd | Zahnradpumpe |
DE1134590B (de) * | 1957-11-09 | 1962-08-09 | Bosch Gmbh Robert | Zahnradpumpe |
DE1170786B (de) * | 1959-07-21 | 1964-05-21 | Friedrich Reichert Maschf | Fuer beide Drehrichtungen geeignete Zahnradpumpe |
US3063378A (en) * | 1961-01-17 | 1962-11-13 | Gen Metals Corp | Pump construction |
US3415459A (en) * | 1965-06-14 | 1968-12-10 | United Eng Foundry Co | Coil uncoiling arrangement |
US3416459A (en) * | 1966-05-24 | 1968-12-17 | Parker Hannifin Corp | Rotary pump or motor |
US4470776A (en) * | 1979-11-28 | 1984-09-11 | Commercial Shearing, Inc. | Methods and apparatus for gear pump lubrication |
JPS5830493A (ja) * | 1981-08-18 | 1983-02-22 | Matsushita Electric Ind Co Ltd | 歯車ポンプのポンプケ−ス |
DE3307099A1 (de) * | 1983-03-01 | 1984-09-06 | Alfred Teves Gmbh, 6000 Frankfurt | Verstellbare fluegelzellenpumpe |
JPH01174585U (de) * | 1988-05-27 | 1989-12-12 | ||
JP3032411B2 (ja) * | 1993-07-30 | 2000-04-17 | トリニティ工業株式会社 | 塗料用歯車ポンプ |
DE19513822C2 (de) | 1995-04-12 | 1999-10-28 | Volkswagen Ag | Einrichtung zum Fördern von Kraftstoff aus einem Vorratstank zu einer Brennkraftmaschine eines Kraftfahrzeuges |
DE19647053C1 (de) * | 1996-11-14 | 1998-04-30 | Bosch Gmbh Robert | Einrichtung zum Fördern von Kraftstoff aus einem Vorratstank zu einer Brennkraftmaschine eines Kraftfahrzeuges |
DE19714648B4 (de) * | 1997-04-09 | 2005-06-30 | Robert Bosch Gmbh | Kraftstoff-Förderpumpe |
DE29706316U1 (de) * | 1997-04-09 | 1998-08-06 | Robert Bosch Gmbh, 70469 Stuttgart | Förderpumpe |
US6152715A (en) * | 1998-01-30 | 2000-11-28 | Kaempe; Staffan I. | Pressure clamped hydraulic pump |
-
1999
- 1999-11-24 DE DE19956520A patent/DE19956520A1/de not_active Withdrawn
-
2000
- 2000-11-10 WO PCT/DE2000/004006 patent/WO2001038739A1/de active IP Right Grant
- 2000-11-10 EP EP00988601A patent/EP1149244B1/de not_active Expired - Lifetime
- 2000-11-10 JP JP2001540055A patent/JP2003515058A/ja active Pending
- 2000-11-10 US US09/889,892 patent/US6537046B1/en not_active Expired - Lifetime
- 2000-11-10 DE DE50012820T patent/DE50012820D1/de not_active Expired - Lifetime
Non-Patent Citations (1)
Title |
---|
See references of WO0138739A1 * |
Also Published As
Publication number | Publication date |
---|---|
EP1149244B1 (de) | 2006-05-24 |
DE19956520A1 (de) | 2001-06-13 |
JP2003515058A (ja) | 2003-04-22 |
US6537046B1 (en) | 2003-03-25 |
DE50012820D1 (de) | 2006-06-29 |
WO2001038739A1 (de) | 2001-05-31 |
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