EP1276992B1 - Pompe a engrenages, en particulier pour pompe a carburant haute pression - Google Patents

Pompe a engrenages, en particulier pour pompe a carburant haute pression Download PDF

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Publication number
EP1276992B1
EP1276992B1 EP01927598A EP01927598A EP1276992B1 EP 1276992 B1 EP1276992 B1 EP 1276992B1 EP 01927598 A EP01927598 A EP 01927598A EP 01927598 A EP01927598 A EP 01927598A EP 1276992 B1 EP1276992 B1 EP 1276992B1
Authority
EP
European Patent Office
Prior art keywords
section
groove
gear
distance
gear pump
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
EP01927598A
Other languages
German (de)
English (en)
Other versions
EP1276992A1 (fr
Inventor
Peter Boehland
Robert Reitsam
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
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Filing date
Publication date
Application filed by Robert Bosch GmbH filed Critical Robert Bosch GmbH
Publication of EP1276992A1 publication Critical patent/EP1276992A1/fr
Application granted granted Critical
Publication of EP1276992B1 publication Critical patent/EP1276992B1/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
    • 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
    • F04C2/12—Rotary-piston machines or pumps of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing of other than internal-axis type
    • F04C2/14—Rotary-piston machines or pumps of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing of other than internal-axis type with toothed rotary pistons
    • F04C2/18—Rotary-piston machines or pumps of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing of other than internal-axis type with toothed rotary pistons with similar tooth forms
    • 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
    • F04C15/0049—Equalization of pressure pulses

Definitions

  • the invention relates to a gear pump with a housing, two gears which are arranged in the housing and engage with each other, and at least one groove which is formed in the housing on the pressure side of the gear pump, as defined in the preamble of claim 1.
  • a gear pump with a housing, two gears which are arranged in the housing and engage with each other, and at least one groove which is formed in the housing on the pressure side of the gear pump, as defined in the preamble of claim 1.
  • Such a pump is eg ass each of the print fonts DE-A 1553014 or GB-A-967944 or GB-A2306354 known.
  • Such a gear pump can serve, in particular, as a prefeed pump for a high-pressure fuel pump, the fuel being supplied by the prefeed pump at a pressure of approximately 600 kPa (6 bar).
  • the high pressure fuel pump then generates a pressure which may be on the order of 180 MPa (1800 bar) as used in a so-called common rail injection system.
  • the gear pump is driven at the same speed as the high pressure fuel pump and must deliver enough fuel at the engine starting speed. For this reason, it is necessary that the gears run with the smallest possible clearance to the housing and the Umschlingungswin of the two gears, so the angular range over which filled with the fuel to be pumped tooth spaces between the suction side and the pressure side of the gear pump through the Housing sealed are as large as possible. At maximum engine speed, however, the gear pump may not deliver too much fuel. Instead of a complex valve control for volume control usually a throttle is used on the suction side, which limits this flow rate. This results in that when a certain flow rate, the interdental spaces are no longer completely filled with fuel.
  • the groove is provided, which should allow a continuous increase in pressure in the not completely filled with fuel interdental space.
  • the groove acts like a throttle, which allows a controlled back flow of the fuel from the pressure side of the pump in the tooth space located in the region of the groove.
  • the object of the invention is to develop a gear pump of the type mentioned in that even at low speeds, a large flow rate is achieved, while at high speeds cavitation damage to be avoided.
  • the groove forms a kind of pre-chamber, which communicates with the pressure side by the comparatively narrow gap formed in the first portion between the bottom of the groove and the tips of the gear teeth.
  • the narrow gap in conjunction with the overflow cross-section formed in the region of the second section of the groove, leads to a continuous increase in pressure of the interproximal space which opens straight to the groove.
  • the groove has an overall extension over a comparatively small angular range, so that there is a large wrap angle between gear and housing, which is advantageous for the flow rate at low speeds.
  • FIG. 1 shows a high-pressure fuel pump 5, which can compress fuel by means of a pump element 7 to a high pressure of the order of magnitude of up to 180 MPa (1800 bar).
  • the pump element is supplied with the fuel via a gear pump 10, which is in communication with a drive shaft 12 for the pump element 7.
  • the gear pump 10 has two gears 14, 16 (see FIG. 2) which engage with each other and are arranged in a housing 18. By rotation in the arrow direction, the gears 14, 16 feed the fuel, which is supplied on the suction side S, by means of the gap between two adjacent gear teeth 20 to the pressure side D.
  • FIG. 2 shows a groove 22 which is arranged in the housing starting from the pressure side.
  • the groove 22 serves to allow the most uniform, controlled pressure increase in the spaces between two adjacent gear teeth, when in the interdental spaces at the exit from the housing 18 and the passage to the pressure side, a lower pressure than on the pressure side and not complete with filled with fuel.
  • the vapor bubbles in the fuel would implode in the spaces between the teeth, and cavitation damage to the housing and to the flanks of the gear teeth 20 could occur. This would particularly affect the material sensitive to cavitation damage.
  • the groove 22 here consists of a first section 24, which extends over an angular range ⁇ , and a second section 26, which extends over an angular range ⁇ , wherein the angular range ⁇ is much smaller than the angular range ⁇ .
  • the distance s between the tips of the gear teeth and the bottom of the groove 22 is comparatively small, for example of the order of 0.2 mm, while the maximum distance t between the tooth tips and the bottom of the groove 22 in the second section is significantly greater is, for example, in the order of 0.7 mm.
  • the bottom of the groove 22 extends approximately concentrically with the axis of rotation of the gear 14, while the bottom of the groove 22 extends in the second section approximately parabolic starting from the first section.
  • the contour of the groove in the second portion is chosen so that it merges on its side facing away from the first portion end in an approximately radial direction in the region of the housing, which bears tightly against the toothed tips.
  • the angular range ⁇ is about 5 °, while the angular range ⁇ is about 36 °.
  • the angular ranges are matched to the distance of the gear teeth 20 from each other, that the groove 22 extends over a total angular range, which is slightly larger than the angular distance between two gear teeth.
  • the special design of the groove 22 leads to a continuous increase in pressure in the region of the interdental spaces in the passage of a tooth space from the region of the looping through the housing in the region of the pressure side.
  • the Gear 14 is thus in the position shown in Figure 3, in which a lying in front of the considered interdental space 28 gear tooth 20 enters the second portion 26 of the groove 22, there is a comparatively narrow gap between the housing and the corresponding gear tooth, so that the Fuel from a region of higher pressure comparatively slowly flows into the tooth space 28.
  • the flow is in the radial direction, so that it follows the gear edge in the direction of the tooth base. This is ensured by the course of the contour of the groove 22 in this area.
  • the described groove 22 can of course also be provided for the second gear 16 in order to prevent cavitation damage there as well.

Landscapes

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

Claims (9)

  1. Pompe à engrenage comprenant un boîtier (18), deux pignons (14, 16) montés dans le boîtier et en prise l'un avec l'autre, au moins une rainure (22) réalisée dans le boîtier sur le côté en pression de la pompe,
    caractérisée en ce que
    la rainure présente une première section (24) partant du côté en pression et dans laquelle le fond de la rainure (22) est proche des pointes des dents (20) du pignon, et une seconde section (26) faisant suite à la première et dans laquelle le fond de la rainure (22) est à une distance maximale des pointes des dents plus grande que celle dans la première section, cette première section s'étendant dans une zone angulaire (α) plus petite que la deuxième section, tandis que la rainure s'étend sur une zone angulaire (α, β) dépassant l'espacement angulaire de deux dents (20).
  2. Pompe à engrenage selon la revendication 1,
    caractérisée en ce que
    le contour de la première section de la rainure (22) présente un tracé qui donne une section constante.
  3. Pompe à engrenage selon la revendication 1 ou 2,
    caractérisée en ce que
    le contour de la seconde section de la rainure (22) présente un tracé qui donne une section décroissante.
  4. Pompe à engrenage selon la revendication 3,
    caractérisée en ce que
    le contour de la seconde section de la rainure (22) présente un tracé en forme de parabole.
  5. Pompe à engrenage selon la revendication 4,
    caractérisée en ce que
    le contour de la seconde section (26) du côté éloigné de la première section (24) est sensiblement radial par rapport à l'axe de rotation du pignon correspondant.
  6. Pompe à engrenage selon une des revendications précédentes,
    caractérisée en ce qu'
    elle est associée à une pompe de carburant à haute pression (5) et la distance (t) séparant les pointes de dent et le fond de la rainure de la seconde section est à peu près égale à la section effective d'écoulement dans la rainure divisée par la hauteur du pignon, tandis que la distance (s) entre les pointes de dent du pignon (14, 16) et le fond de la rainure (22) dans la première section est à peu près égale au tiers de la distance dans la première section.
  7. Pompe à engrenage selon la revendication 6,
    caractérisée en ce que
    la distance (t) entre les pointes de dent et le fond de la rainure dans la seconde section, est à peu près égale à 0,7 mm.
  8. Pompe à engrenage selon la revendication 6,
    caractérisée en ce que
    la distance (s) entre les pointes de dent du pignon (14, 16) et le fond de la rainure (22) dans la première section, est à peu près égale à 0,2 mm.
  9. Pompe à engrenage selon la revendication 6,
    caractérisée en ce que
    la première section (24) de la rainure (22) s'étend sur une zone angulaire d'environ 5°, tandis que la seconde section (26) s'étend sur une zone angulaire d'environ 36°.
EP01927598A 2000-04-13 2001-03-24 Pompe a engrenages, en particulier pour pompe a carburant haute pression Expired - Lifetime EP1276992B1 (fr)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
DE10018348 2000-04-13
DE10018348A DE10018348A1 (de) 2000-04-13 2000-04-13 Zahnradpumpe, insbesondere für eine Hochdruck-Kraftstoffpumpe
PCT/DE2001/001146 WO2001079699A1 (fr) 2000-04-13 2001-03-24 Pompe a engrenages, en particulier pour pompe a carburant haute pression

Publications (2)

Publication Number Publication Date
EP1276992A1 EP1276992A1 (fr) 2003-01-22
EP1276992B1 true EP1276992B1 (fr) 2007-07-25

Family

ID=7638617

Family Applications (1)

Application Number Title Priority Date Filing Date
EP01927598A Expired - Lifetime EP1276992B1 (fr) 2000-04-13 2001-03-24 Pompe a engrenages, en particulier pour pompe a carburant haute pression

Country Status (9)

Country Link
US (1) US6527530B2 (fr)
EP (1) EP1276992B1 (fr)
JP (1) JP2003531339A (fr)
KR (1) KR100691209B1 (fr)
BR (1) BR0105929B1 (fr)
DE (2) DE10018348A1 (fr)
RU (1) RU2267650C2 (fr)
TW (1) TW468002B (fr)
WO (1) WO2001079699A1 (fr)

Families Citing this family (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102006045932A1 (de) 2006-09-28 2008-04-03 Robert Bosch Gmbh Zahnradpumpe mit reduzierten Druckpulsationen auf der Förderseite
US20080181803A1 (en) * 2007-01-26 2008-07-31 Weinbrecht John F Reflux gas compressor
EP2180188B1 (fr) * 2008-10-24 2016-09-07 Edwards Limited Améliorations dans et concernant des pompes à racines
WO2010150388A1 (fr) * 2009-06-25 2010-12-29 株式会社Tbk Pompe à engrenages
DE102009029522A1 (de) 2009-09-17 2011-03-24 Robert Bosch Gmbh Zahnradpumpe mit zwei rotierenden Pumpelementen
WO2015181908A1 (fr) * 2014-05-28 2015-12-03 株式会社 島津製作所 Pompe ou moteur à engrenages
DE102017209022A1 (de) * 2017-05-30 2018-12-06 Robert Bosch Gmbh Außenzahnradmaschine

Family Cites Families (11)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2424750A (en) * 1941-07-05 1947-07-29 Du Pont Method and apparatus for metering, in its bubble-free state, a bubblecontaining fluid
GB967944A (en) * 1962-04-06 1964-08-26 Daimler Benz Ag Improvements relating to gear pumps
DE1553014A1 (de) * 1963-03-04 1969-08-21 Otto Eckerle Einrichtung an Pumpen zur Verminderung der Geraeuschentwicklung
US3667874A (en) * 1970-07-24 1972-06-06 Cornell Aeronautical Labor Inc Two-stage compressor having interengaging rotary members
DE2116317A1 (de) * 1971-04-03 1972-10-12 Motoren- Und Turbinen-Union Friedrichshafen Gmbh, 7990 Friedrichshafen Zahnradpumpe
USRE29627E (en) * 1974-02-12 1978-05-09 Calspan Corporation Rotary compressor
US4215977A (en) * 1977-11-14 1980-08-05 Calspan Corporation Pulse-free blower
DE3414064A1 (de) * 1982-10-13 1985-10-17 Aerzener Maschinenfabrik Gmbh, 3251 Aerzen Roots-kompressor zum komprimieren von gasfoermigen foerdermedium
DE3527292A1 (de) * 1985-07-30 1987-02-12 Aerzener Maschf Gmbh Verfahren zum komprimieren von gasfoermigem foerdermedium sowie roots-kompressor zur durchfuehrung des verfahrens
US5145349A (en) * 1991-04-12 1992-09-08 Dana Corporation Gear pump with pressure balancing structure
US6092283A (en) * 1995-10-18 2000-07-25 Caterpillar Inc. Method and apparatus for producing a gear pump

Also Published As

Publication number Publication date
TW468002B (en) 2001-12-11
WO2001079699A1 (fr) 2001-10-25
DE10018348A1 (de) 2001-10-25
KR100691209B1 (ko) 2007-03-09
DE50112762D1 (de) 2007-09-06
US6527530B2 (en) 2003-03-04
US20020106296A1 (en) 2002-08-08
RU2267650C2 (ru) 2006-01-10
EP1276992A1 (fr) 2003-01-22
BR0105929A (pt) 2002-03-12
JP2003531339A (ja) 2003-10-21
BR0105929B1 (pt) 2009-05-05
KR20020025076A (ko) 2002-04-03

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