EP1267077B1 - Zahnradpumpe mit drei Wellen - Google Patents

Zahnradpumpe mit drei Wellen Download PDF

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Publication number
EP1267077B1
EP1267077B1 EP20020291491 EP02291491A EP1267077B1 EP 1267077 B1 EP1267077 B1 EP 1267077B1 EP 20020291491 EP20020291491 EP 20020291491 EP 02291491 A EP02291491 A EP 02291491A EP 1267077 B1 EP1267077 B1 EP 1267077B1
Authority
EP
European Patent Office
Prior art keywords
chamber
delivery
pump
inlet
chambers
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 - Fee Related
Application number
EP20020291491
Other languages
English (en)
French (fr)
Other versions
EP1267077A1 (de
Inventor
Guillaume Adam
Jean Cros
Gonzalo Portela Garnika
Denis Reverseau
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.)
Renault SAS
Original Assignee
Renault SAS
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Filing date
Publication date
Application filed by Renault SAS filed Critical Renault SAS
Publication of EP1267077A1 publication Critical patent/EP1267077A1/de
Application granted granted Critical
Publication of EP1267077B1 publication Critical patent/EP1267077B1/de
Anticipated expiration legal-status Critical
Expired - Fee Related 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
    • F04C14/02—Control of, monitoring of, or safety arrangements for, machines, pumps or pumping installations specially adapted for several machines or pumps connected in series or in parallel
    • 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

Definitions

  • the present invention relates to the field of volumetric pumps, ie whose theoretical flow rate is proportional to the speed, used in particular for the lubrication of internal combustion engines of road vehicles.
  • a dual-gear volumetric pump comprising three pumping gears defining two intake chambers and two delivery chambers, a central supply duct connected to two inlet ducts opening respectively into the first and in the second inlet chamber, and a central discharge pipe joining two discharge pipes respectively from the first and the second discharge chamber.
  • this invention also applies to any volumetric pump having more than three gears defining between them more than two inlet chambers and two discharge chambers.
  • This type of pump is commonly used in systems, such as internal combustion engines of motor vehicles, whose lubrication requires a high flow and pressure at low speeds.
  • a first drive gear meshes with a second driven gear, driving itself a third driven gear.
  • the three gables define two by two, two intake chambers and two discharge chambers.
  • the two gears operate in parallel, in repressing two separate streams of oil.
  • the advantage of this mode of operation is to double the flow rate of a conventional single gear pump, by adding only the volume of a pinion.
  • the positive displacement pumps pose problems of use: on the one hand, the viscosity range of the oil is very wide, because of the variations of temperature of the engine, and on the other hand the speed range of the pump, directly related to the engine speed, is also very extensive.
  • An oil pump must ensure good lubrication of the engine over its entire operating range and temperature. Moreover, it must be compact, silent, and consume the minimum of energy, low and high temperature.
  • the efficiency of the positive displacement pumps being low in the low and medium speed ranges (approximately up to 2000 revolutions / minute), the pumps must be dimensioned according to this unfavorable operation, and therefore oversized at high speeds.
  • the size of the oil pumps being directly related to their capacity, the pumps are therefore more and more bulky. Moreover, the larger the pumps, the more they are noisy because the amount of pulsed oil in the gears increases with the cubic capacity.
  • the object of the invention is to obtain high flow rates in a dual gear volumetric pump, while keeping a small size.
  • the pump comprises a first communication valve between the first intake chamber and the second discharge chamber, and a second communication valve between the second intake chamber and the first discharge chamber.
  • the pump comprises a single communication valve between the first chamber inlet and second discharge chamber on the one hand, and between the second inlet chamber and the first discharge chamber on the other.
  • the invention also relates to a method for controlling a dual-gear volumetric pump comprising two intake chambers and two discharge chambers depending on its delivery pressure as defined in claim 3.
  • the pump has a first mode of operation in which the intake chambers and the discharge chambers are not in communication, and a second mode of operation in which a portion of the flow discharged by a second gear is returned to the inlet chamber of the first gear.
  • It may also have a third mode of operation in which all the flow delivered by the second gear is discharged to the inlet chamber of the first gear, and a fourth operating mode in which all the flow discharged by the second gear.
  • the gear is pushed back to the inlet chamber of the first gear, and a portion of the flow delivered by the first gear is returned to the intake chamber of the second gear.
  • the pump behaves like a conventional pump with two gears operating in parallel, that is to say with two inlet chambers 4, 7 and two delivery chambers 6, 8.
  • the two valves 17, 18 are closed.
  • the oil enters through the central supply duct 9, and is distributed between the two intake ducts 11, 12.
  • the two pinions 1 and 2 propel the oil towards the first delivery chamber 6, and the two pinions 2 and 3 propel the oil to the second discharge chamber 8. It is then discharged through the conduits 14 and 16 to the central discharge pipe 13.
  • the first valve 17 opens gradually. At least part of the flow from the second chamber discharge 8 being returned to the first inlet chamber 4, the pump is in a first phase of pressure regeneration (cf. figure 2 ), where the increase in pressure as a function of the speed is lower than between 0 and S1.
  • the first valve 17 is fully open and closes the intake duct 11.
  • the pressure supplied by the pump continues to rise with the engine speed. But all the flow of the second gear 2, 3 enters the first inlet chamber 4 (volumetric efficiency close), at a pressure identical to that of the second discharge chamber 8, the pressure losses close. Only one gear pump pumps, so the energy consumption is almost halved, while the pump exhaust pressure increases faster than the speed between S1 and S2.
  • the second valve 18 opens, and at least a portion of the flow of the first discharge chamber 6 is returned to the second intake chamber 7, so that beyond S3, the slope of the curve is more between S2 and S3 (cf. figure 5 ). We are then in a second phase of regeneration of flow.
  • the pump proposed by the invention is therefore a conventional double-gear pump with the particularity of having oil orientation means for short-circuiting one of the discharge pipes to the other inlet chamber at a pressure equal to that of repression.
  • the valve 19 On the figure 6 , corresponding to the first mode of operation, the valve 19 is completely closed. On the figure 7 , corresponding to the second mode of operation, it partially releases the passage between the second discharge chamber and the first inlet chamber. On the figure 8 according to the third mode of operation, this passage is completely open, establishing in the chamber 4 the discharge pressure. Finally, on the figure 9 the valve releases the inlet of the second intake duct 12, and a portion of the flow rate of the first discharge chamber 6 is returned to the second intake chamber 7. With this arrangement, the single valve 19 thus ensures only the functions previously performed by the two valves 17, 18.
  • valve (s) proposed (s) proposed by the invention allows (tent) to bypass one of the pump backs to the inlet at a pressure equal to that of the discharge. This measurement ensures a power saving consumed by the pump in the operating phases thereof where the pressure is high and where the motor does not need the full flow of the pump, for example when the engine is cold.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Rotary Pumps (AREA)

Claims (8)

  1. Verdrängerpumpe mit doppeltem Zahnrad (1, 2; 2, 3), die drei Pumpritzel (1, 2,3), die zwei Ansaugkammern (4, 7) und zwei Druckkammern (6, 8) definieren, eine zentrale Versorgungsleitung (9), die mit zwei Ansaugleitungen (11, 12) verbunden ist, die in die erste bzw. die zweite Ansaugkammer münden, und eine zentrale Abgasleitung (13) aufweist, die zwei Druckleitungen (14, 16) miteinander verbindet, die von der ersten bzw. von der zweiten Druckkammer kommen, und Ausrichtmittel des Druckfluids (17, 18; 19) besitzt, die fähig sind, die Ansaugkammern und die Druckkammern miteinander zu verbinden, um mindestens einen Teil des von der zweiten Druckkammer kommenden Durchsatzes zur ersten Ansaugkammer zurückzuschicken, dadurch gekennzeichnet, dass sie eine erste Verbindungsklappe (17) zwischen der ersten Ansaugkammer (4) und der zweiten Druckkammer (8) und eine zweite verbindungsklappe (18) zwischen der zweiten Ansaugkammer (7) und der ersten Druckkammer (6) aufweist.
  2. Verdrängerpumpe nach dem Oberbegriff des Anspruchs 1, dadurch gekennzeichnet, dass sie eine einzige Verbindungsklappe (19) zwischen der ersten Ansaugkammer (4) und der zweiten Druckkammer (8) einerseits und zwischen der zweiten Ansaugkammer (7) und der ersten Druckkammer (6) andererseits aufweist.
  3. Verfahren zur Steuerung einer Verdrängerpumpe nach Anspruch 1 oder 2, dadurch gekennzeichnet, dass die Pumpe über einen ersten Betriebsmodus, bei dem die Ansaugkammern (4, 7) und die Druckkammern (6, 8) nicht in Verbindung stehen, und über einen zweiten Betriebsmodus verfügt, bei dem mindestens ein Teil des von einem zweiten Zahnrad (2, 3) verdrängten Drucks zur Ansaugkammer (4) des ersten Zahnrads (1) zurückgeschickt wird.
  4. Steuerungsverfahren nach Anspruch 3, dadurch gekennzeichnet, dass die Pumpe über einen dritten Betriebsmodus verfügt, bei dem der ganze vom zweiten Zahnrad (2, 3) verdrängte Druck in die Ansaugkammer (4) des ersten Zahnrads (1, 2) verdrängt wird.
  5. Steuerungsverfahren nach Anspruch 4, dadurch gekennzeichnet, dass die Pumpe über einen vierten Betriebsmodus verfügt, bei dem der ganze vom zweiten Zahnrad (2, 3) verdrängte Druck in die Ansaugkammer (4) des ersten Zahnrads (1, 2) verdrängt wird und ein Teil des von diesem letzteren verdrängten Drucks in die Ansaugkammer (7) des zweiten Zahnrads (2, 3) zurückgeschickt wird.
  6. Steuerungsverfahren nach Anspruch 3, 4 oder 5, dadurch gekennzeichnet, dass der erste Betriebsmodus unterhalb einer ersten Verdrängungsdruckschwelle S1 beibehalten wird, und dass der zweite Betriebsmodus zwischen der ersten Schwelle S1 und einer zweiten Druckschwelle S2 höher als S1 übernommen wird.
  7. Steuerungsverfahren nach Anspruch 4, 5 oder 6, dadurch gekennzeichnet, dass der dritte Betriebsmodus zwischen der zweiten Druckschwelle S2 und einer dritten Druckschwelle S3 höher als S2 übernommen wird.
  8. Steuerungsverfahren nach Anspruch 7, dadurch gekennzeichnet, dass der vierte Betriebsmodus jenseits der dritten Druckschwelle S3 übernommen wird.
EP20020291491 2001-06-15 2002-06-14 Zahnradpumpe mit drei Wellen Expired - Fee Related EP1267077B1 (de)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
FR0107834 2001-06-15
FR0107834A FR2826069B1 (fr) 2001-06-15 2001-06-15 Pompe volumetrique a double engrenage

Publications (2)

Publication Number Publication Date
EP1267077A1 EP1267077A1 (de) 2002-12-18
EP1267077B1 true EP1267077B1 (de) 2008-02-27

Family

ID=8864341

Family Applications (1)

Application Number Title Priority Date Filing Date
EP20020291491 Expired - Fee Related EP1267077B1 (de) 2001-06-15 2002-06-14 Zahnradpumpe mit drei Wellen

Country Status (3)

Country Link
EP (1) EP1267077B1 (de)
DE (1) DE60225207T2 (de)
FR (1) FR2826069B1 (de)

Families Citing this family (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB2397345A (en) * 2003-01-17 2004-07-21 Dana Automotive Ltd A Triple Gear Pump
JPWO2006033207A1 (ja) * 2004-09-22 2008-05-15 株式会社Tbk タンデムポンプの無負荷運転装置
EP2634430B1 (de) 2012-02-28 2018-08-08 Maag Pump Systems AG Getriebepumpenanordnung
CN102926997B (zh) * 2012-10-28 2016-03-16 张意立 一种法兰内螺纹锥形弹簧齿轮泵
RU2536736C1 (ru) * 2013-11-07 2014-12-27 Закрытое Акционерное Общество "Новомет-Пермь" Шестеренный насос для перекачки жидкости
CN107366619A (zh) * 2016-05-13 2017-11-21 王冬 碎化气泡防失压齿轮油泵

Family Cites Families (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
BE549734A (de) *
DE674380C (de) * 1937-02-18 1939-04-13 Ehrich & Graetz Akt Ges Regeleinrichtung fuer Brennstoffoerderpumpen
US2665637A (en) * 1947-05-07 1954-01-12 Borg Warner Pumping system
US4502845A (en) * 1983-03-24 1985-03-05 General Motors Corporation Multistage gear pump and control valve arrangement

Also Published As

Publication number Publication date
DE60225207T2 (de) 2009-03-26
FR2826069B1 (fr) 2004-03-12
EP1267077A1 (de) 2002-12-18
FR2826069A1 (fr) 2002-12-20
DE60225207D1 (de) 2008-04-10

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