EP1462654B1 - Pompe à engrenages - Google Patents

Pompe à engrenages Download PDF

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Publication number
EP1462654B1
EP1462654B1 EP04450056A EP04450056A EP1462654B1 EP 1462654 B1 EP1462654 B1 EP 1462654B1 EP 04450056 A EP04450056 A EP 04450056A EP 04450056 A EP04450056 A EP 04450056A EP 1462654 B1 EP1462654 B1 EP 1462654B1
Authority
EP
European Patent Office
Prior art keywords
gear
pressure
pump
gear pump
shiftable
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
EP04450056A
Other languages
German (de)
English (en)
Other versions
EP1462654A1 (fr
Inventor
Alfred Götschhofer
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.)
TCG Unitech Systemtechnik GmbH
Original Assignee
TCG Unitech Systemtechnik 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 TCG Unitech Systemtechnik GmbH filed Critical TCG Unitech Systemtechnik GmbH
Priority to AT04450056T priority Critical patent/ATE307293T1/de
Priority to PL04450056T priority patent/PL1462654T3/pl
Publication of EP1462654A1 publication Critical patent/EP1462654A1/fr
Application granted granted Critical
Publication of EP1462654B1 publication Critical patent/EP1462654B1/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
    • F04C14/18—Control of, monitoring of, or safety arrangements for, machines, pumps or pumping installations characterised by varying the volume of the working chamber
    • F04C14/185—Control of, monitoring of, or safety arrangements for, machines, pumps or pumping installations characterised by varying the volume of the working chamber by varying the useful pumping length of the cooperating members in the axial direction
    • 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
    • F04C15/0003—Sealing arrangements in rotary-piston machines or pumps
    • F04C15/0023—Axial sealings for working fluid
    • F04C15/0026—Elements specially adapted for sealing of the lateral faces of intermeshing-engagement type machines or pumps, e.g. gear machines or 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
    • 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

Definitions

  • the invention relates to a gear pump with variable delivery volume two externally toothed gears meshing with each other which mesh are rotatably mounted in a pumping chamber of a pump housing, wherein at least one of the two gears is drivable via a drive shaft and one of the two gears, preferably the aborted gear, in the direction the axis of this gear is designed to be displaceable.
  • Gear pumps with two intermeshing externally toothed Gears have a gear driven by a drive shaft on which drives the second gear.
  • the gear engagement width is decisive for the volume flow of the Pumped fluid through the gear pump decisive. Losses by the head play of the gears to the pump housing and by the play of the Spaltshuses arise at the ends of the gears are in efficiency the gear pump reflected.
  • Gear pumps of this type are usually used for oil pumps of internal combustion engines.
  • conventional Oil pumps are powered by a rigid, non-variable drive such as chain, gears, Timing belt, etc. in a fixed speed ratio with the crankshaft of the Motors coupled.
  • Oil pumps are generally used in the worst case of oil supply the internal combustion engine over the entire speed field designed, the is the idle speed with the largest gap cross section in the bearing points, inclusive all other consumers on the engine such as pistons, spray nozzle for piston cooling or turbocharger, etc. From this interpretation it follows that the oil pump at higher speeds of the internal combustion engine over a multiple of the need Promotes oil quantity for high engine speeds.
  • the quantity regulation to the actual Consumption of the respective engine operating state is usually carried out by pressure control and Ab juryn the excess amount of oil delivered in the oil sump, or by returning it to the suction channel of the pump. Because the Gears of the pump thus always promote the maximum amount of oil must be independent from the actual need always approximately the same high drive power to be provided. This has a disadvantageous effect on the efficiency.
  • a gear pump with adjustable displacement is a gear pump with adjustable displacement known.
  • a gear of the gear pump has openings, which extending from a coaxial bore to the tooth spaces.
  • a rotary valve with at least one web which is a partially cylindrical Has lateral surface and defines an axial recess on the rotary valve, rotatably mounted on a gear carrying a shaft.
  • the jetty is with its lateral surface in the inside of the bore and the recess is connected to the low pressure side of the pump.
  • the delivery volume by changing the meshing width to adjust.
  • at least one of the two gears in shifted axially and thus the meshing width are changed, which are partly in the tooth gaps engaging patches necessary to To avoid dead spaces.
  • Such gear pumps are for example from the GB 2 265 945 A, AT 003 767 U1, DE 41 21 074 A1 or the RU 2 177 085 C known.
  • the gear pump Relatively much space through the axial gear adjustment to complete takes.
  • US 2,434,135 A discloses a gear pump with an externally toothed Gear, which is in engagement with an internally toothed gear. By Moving the externally toothed gear and / or the internally toothed Gear, the delivery volume can be changed because the outlet side with the inlet side is shorted. On gear pumps with two externally toothed Gears, this concept is not readily transferable.
  • the object of the invention is the simplest possible way in a gear pump of the type mentioned to achieve a regulation of the delivery volume.
  • a through the in the axial direction measured distance between a substantially planar first inner side wall the delivery chamber of the pump housing and a first end face of the displaceable gear defined gap is variable and that a the first inner side wall opposite and parallel to this plane second inner side wall of the delivery chamber in the region of one of the first end face remote from the second end face of the sliding gear concentric Has formed to the axis, substantially cylindrical recess, whose Diameter at least in the region of the sliding gear larger than the Outer diameter of the gear is.
  • the gap in a range between 0 to d / 5, preferably in a range between 0 to d / 50 is variable, wherein d is the outer diameter of the sliding gear.
  • the regulation of the delivery volume is mainly by changing the gap size and thus the gap losses. filler for filling the dead spaces, which intervene, for example, in the tooth gaps, are not necessary.
  • the pressure or flow control over the Change in the gap size satisfy extremely low axial displacements, because the gap greatly influences the pressure and flow rate of the gear pump.
  • a preferably plate-shaped Sealing disc is arranged, which the conveying space of the pump housing separates from a dead space within the niche, preferably the Sealing disc rotatably connected to the sliding gear.
  • the preferably plate-shaped sealing disc is a lateral seal allows for the dead space.
  • the sealing disc facing on the second end face Side in the region of each interdental space of the sliding gear at least having a radial relief groove.
  • the pressure and flow rate control takes place in the described gear pump completely without control piston or valves, whereby a very compact construction can be achieved.
  • the gear pump in the control range also has a significant lower power consumption. Due to the extremely low displacement of Gears are almost always supporting the teeth all over the tooth flank, causing they are subject to much less wear than the tooth mesh width regulated gear pumps.
  • the dead space via a discharge channel with a pressure sink preferably fluidly connectable to the suction side or the pump environment is, preferably in the discharge channel in the direction of Pressure sink opening pressure relief valve is arranged.
  • the pressure relief valve has the task to prevent a pressure increase in the dead space. Thereby can avoid a malfunction of the control characteristics of the gear pump be, especially in cold run and in radially closed Sealing is important.
  • the sealing disc has at least one circumferential sealing groove in its jacket region. Due to the circumferential sealing groove can be dispensed with radial relief grooves become.
  • a simple shift of the gear can be achieved when the sliding Gear, preferably also the sealing disc, rigid on a in Pump housing rotatable and adjustable in the direction of the axis control shaft is arranged.
  • the control shaft for axial adjustment at least one pressure piston which is connected to a pressure chamber which can be connected to a pressure medium borders, wherein preferably the pressure medium through the fluid is formed and the pressure chamber fluidly connected to the pressure side of the gear pump is.
  • the Pressure chamber with an external pressure source or a pure oil control device, connected is. This allows external control.
  • the default the control shaft can be trained on a trained example as a compression spring Return spring take place.
  • the control shaft, at least in one direction, by an electric servomotor is adjustable.
  • the gear pump 1 has two meshing, externally toothed Gears 2, 3, which in a delivery chamber 11 of a pump housing 4 are rotatably arranged.
  • the gear 3 is via a drive shaft. 5 driven and drives the gear 2.
  • the aborted gear 2 is together arranged with a sealing disc 6 on a control shaft 7 and can be moved with this in the direction of the axis 2 'of the gear 2, as with the arrow P is indicated.
  • reference numeral 8 is the suction side, with reference numerals 9, the pressure side of the gear pump 1 and the arrows S, the flow direction of the medium.
  • the gap 10 shown in FIG. 3 can be changed.
  • the gap 10 is as a distance between a flat first inner side wall 11a of the delivery chamber 11 of the pump housing 4 and a first end face 2a of the displaceable Gear 2 defined.
  • With the outer diameter d of the sliding Gear 2 is the adjustment range of the gap 10 between 0 to d / 5, preferably between 0 to d / 50, wherein the rest state shown in Fig. 2 a minimum, design-related value for the gap 10 assigned is.
  • the regulation of the pressure or the flow rate is on the gap 10 and thus accomplished by changing the gap losses. This can be up Pockets, in particular for filling the interdental spaces 14, are dispensed with. Even a slight displacement of the displaceable gear 2 is sufficient to change the gap 10 sufficiently.
  • the arranged in the niche 22 plate or annular sealing disc 6 is used to the the gear wheels 2, 3 receiving delivery chamber 11 of a for Displacement of the gear 2 necessary dead space 12 within the niche 22nd seal.
  • This is via a in Figs. 2 and 3 and Fig. 4 and 5 dashed lines relief channel 25 connected to a pressure sink, which the suction chamber 8 or the pump environment, such as the oil space of an oil pan, may be.
  • in the Relief channel 25 is a pressure relief valve opening in the direction of the pressure sink 26 arranged.
  • the sealing disc 6 has tooth space symmetry arranged radial relief grooves 13 on the side of the first Front side 2a facing away from the second end face 2b of the movable gear. 2 on.
  • Each radial relief groove 13 is in each case in the region of a tooth gap 14 of the sliding gear 2 is arranged and communicates during one revolution of the displaceable gear 2 with an outlet groove 15, which in the pressure-side engagement region 23 of the two gears 2, 3 in the Pump housing 4 is formed.
  • radial relief grooves 13 can be largely dispensed with if the Sealing disc 6, as shown in Fig. 6, in its jacket region with at least a circumferential sealing groove 27 is provided which as a labyrinth seal acts and compensates for pressure peaks.
  • the indicated by reference numeral 29 Leckagenut has the task in the Dead space 12 through the annular gap between the sealing disc 6 and pump housing 4 leak leaks to the outside.
  • the leakage groove 29 is for example designed spirally and connects the dead space 12 with a spring chamber 30. In order to discharge leaks reliably in normal operation, is the sum of the cross-sectional areas of bearing clearance of the control shaft 7 and the leakage groove 29 at least as large as the annular gap between the sealing disc 6 and pump housing 4.
  • the control shaft 7 has a pressure piston 17, which is the pump housing cover 4a is sealed off via the seal 18.
  • the pressure piston 17 is adjacent to a pressure chamber 19, which closed by the screw 20 is.
  • a Drucköleinberg 21 which with the pressure side 9 of the gear pump 1 is fluidly connected (Fig. 2, 3), or which with an external pressure source or a so-called pure oil control (oil pressure, is taken after the oil filter), in communication (Fig. 4, 5).
  • a so-called pure oil control oil pressure, is taken after the oil filter
  • Fig. 4, 5 so-called pure oil control
  • the return to the normal position takes place via a in the spring chamber 30 arranged return spring 28, for example, a compression spring, or an electric servomotor.
  • the deflection of the control shaft 7 in the control position instead of by the pump pressure also by take the electric servomotor.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Rotary Pumps (AREA)
  • Details And Applications Of Rotary Liquid Pumps (AREA)
  • Lubrication Of Internal Combustion Engines (AREA)
  • Valve Device For Special Equipments (AREA)
  • Valve-Gear Or Valve Arrangements (AREA)

Claims (15)

  1. Pompe à engrenage (1) à débit volumique variable comprenant deux pignons dentés (2, 3) à denture extérieure en prise (23) l'un avec l'autre, ces pignons étant montés à rotation dans une chambre de transfert (11) d'un boítier de pompe (4),
    au moins l'un des deux pignons dentés (3) étant entraíné par l'intermédiaire d'un arbre d'entraínement (5) et l'un des deux pignons (2), de préférence le pignon entraíné (2) est coulissant dans la direction de son axe (2'),
    une mesure d'intervalle (10) définie par la distance mesurée dans la direction axiale entre une première paroi latérale intérieure (11a) essentiellement plane de la chambre de refoulement (11) du boítier de pompe (4) et une première face frontale (2a) du pignon coulissant (2) est variable,
    caractérisée en ce qu'
    une seconde paroi latérale intérieure (11b) de la chambre de refoulement (11), plane, en regard de la première paroi latérale intérieure (1la) et parallèle à celle-ci, présente dans la zone de la seconde face frontale (2b) du pignon coulissant (2), non tournée vers la première face frontale (2a), une niche principalement cylindrique (22) concentrique à l'axe (2') et dont le diamètre (D) est plus grand que le diamètre extérieur (d) du pignon denté (2) au moins au niveau de ce pignon coulissant (2).
  2. Pompe à engrenage (1) selon la revendication 1,
    caractérisée en ce que
    la mesure de l'intervalle (10) est variable dans une plage comprise entre 0 et d/5, de préférence dans une plage comprise entre 0 et d/50, (d) étant le diamètre extérieur du pignon coulissant (2).
  3. Pompe à engrenage (1) selon la revendication 1 ou 2,
    caractérisée en ce qu'
    au niveau de la niche (22) se situe un joint d'étanchéité (6), de préférence en forme de coupelle, qui sépare la chambre de refoulement (11) du boítier de pompe (4) d'un volume mort (12) dans la niche (22) par rapport à la chambre de transfert (11),
    de préférence la rondelle d'étanchéité (6) est reliée solidairement au pignon coulissant (2).
  4. Pompe à engrenage (1) selon la revendication 3,
    caractérisée en ce que
    la rondelle d'étanchéité (6) présente une rainure de décharge radiale (13) sur le côté tourné vers la seconde face frontale (2b) au niveau de chaque intervalle de dents (14) du pignon coulissant (2).
  5. Pompe à engrenage (1) selon la revendication 4,
    caractérisée en ce qu'
    au niveau de l'engrènement (23) des deux pignons (2, 3), côté pression, sur le côté de la rondelle d'étanchéité (6), la première paroi latérale intérieure (11a) comporte un regard de la seconde paroi latérale intérieure (11b) de la chambre de transfert (11), une rainure de sortie (15) disposée pour que pendant une rotation de la rondelle d'étanchéité (6), chaque rainure de décharge (13) communique au moins une fois avec la rainure de sortie (15).
  6. Pompe à engrenage (1) selon l'une des revendications 3 à 5,
    caractérisée en ce que
    le volume mort (12) est relié à un canal de fuite.
  7. Pompe à engrenage (1) selon la revendication 6,
    caractérisée en ce que
    le canal de fuite est formé par une rainure de fuite (29), de préférence en forme d'hélice, réalisée dans le corps de pompe (4) de façon adjacente à l'arbre de réglage (7).
  8. Pompe à engrenage (1) selon l'une des revendications 3 à 7,
    caractérisée en ce que
    le volume mort (12) est relié par un canal de décharge (25) à un puits de pression, de préférence côté aspiration (8) ou à l'environnement de la pompe par une liaison de fluide,
    et de préférence le canal de décharge (25) comporte une soupape de décharge de pression (26) s'ouvrant en direction du côté du puits de pression.
  9. Pompe à engrenage (1) selon l'une des revendications 3 à 8,
    caractérisée en ce que
    la rondelle d'étanchéité (6) comporte au moins une rainure d'étanchéité (27) périphérique dans sa zone enveloppe.
  10. Pompe à engrenage (1) selon l'une des revendications 1 à 9,
    caractérisée en ce que
    le pignon coulissant (2), et de préférence la rondelle d'étanchéité (6), sont installés solidairement en rotation sur un axe de réglage (7) coulissant dans la direction de l'axe (2') et tournant dans le corps de pompe (4).
  11. Pompe à engrenage (1) selon la revendication 10,
    caractérisée en ce que
    l'axe de réglage (7) comporte au moins un piston de pression (17) pour le réglage axial, ce piston délimitant une chambre de pression (19) communiquant avec un fluide sous pression.
  12. Pompe à engrenage (1) selon la revendication 11,
    caractérisée en ce que
    le fluide sous pression est constitué par le fluide refoulé et la chambre de pression (19) communique avec le côté de pression (9) de la pompe à engrenage (1).
  13. Pompe à engrenage (1) selon la revendication 11,
    caractérisée en ce que
    la chambre de pression (19) est reliée à une source de pression externe ou à une installation de commande d'huile nettoyée.
  14. Pompe à engrenage (1) selon l'une des revendications 8 à 13,
    caractérisée en ce qu'
    un ressort de rappel agit sur l'arbre de réglage (7) contre la direction de débattement par le piston de pression (17).
  15. Pompe à engrenage (1) selon l'une des revendications 8 à 14,
    caractérisée en ce que
    l'arbre de réglage (7) est réglable au moins dans une direction par un moteur de réglage électrique.
EP04450056A 2003-03-28 2004-03-11 Pompe à engrenages Expired - Lifetime EP1462654B1 (fr)

Priority Applications (2)

Application Number Priority Date Filing Date Title
AT04450056T ATE307293T1 (de) 2003-03-28 2004-03-11 Zahnradpumpe
PL04450056T PL1462654T3 (pl) 2003-03-28 2004-03-11 Pompa zębata

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
AT4932003 2003-03-28
AT0049303A AT413140B (de) 2003-03-28 2003-03-28 Zahnradpumpe

Publications (2)

Publication Number Publication Date
EP1462654A1 EP1462654A1 (fr) 2004-09-29
EP1462654B1 true EP1462654B1 (fr) 2005-10-19

Family

ID=32777542

Family Applications (1)

Application Number Title Priority Date Filing Date
EP04450056A Expired - Lifetime EP1462654B1 (fr) 2003-03-28 2004-03-11 Pompe à engrenages

Country Status (7)

Country Link
US (1) US7137798B2 (fr)
EP (1) EP1462654B1 (fr)
JP (1) JP2004301125A (fr)
AT (2) AT413140B (fr)
DE (1) DE502004000102D1 (fr)
ES (1) ES2247580T3 (fr)
PL (1) PL1462654T3 (fr)

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JP2007514097A (ja) * 2003-12-10 2007-05-31 フォイクト・ディーター オイルポンプの回転数依存型圧力制御
DE102004026048A1 (de) * 2004-05-25 2005-12-29 Cor Pumps + Compressors Ag Spaltverluststromsteuerung
US8302353B2 (en) 2004-10-15 2012-11-06 Thomas Bren Water intrusion prevention method and apparatus
CA2588811C (fr) * 2004-12-22 2014-01-21 Magna Powertrain Inc. Pompe type gerotor a cylindree variable
US20070201989A1 (en) * 2005-10-14 2007-08-30 Parker-Hannifin Low ripple gear pump/motor
US7717690B2 (en) * 2006-08-15 2010-05-18 Tbk Co., Ltd. Gear pump
BRPI1001768A2 (pt) * 2010-05-24 2012-01-24 Jose Luiz Bertazzolli transmissão continuamente variável
DE102010038430B4 (de) 2010-07-26 2012-12-06 Schwäbische Hüttenwerke Automotive GmbH Verdrängerpumpe mit Absaugnut
JP5909966B2 (ja) * 2011-09-30 2016-04-27 株式会社Ｌｉｘｉｌ ポンプ及び洗浄装置
RU2511848C1 (ru) * 2012-11-06 2014-04-10 Анатолий Константинович Маришкин Регулируемый шестеренный насос
CN105041639A (zh) * 2015-08-27 2015-11-11 刘凡 一种外啮合变量齿轮泵
US10113546B2 (en) 2016-08-16 2018-10-30 Caterpillar Inc. Pump for an engine
CN110069898B (zh) * 2019-05-30 2023-02-07 河南航天液压气动技术有限公司 一种齿轮泵设计容积效率计算的方法
CN110608130B (zh) * 2019-10-12 2024-03-26 山东路得威工程机械制造有限公司 一种高速液压马达

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DE3528651A1 (de) * 1985-08-09 1987-02-19 Rohs Hans Guenther Prof Dr Ing Zahnradpumpe
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JPH11343982A (ja) * 1998-05-30 1999-12-14 Suzuki Motor Corp トロコイド型オイルポンプ
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RU2177085C2 (ru) * 1999-05-07 2001-12-20 Бодогазин Сергей Борисович Насос шестеренный регулируемый
DE19924057A1 (de) * 1999-05-26 2000-11-30 Bosch Gmbh Robert Zahnradmaschine (Pumpe oder Motor)

Also Published As

Publication number Publication date
US7137798B2 (en) 2006-11-21
ATA4932003A (de) 2005-04-15
DE502004000102D1 (de) 2006-03-02
ES2247580T3 (es) 2006-03-01
JP2004301125A (ja) 2004-10-28
PL1462654T3 (pl) 2005-12-30
EP1462654A1 (fr) 2004-09-29
ATE307293T1 (de) 2005-11-15
AT413140B (de) 2005-11-15
US20040191103A1 (en) 2004-09-30

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