EP1644641B1 - Pompe a engrenages a jeu axial optimise - Google Patents

Pompe a engrenages a jeu axial optimise Download PDF

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Publication number
EP1644641B1
EP1644641B1 EP04740962A EP04740962A EP1644641B1 EP 1644641 B1 EP1644641 B1 EP 1644641B1 EP 04740962 A EP04740962 A EP 04740962A EP 04740962 A EP04740962 A EP 04740962A EP 1644641 B1 EP1644641 B1 EP 1644641B1
Authority
EP
European Patent Office
Prior art keywords
pump
ring plate
flange
spacer element
cover
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.)
Not-in-force
Application number
EP04740962A
Other languages
German (de)
English (en)
Other versions
EP1644641A1 (fr
Inventor
Josef Bachmann
Rolf Schwarze
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.)
GKN Sinter Metals Holding GmbH
Original Assignee
GKN Sinter Metals Holding 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 GKN Sinter Metals Holding GmbH filed Critical GKN Sinter Metals Holding GmbH
Priority to PL04740962T priority Critical patent/PL1644641T3/pl
Publication of EP1644641A1 publication Critical patent/EP1644641A1/fr
Application granted granted Critical
Publication of EP1644641B1 publication Critical patent/EP1644641B1/fr
Not-in-force legal-status Critical Current
Anticipated expiration legal-status Critical

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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
    • F04C2/10—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
    • 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
    • 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
    • F04C2/10—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
    • 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
    • F04C2230/00—Manufacture
    • F04C2230/60—Assembly methods
    • F04C2230/602—Gap; Clearance
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F05—INDEXING SCHEMES RELATING TO ENGINES OR PUMPS IN VARIOUS SUBCLASSES OF CLASSES F01-F04
    • F05C—INDEXING SCHEME RELATING TO MATERIALS, MATERIAL PROPERTIES OR MATERIAL CHARACTERISTICS FOR MACHINES, ENGINES OR PUMPS OTHER THAN NON-POSITIVE-DISPLACEMENT MACHINES OR ENGINES
    • F05C2251/00—Material properties
    • F05C2251/04—Thermal properties
    • F05C2251/042—Expansivity
    • F05C2251/046—Expansivity dissimilar

Definitions

  • the invention relates to a pump, in particular oil pump for internal combustion engines, consisting of a pump housing, wherein the pump housing consists of a pump cover and a pump flange, wherein between the pump cover and the pump flange at least one gear set is arranged and the pump cover and the pump flange connected via at least one spacer element are, such as in the publications DE 199 22 792 A1 and US 5,876,192.
  • the hot idling operation is characterized by high internal leakage of the oil pump and a relatively high oil requirement of the engine.
  • the hot idling operation is an essential operating point for the sizing of the oil pump.
  • the oil pump In general, in the classic pump design, the oil pump is designed for this operating point. In normal vehicle operation, this leads to an oversized oil pump, since the ⁇ lschluckline the internal combustion engine degressive over the speed runs, wherein the delivery characteristic of the oil pump increases approximately linearly with the speed. The resulting oversupply of oil is blown off energy-consuming via a pressure relief valve.
  • the axial clearance of the pump is set to 0.07 mm at 20 ° C.
  • the object of the invention is to form a pump having a low in the temperature range from minus 40 ° C to 160 ° C axially changing axial clearance and has a low drop in this temperature range volumetric efficiency.
  • a pump in particular oil pump for internal combustion engines, consisting of a pump housing, wherein the pump housing consists of a pump cover and a pump flange, wherein between the pump cover and the pump flange at least one gear set is arranged and the pump cover and the pump flange over at least one spacer element are connected, wherein the spacer element has a lower thermal expansion coefficient than the pump cover, the pump flange and the gear set.
  • the inventively designed pump allows an improvement in the volumetric efficiency of a pump by 40 to 50% compared to pumps having a pump housing of die-cast aluminum and a gear set made of steel.
  • the volumetric efficiency of the pump according to the invention is about 20 to 25% higher compared to pumps which have a pump housing and a gear set made of steel.
  • the mechanical efficiency is improved at low temperatures.
  • Another advantage is the effect on the pump design as the pump size can be reduced.
  • a reduction of the power consumption and the weight of the pump is possible and, above all, a reduction in fuel consumption. It can be calculated by the inventive design of the pump the optimal axial clearance for almost all pump types with the best possible efficiencies. For many types of pumps, this optimization can be retrofitted cost-effectively.
  • the graph shows that when a steel pump housing is combined with a steel wheel set, the planned axial clearance remains constant over temperature, since the pump housing and the wheel set have an identical thermal expansion coefficient.
  • An optimized in terms of weight pump housing made of die-cast aluminum in combination with a wheel of sintered steel shows the rising at higher temperatures axial play and the consequent internal leakage, which are not desirable.
  • FIG. 7 shows how the volumetric efficiency with increasing pressure and increasing temperatures behaves for a pump produced according to the prior art, the following test conditions being present:
  • Pump housing cast iron Wheel set: sintered steel Wheel set type: Planetary rotor set Wheel set width: 18.00 mm Stroke volume: 5.40 cm 3 / U Medium: ATF gear oil Rotation speed : 500 rpm
  • volumetric efficiency of a pump made according to the prior art at rising pressure at 20 ° C decreases by about 7%.
  • the volumetric efficiency decreases by about 30%.
  • volumetric efficiency of a pump according to the invention falls by only about 7% with increasing pressure and almost independent of the temperature.
  • a pump ring plate is arranged, in which at least one gear set is mounted, wherein the pump ring plate has a larger thermal expansion coefficient than the spacer element.
  • the coefficient of thermal expansion of the spacer element by at least a factor of 10 is smaller than the respective thermal expansion coefficient of the pump cover, the pump flange, the wheelset and the pump ring plate.
  • the thermal expansion coefficient of the spacer element is less than 0.00002 ° C -1 .
  • the spacer element consists of nickel steel, preferably with a share of 36% nickel.
  • the spacer elements is a sintered part.
  • the sintered metallic component may be provided with corresponding alloying elements to obtain a spacer element with a coefficient of thermal expansion tailored to the application.
  • a Planetenrotorsatz is mounted eccentrically, wherein the inner rotor is connected to a drive shaft and the pump cover, the pump ring plate and the pump flange are sealingly separated from each other, wherein spacer elements are provided whose height by the amount the planned axial clearance is greater than the height of the planetary rotor set and the height of the pump ring plate is smaller by the thermal expansion difference amount than the height of the spacer, wherein the existing between pump cover, pump ring plate and pump flange expansion gap is sealed by sealing elements.
  • the pump cover is provided with a collar which projects into the pump ring plate and in the pump ring plate a Planetenrotorsatz is mounted, wherein the pump ring plate is penetrated by at least one spacer element which in contact with the pump cover and the Pump flange is.
  • the pump cover and the pump flange are provided with a collar which projects into the pump ring plate and a Planetenrotorsatz is mounted in the pump ring plate, wherein the pump ring plate is penetrated by at least one spacer element which in contact with the Pump cover and the pump flange is.
  • Figure 1.1 shows a section through a pump housing in plate construction, which consists of a pump cover 2, a pump ring plate 6 and a pump flange 3.
  • a Planetenrotorsatz 4 consisting of an outer rotor 16, planetary rotors 17 and an inner rotor 7, mounted eccentrically.
  • the inner rotor 7 is driven.
  • bearing bores 14 are provided for the spacers 5.
  • O-ring groove 12 is incorporated, in which a sealing ring 11 (O-ring) is inserted, which prevents leakage to the outside.
  • the spacers 5 are tuned to the height of the Planetenrotorsatzes so that the spacers 5 are exactly higher by the amount of the planned axial clearance 24 than the height of the Planetenrotorsatzes 4.
  • the difference in height between spacers 5 and planetary rotor 4 corresponds to the axial clearance 24 at ambient temperature.
  • the pump ring plate 6 is to be tuned with the spacers 5 so that the pump ring plate 6 by the heat expansion amount (coefficient of thermal expansion (pump ring plate) * Height (pump ring plate) * temperature) is smaller than the distance bushes 5. This corresponds to the expansion gap 15.
  • the material for the spacers 5 is chosen so that the coefficient of thermal expansion is always smaller than that of the wheelset 4 and the pump ring plate 6.
  • the wheelset 4 is formed of sintered aluminum Si 14.
  • Figure 1.2 shows that in the pump cover 2 on a partial circle eight through holes 13 and in the pump flange 3 eight threaded holes for a screw by means of screws 14 are introduced.
  • the pump ring plate 6 are provided on the same pitch circle of the pump cover 2 and in the same position as the through holes 13, the bearing bores 14 for the spacer elements, which are designed as spacers 5.
  • Figure 1.3 shows a detail according to Figure 1.1, wherein between the pump cover 2 and the pump flange 3, a pump ring plate 6, a Planetenrotorsatz 4, consisting of an outer rotor 16, planetary rotors 17 and an inner rotor 7, is mounted eccentrically.
  • a pump cover 2 and the pump flange 3 an O-ring groove 12.1, 12.2 is incorporated, in which a sealing ring 11.1, 11.2 (O-ring) is inserted, the leakage prevented to the outside.
  • the spacer element 5 has a greater height than the pump ring plate 6, so that there is an expansion gap 15.1, 15.2.
  • FIG. 2.1 shows a further embodiment of the invention, which achieves the same behavior of the pump 1 according to FIG. This construction is ideal for narrow wheelsets.
  • the pump cover 2 is provided with a collar 18 which projects into the pump ring plate 6.
  • the collar 18 is to be fitted in the pump ring plate 6. Since the pump cover 2 is seated on the spacers 5, the collar length 19 increases at a temperature increase in the direction of wheel 4 and affects the axial clearance 24.
  • the waist length 19 is applied so that over the extension of the waist 19 of the Pump cover 2 needed Axial play 24 sets.
  • the pump cover 2 is made of die-cast aluminum and the gear set of steel or sintered steel.
  • the pump ring plate 6 is made of die-cast aluminum and the spacers 5 made of nickel steel with 36% nickel (Invar).
  • the material of the pump flange 3 has no influence on the expansion in this construction.
  • the thermal expansion coefficient of the Federal 18 should be as high as possible.
  • the pump ring plate can also be made of brass or gunmetal, the coefficient of thermal expansion would be approximately 0.000018 ° C -1 .
  • Figure 3.1 shows a section through a similar construction as Figure 2.1, wherein in this construction, both pumps cover 2 and pump flange 3 with a collar 18.1, 18.2 verses are hen.
  • Pump cover 2 and pump flange 3 should be made of aluminum, or a material with a similar coefficient of thermal expansion. The coefficient of thermal expansion of the Federation 18 should be as high as possible.
  • Figure 4.1 shows a section through a further construction in which the pump ring plate 6 and the pump flange 3 are replaced by a compact pump housing 20.
  • the material of the pump housing 20 may be, for example, cast iron or aluminum die casting.
  • the depth of the bearing bores 21 for the spacers 5 should correspond to the wheelset width 22. By varying the depth of the bearing bores 21 and the corresponding length of the spacers 5 can also influence the axial clearance 24 take.
  • Figure 5.1 shows an embodiment of the invention to Figure 4.1, wherein the depth of the bearing bore 21 and, accordingly, the height of the spacer element is less than the wheelset width 22.
  • the problem arises that the thermal expansion difference between the Material of the wheelset 4 and the spacer element 5 is too large, whereby the axial clearance 24 would go to zero.
  • the spacer element 5 has a lower height than the wheelset width 22.
  • the extension of the spacer element 5 can be calculated as: L ⁇ 2 * Coefficient of thermal expansion casing * temperature + L ⁇ 1 * ( Coefficient of thermal expansion spacer * temperature
  • FIG. 5.2 shows a detail according to FIG. 1.1

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Rotary Pumps (AREA)
  • Details And Applications Of Rotary Liquid Pumps (AREA)

Claims (9)

  1. Pompe (1), en particulier pompe à huile pour moteurs à combustion interne, composée d'un corps de pompe constitué d'un couvercle de pompe (2) et d'une bride de pompe (3), au moins un jeu d'engrenages (4) étant disposé entre le couvercle de pompe (2) et la bride de pompe (3) et le couvercle de pompe (2) et la bride de pompe (3) étant reliés par au moins un élément d'entretoise (5), caractérisée en ce que l'élément d'entretoise (5) présente un coefficient de dilatation thermique plus faible que le couvercle de pompe (2), la bride de pompe (3) et le jeu d'engrenages (4).
  2. Pompe (1) selon la revendication 1, caractérisée en ce qu'entre le couvercle de pompe (2) et la bride de pompe (3) est disposée une plaque annulaire de pompe (6) dans laquelle au moins un jeu d'engrenages (4) est logé, la plaque annulaire de pompe (6) présentant un coefficient de dilatation thermique supérieur à l'élément d'entretoise (5).
  3. Pompe (1) selon la revendication 1 ou 2, caractérisée en ce que le coefficient de dilatation thermique de l'élément d'entretoise (5) est inférieur de l'ordre d'au moins le facteur 10 au coefficient de dilatation thermique respectif du couvercle de pompe (2), de la bride de pompe (3), du jeu de roues (4) et de la plaque annulaire de pompe (6).
  4. Pompe (1) selon l'une quelconque des revendications 1 à 3, caractérisée en ce que le coefficient de dilatation thermique de l'élément d'entretoise (5) est inférieur à 0,0002°C-1.
  5. Pompe (1) selon l'une quelconque des revendications 1, à 4, caractérisée en ce que l'élément d'entretoise (5) est constitué d'acier au nickel, de préférence avec une teneur en nickel de 36 %.
  6. Pompe (1) selon l'une quelconque des revendications 1, à 5, caractérisée en ce que l'élément d'entretoise (5) est une pièce frittée.
  7. Pompe (1) selon l'une quelconque des revendications 1 à 6, caractérisée en ce qu'un jeu de rotors planétaires (4) est disposé excentriquement dans la plaque annulaire de pompe (6), le rotor intérieur (7) étant relié à un arbre d'entraînement (9) et le couvercle de pompe (2), la plaque annulaire de pompe (6) et la bride de pompe (3) étant séparés les uns des autres de manière étanche, dans laquelle des éléments d'entretoise (5) sont prévus dont la hauteur est supérieure à celle du jeu de rotors planétaires (4) de l'ordre du jeu axial prévu, en ce que la hauteur de la plaque annulaire de pompe (6) est inférieure à la hauteur de l'élément d'entretoise (5) de l'ordre du coefficient de dilatation thermique, et dans laquelle la fente de dilatation (10) présente entre le couvercle de pompe (2), la plaque annulaire de pompe (6) et la bride de pompe (3) est rendue étanche par des éléments d'étanchéité (11).
  8. Pompe (1) selon l'une quelconque des revendications 1 à 7, caractérisée en ce que le couvercle de pompe (2) est pourvu d'un épaulement (12) qui fait saillie à l'intérieur de la plaque annulaire de pompe (6) et en ce qu'un jeu de rotors planétaires (4) est logé dans la plaque annulaire de pompe (6), et dans laquelle la plaque annulaire de pompe (6) est traversée par au moins un élément d'entretoise (5) qui est en contact avec le couvercle de pompe (2) et la bride de pompe (3).
  9. Pompe (1) selon l'une quelconque des revendications 1 à 8, caractérisée en ce que le couvercle de pompe (2) et la bride de pompe (3) sont pourvus d'un épaulement (12) qui fait saillie à l'intérieur de la plaque annulaire de pompe (6) et en ce qu'un jeu de rotors planétaires (4) est logé dans la plaque annulaire de pompe (6), et dans laquelle la plaque annulaire de pompe (6) est traversée par au moins un élément d'entretoise (5) qui est en contact avec le couvercle de pompe (2) et la bride de pompe (3).
EP04740962A 2003-07-14 2004-07-12 Pompe a engrenages a jeu axial optimise Not-in-force EP1644641B1 (fr)

Priority Applications (1)

Application Number Priority Date Filing Date Title
PL04740962T PL1644641T3 (pl) 2003-07-14 2004-07-12 Pompa zębata ze zoptymalizowanym luzem osiowym

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE10331979A DE10331979A1 (de) 2003-07-14 2003-07-14 Pumpe mit optimiertem Axialspiel
PCT/EP2004/007729 WO2005005834A1 (fr) 2003-07-14 2004-07-12 Pompe a engrenages a jeu axial optimise

Publications (2)

Publication Number Publication Date
EP1644641A1 EP1644641A1 (fr) 2006-04-12
EP1644641B1 true EP1644641B1 (fr) 2007-05-23

Family

ID=34041874

Family Applications (1)

Application Number Title Priority Date Filing Date
EP04740962A Not-in-force EP1644641B1 (fr) 2003-07-14 2004-07-12 Pompe a engrenages a jeu axial optimise

Country Status (11)

Country Link
US (2) US7713041B2 (fr)
EP (1) EP1644641B1 (fr)
JP (1) JP4489076B2 (fr)
KR (1) KR100777961B1 (fr)
CN (1) CN100564877C (fr)
AT (1) ATE363028T1 (fr)
BR (1) BRPI0412661A (fr)
DE (2) DE10331979A1 (fr)
MX (1) MXPA06000263A (fr)
PL (1) PL1644641T3 (fr)
WO (1) WO2005005834A1 (fr)

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JP4596841B2 (ja) * 2004-07-21 2010-12-15 日立オートモティブシステムズ株式会社 オイルポンプ
JP2008267333A (ja) * 2007-04-24 2008-11-06 Hitachi Ltd オイルポンプ
DE102011107157B4 (de) 2011-07-14 2013-02-28 Geräte- und Pumpenbau GmbH Dr. Eugen Schmidt Zahnringpumpe
DE102013100378A1 (de) * 2013-01-15 2014-07-17 ENVA Systems GmbH Vorrichtung zur Umwandlung von in einem Fluid enthaltener Energie
DE102013016833A1 (de) 2013-10-10 2015-04-16 Daimler Ag Pumpe zum Fördern einer Flüssigkeit, insbesondere eines Schmiermittels einer Verbrennungskraftmaschine für einen Kraftwagen
CN104373345B (zh) * 2014-10-15 2017-08-08 哈尔滨东安发动机（集团）有限公司 一种优化轴向间隙的滑油泵
US10337510B2 (en) * 2017-02-03 2019-07-02 Ford Global Technologies, Llc Wear-resistant coating for oil pump cavity
US11614158B2 (en) * 2020-07-13 2023-03-28 GM Global Technology Operations LLC Hydraulic Gerotor pump for automatic transmission
US11661938B2 (en) * 2021-08-31 2023-05-30 GM Global Technology Operations LLC Pump system and method for optimized torque requirements and volumetric efficiencies

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Also Published As

Publication number Publication date
BRPI0412661A (pt) 2006-09-26
JP4489076B2 (ja) 2010-06-23
EP1644641A1 (fr) 2006-04-12
MXPA06000263A (es) 2006-07-03
DE10331979A1 (de) 2005-02-17
US20100239449A1 (en) 2010-09-23
DE502004003895D1 (de) 2007-07-05
KR100777961B1 (ko) 2007-11-21
WO2005005834A1 (fr) 2005-01-20
US7887309B2 (en) 2011-02-15
CN100564877C (zh) 2009-12-02
KR20060038444A (ko) 2006-05-03
CN1823224A (zh) 2006-08-23
US20060140811A1 (en) 2006-06-29
JP2009513859A (ja) 2009-04-02
ATE363028T1 (de) 2007-06-15
US7713041B2 (en) 2010-05-11
PL1644641T3 (pl) 2007-09-28

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