EP1644641B1 - Gear pump having optimal axial play - Google Patents
Gear pump having optimal axial play Download PDFInfo
- 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.)
- Expired - Lifetime
Links
- 238000002485 combustion reaction Methods 0.000 claims abstract description 5
- 125000006850 spacer group Chemical group 0.000 claims description 51
- PXHVJJICTQNCMI-UHFFFAOYSA-N Nickel Chemical compound [Ni] PXHVJJICTQNCMI-UHFFFAOYSA-N 0.000 claims description 35
- 229910000831 Steel Inorganic materials 0.000 claims description 31
- 239000010959 steel Substances 0.000 claims description 31
- 229910052759 nickel Inorganic materials 0.000 claims description 18
- 238000007789 sealing Methods 0.000 claims description 4
- 229910052782 aluminium Inorganic materials 0.000 description 14
- XAGFODPZIPBFFR-UHFFFAOYSA-N aluminium Chemical compound [Al] XAGFODPZIPBFFR-UHFFFAOYSA-N 0.000 description 14
- 239000003921 oil Substances 0.000 description 14
- 229910001374 Invar Inorganic materials 0.000 description 13
- 239000000463 material Substances 0.000 description 9
- 238000010276 construction Methods 0.000 description 8
- 230000007423 decrease Effects 0.000 description 5
- 239000012208 gear oil Substances 0.000 description 4
- 230000000694 effects Effects 0.000 description 3
- 238000005461 lubrication Methods 0.000 description 3
- 229910001018 Cast iron Inorganic materials 0.000 description 2
- 230000003247 decreasing effect Effects 0.000 description 2
- 239000000446 fuel Substances 0.000 description 2
- 238000005457 optimization Methods 0.000 description 2
- 230000000630 rising effect Effects 0.000 description 2
- 229910001369 Brass Inorganic materials 0.000 description 1
- 229910001060 Gray iron Inorganic materials 0.000 description 1
- 238000005275 alloying Methods 0.000 description 1
- 239000010951 brass Substances 0.000 description 1
- 230000002950 deficient Effects 0.000 description 1
- 230000006866 deterioration Effects 0.000 description 1
- 238000004512 die casting Methods 0.000 description 1
- 238000005265 energy consumption Methods 0.000 description 1
- 230000007257 malfunction Effects 0.000 description 1
- 238000004513 sizing Methods 0.000 description 1
- 210000002023 somite Anatomy 0.000 description 1
Images
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)
Abstract
Description
Die Erfindung betrifft eine Pumpe, insbesondere Ölpumpe für Verbrennungsmotoren, bestehend aus einem Pumpengehäuse, wobei das Pumpengehäuse aus einem Pumpendeckel und einem Pumpenflansch besteht, wobei zwischen dem Pumpendeckel und dem Pumpenflansch wenigstens ein Zahnradsatz angeordnet ist und der Pumpendeckel und der Pumpenflansch über wenigstens ein Distanzelement verbunden sind, wie z.B. in den Druckschriften DE 199 22 792 A1 und US 5 876 192 offenbart.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.
Die Entwicklung von Automobilen mit niedrigen Kraftstoffverbräuchen erfordert die Optimierung von Fahrzeug- und Motorenkomponenten. Für den Kraftfahrzeugenergieverbrauch im häufig auftretenden Kurzstrecken- und Stadtverkehr sind hierbei die Verluste, die unter anderem durch den Antrieb von Nebenaggregaten bedingt sind, von besonderer Bedeutung. Die Antriebsleistung von unter anderem Ölpumpen, die die Motorschmierung sicherstellen, können zu einer Verringerung der eigentlichen Motorleistung führen, wodurch der Kraftstoffverbrauch stark ansteigt.The development of low-consumption automobiles requires the optimization of vehicle and engine components. For the motor vehicle energy consumption in frequently occurring short-distance and city traffic here are the losses, which are caused inter alia by the drive of ancillaries, of particular importance. The power of, inter alia, oil pumps, which ensure the engine lubrication, can lead to a reduction in the actual engine performance, which fuel consumption increases sharply.
Bei bis zu minus 40°C muß die Funktion der Motorschmierung und eine ausreichend schnelle Motorschmierung gewährleistet werden und im heißen Leerlaufbetrieb bis zu 160°C darf die Ölversorgung keinen Mangel aufweisen. Der Heißleerlaufbetrieb ist gekennzeichnet durch hohe innere Leckagen der Ölpumpe und einen relativ hohen Ölbedarf des Motors. Der Heißleerlaufbetrieb ist ein wesentlicher Betriebspunkt für die Dimensionierung der Ölpumpe.Up to minus 40 ° C, the function of the engine lubrication and a sufficiently fast engine lubrication must be guaranteed and in hot idle operation up to 160 ° C, the oil supply must not be deficient. 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.
Im allgemeinen wird bei der klassischen Pumpenauslegung die Ölpumpe für diesen Betriebspunkt ausgelegt. Im normalen Fahrzeugbetrieb führt dies zu einer überdimensionierten Ölpumpe, da die Ölschlucklinie des Verbrennungsmotors degressiv über die Drehzahl verläuft, wobei die Förderkennlinie der Ölpumpe näherungsweise linear mit der Drehzahl ansteigt. Das hieraus resultierende Überangebot an Öl wird über ein Überdruckbegrenzungsventil energieverzehrend abgeblasen.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 Ölschlucklinie 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.
Die vorstehend beschriebene Problematik wird dadurch verstärkt, daß insbesondere die Automobilindustrie den Einsatz dünnflüssigerer Öle wünscht. Hierdurch wird zwar die Funktion von Pumpen bei Minustemperaturen verbessert, wobei der volumetrische Wirkungsgrad bei hohen Temperaturen verschlechtert wird.The problem described above is compounded by the fact that in particular the automotive industry desires the use of less viscous oils. Although this improves the function of pumps at minus temperatures, the volumetric efficiency at high temperatures is degraded.
Ein weiteres Problem besteht darin, daß fast alle Pumpengehäuse aus im Vergleich zu den eingesetzten Zahnradsätzen unterschiedlichen Materialien gefertigt werden. Eine Vielzahl von Pumpengehäusen wird beispielsweise aus Gründen der Gewichtsersparnis aus Aluminium Druckguß hergestellt, wohingegen die Zahnradsätze aus Stahl, insbesondere Sinterstahl hergestellt werden. Aufgrund der unterschiedlichen Wärmeausdehnungskoeffizienten des Pumpengehäuses und der Zahnradsätze ergibt sich, daß das notwenige geplante Axialspiel zwischen Zahnradsatz und Pumpengehäuse sich bei Temperaturerhöhung und/oder -erniedrigung verändert. Bei einer Temperaturerhöhung erfolgt eine ungefähr lineare Erhöhung des Axialspiels, so daß weitere Verluste des volumetrischen Wirkungsgrades erfolgen, welche 50 bis 60 % betragen können. Der volumetrische Wirkungsgrad einer Pumpe sinkt ungefähr linear bei steigenden Temperaturen.Another problem is that almost all pump housings are made of different materials compared to the gear sets used. A variety of pump housings is made, for example, for reasons of weight savings from die-cast aluminum, whereas the gear sets are made of steel, especially sintered steel. Due to the different coefficients of thermal expansion of the pump housing and the gear sets results that the necessary planned axial clearance between gear set and pump housing changes with temperature increase and / or decrease. With a temperature increase, an approximately linear increase of the axial play, so that further losses of the volumetric efficiency takes place, which can be 50 to 60%. The volumetric efficiency of a pump decreases approximately linearly with increasing temperatures.
Die vorstehend beschriebene Problematik wird vertiefend am Beispiel einer Flügelzellenpumpe mit folgenden Kennwerten dargestellt:
Das Axialspiel der Pumpe wird auf 0,07 mm bei 20°C ausgelegt.The axial clearance of the pump is set to 0.07 mm at 20 ° C.
Temperaturdifferenz 130° C (20°C bis 150°C):
- Ausdehnung Aluminium-Gehäuse:
- Ausdehnung Sinterstahlradsatz:
- Extension aluminum housing:
- Expansion of sintered steel wheelset:
Das ergibt ein Axialspiel von 0.143mm.This results in an axial play of 0.143mm.
Temperaturdifferenz 60°C (-40°C bis 20°C):
- Schrumpfung Aluminium-Gehäuse:
- Schrumpfung Sinterstahlradsatz:
- Shrinkage aluminum housing:
- Shrinkage sintered steel wheelset:
Das ergibt ein Axialspiel von 0.037 mm.This results in an axial clearance of 0.037 mm.
Durch die unterschiedliche Wärmeausdehnung der Werkstoffe, vergrößert sich das Axialspiel bei 150°C auf 0.143 mm und verkleinert sich bei 40°C auf 0.037 mm. Eine Verdoppelung des Axialspiels und eine Verringerung der Viskosität des Mediums führt zu einem volumetrischen Wirkungsgradverlusten von 50 bis 60%. Bei niedrigen Temperaturen kann es durch die Verkleinerung des Axialspiels zu Funktionsstörungen und zu erheblicher Verschlechterung des mechanischen Wirkungsgrades kommen. 0.01 mm Axialspielzunahme bedeutet ca. 1Liter/min Förderstromabnahme bei 100°C, 5.5bar, 550 U/min (Aussage TV-H Nov. 98). Bei der Auslegung einer Ölpumpe müssen diese volumetrischen Verluste berücksichtigt werden und die Pumpe entsprechend größer ausgelegt werden. Durch die größer ausgelegte Pumpe kommt es bei höheren Drehzahlen zu einem Überangebot an Öl das leistungsverzehrend abgeführt werden muß. Aufgabe der Erfindung ist es, eine Pumpe zu bilden, die ein im Temperaturbereich von minus 40°C bis 160°C sich gering änderndes Axialspiel aufweist und eine über diesen Temperaturbereich nur gering abfallenden volumetrischen Wirkungsgrad aufweist.Due to the different thermal expansion of the materials, the axial clearance increases to 0.143 mm at 150 ° C and decreases to 0.037 mm at 40 ° C. Doubling the axial play and decreasing the viscosity of the medium results in a volumetric efficiency loss of 50 to 60%. At low temperatures, the reduction of axial play can lead to malfunctions and a considerable deterioration of the mechanical efficiency. 0.01 mm Axialspielzunahme means about 1 liter / min flow reduction at 100 ° C, 5.5bar, 550 rev / min (statement TV-H Nov. 98). When designing an oil pump, these volumetric losses must be taken into account and the pump designed accordingly larger. Due to the larger design Pump occurs at higher speeds to an oversupply of oil that must be dissipated consuming power. 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.
Die Aufgabe wird erfindungsgemäß gelöst, durch eine Pumpe, insbesondere Ölpumpe für Verbrennungsmotoren, bestehend aus einem Pumpengehäuse, wobei das Pumpengehäuse aus einem Pumpendeckel und einem Pumpenflansch besteht, wobei zwischen dem Pumpendeckel und dem Pumpenflansch wenigstens ein Zahnradsatz angeordnet ist und der Pumpendeckel und der Pumpenflansch über wenigstens ein Distanzelement verbunden sind, wobei das Distanzelement einen geringeren Wärmeausdehnungskoeffizienten aufweist als der Pumpendeckel, der Pumpenflansch und der Zahnradsatz.The object is achieved by 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.
Die erfindungsgemäß gestaltete Pumpe ermöglicht eine Verbesserung des volumetrischen Wirkungsgrads einer Pumpe um 40 bis 50% gegenüber Pumpen, die ein Pumpengehäuse aus Aluminium-Druckguß und einen Zahnradsatz aus Stahl aufweisen. Der volumetrische Wirkungsgrad der erfindungsgemäßen Pumpe ist um ca. 20 bis 25% höher gegenüber Pumpen, die ein Pumpengehäuse und einen Zahnradsatz aus Stahl aufweisen. Des weiteren wird bei niedrigen Temperaturen der mechanische Wirkungsgrad verbessert. Ein weiterer Vorteil besteht bezüglich der Auswirkung auf die Pumpenauslegung, da die Pumpengröße reduziert werden kann. Ferner ist eine Reduzierung der Leistungsaufnahme und des Gewichtes der Pumpe möglich und vor allem eine Reduzierung des Kraftstoffverbrauchs. Es läst sich durch die erfindungsgemäße Gestaltung der Pumpe das optimale Axialspiel für fast alle Pumpenarten mit den bestmöglichen Wirkungsgraden berechnen. Bei vielen Pumpentypen ist diese Optimierung kostengünstig nachrüstbar.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. Furthermore, the mechanical efficiency is improved at low temperatures. Another advantage is the effect on the pump design as the pump size can be reduced. Furthermore, 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.
Die Vorteile der erfindungsgemäßen Gestaltung der Pumpe werden am Beispiel der im Stand der Technik gewürdigten Flügelzellenpumpe dargelegt:
- Optimierte Flügelzellenpumpe:
- Wärmeausdehnungskoeffizient Invar = 0.0000015°C-1
- Ausdehnung des Distanzelements aus Invar (Nickelstahl):
- Ausdehnung Sinterstahlradsatz:
- Hieraus ergibt sich ein Axialspiel von 0.026mm
- Schrumpfung des Distanzelements aus Invar (Nickelstahl):
- Schrumpfung Sinterstahlradsatz:
- Hieraus ergibt sich ein Axialspiel von 0.119mm
- Optimized vane pump:
- Thermal expansion coefficient Invar = 0.0000015 ° C -1
- Expansion of the spacer made of Invar (nickel steel):
- Expansion of sintered steel wheelset:
- This results in an axial clearance of 0.026mm
- Shrinkage of the spacer made of Invar (nickel steel):
- Shrinkage sintered steel wheelset:
- This results in an axial play of 0.119mm
Durch den Einbau eine Distanzelementes mit einem Wärmeausdehnungskoeffizienten von 0.0000015°C-1 verkleinert sich das Axialspiel bei 150°C auf 0.026 mm und vergrößert sich bei - 40°C auf 0.119 mm. Es zeigt sich somit, daß durch den Einbau einer Distanzelementes in das Pumpengehäuse beispielsweise aus Nickelstahl (Invar) mit 36% Nickel (Wärmeausdehnungskoeffizient von 0.0000015), die negative Auswirkung der Wärmeausdehnung in positive umgekehrt, d. h., bei hohen Temperaturen verkleinert sich das Axialspiel und bei niedrigen Temperaturen vergrößert sich das Axialspiel.By installing a spacer element with a thermal expansion coefficient of 0.0000015 ° C -1 , the axial clearance at 150 ° C reduces to 0.026 mm and increases at -40 ° C to 0.119 mm. It is thus found that by incorporating a spacer into the pump housing, for example made of nickel steel (Invar) with 36% nickel (coefficient of thermal expansion of 0.0000015), the negative effect of thermal expansion in positive vice versa, ie at high temperatures reduces the axial play and at low temperatures increases the axial play.
Die Auswirkung der Wärmeausdehnung bezüglich der Veränderung des Axialspiels über die Temperatur ist in der Grafik in Figur 6 wiedergegeben.The effect of thermal expansion on the change in axial clearance versus temperature is shown in the graph in FIG.
Die Grafik zeigt, daß bei einer Kombination eines Pumpengehäuses aus Stahl mit einem Radsatz aus Stahl das geplante Axialspiel über die Temperatur konstant bleibt, da das Pumpengehäuse und der Radsatz einen identischen Wärmeausdehnungskoeffizienten aufweisen. Ein hinsichtlich des Gewichtes optimiertes Pumpengehäuse aus Aluminium-Druckguß in Kombination mit einem Radsatz aus Sinterstahl zeigt das bei höheren Temperaturen steigende Axialspiel und die dadurch bedingten inneren Leckagen, die nicht gewünscht sind. Die erfindungsgemäße Kombination eines leichten Pumpengehäuses aus Aluminium-Druckguß mit einem Sinterstahlradsatz und Distanzelementen mit einem geringeren Wärmeausdehnungskoeffizienten als der Radsatz und das Pumpengehäuse zeigt ein sich bei steigenden Temperaturen verringerndes Axialspiel.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. The inventive combination of a lightweight pump housing made of die-cast aluminum with a Sinterstahlradsatz and spacer elements with a lower coefficient of thermal expansion than the wheelset and the pump housing shows a decreasing with increasing temperatures axial clearance.
Ferner wird durch die in Figur 7 wiedergegeben Grafik dargestellt, wie sich der volumetrische Wirkungsgrad bei steigendem Druck und steigenden Temperaturen verhält für eine nach dem Stand der Technik hergestellte Pumpe, wobei folgende Testbedingungen vorlagen:
Es ist deutlich erkennbar, daß der volumetrische Wirkungsgrad einer nach dem Stand der Technik hergestellten Pumpe bei steigendem Druck bei 20°C um ungefähr 7% sinkt. Bei einer auf 80°C erhöhten Temperatur sinkt der volumetrische Wirkungsgrad um ungefähr 30%.It can be clearly seen that the volumetric efficiency of a pump made according to the prior art at rising pressure at 20 ° C decreases by about 7%. At a temperature increased to 80 ° C, the volumetric efficiency decreases by about 30%.
Demgegenüber zeigt die in Figur 8 wiedergegeben Grafik, wie sich der volumetrische Wirkungsgrad bei steigendem Druck und steigenden Temperaturen verhält bei einer erfindungsgemäßen Pumpe verhält, wobei folgende Testbedingungen vorlagen:
Es ist erkennbar, daß der volumetrische Wirkungsgrad einer erfindungsgemäßen Pumpe bei steigendem Druck und nahezu unabhängig von der Temperatur um nur ungefähr 7% sinkt.It can be seen that the volumetric efficiency of a pump according to the invention falls by only about 7% with increasing pressure and almost independent of the temperature.
In vorteilhafter Ausgestaltung der Erfindung ist vorgesehen, daß zwischen dem Pumpendeckel und dem Pumpenflansch eine Pumpenringplatte angeordnet ist, in der wenigstens ein Zahnradsatz gelagert ist, wobei die Pumpenringplatte einen größeren Wärmeausdehnungskoeffizienten aufweist als das Distanzelement.In an advantageous embodiment of the invention it is provided that between the pump cover and the pump flange, 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.
In weiterer vorteilhafter Ausgestaltung der Erfindung ist vorgesehen, daß der Wärmeausdehnungskoeffizient des Distanzelementes um wenigstens den Faktor 10 kleiner ist als der jeweilige Wärmeausdehnungskoeffizient des Pumpendeckels, des Pumpenflansches, des Radsatzes und der Pumpenringplatte.In a further advantageous embodiment of the invention, it is provided that 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.
In besonders vorteilhafter Ausgestaltung der Erfindung ist vorgesehen, daß der Wärmeausdehnungskoeffizient des Distanzelementes kleiner 0,00002 °C-1 ist.In a particularly advantageous embodiment of the invention it is provided that the thermal expansion coefficient of the spacer element is less than 0.00002 ° C -1 .
In zweckmäßiger Ausgestaltung der Erfindung ist vorgesehen, daß das Distanzelement aus Nickelstahl besteht, vorzugsweise mit einem Anteil von 36% Nickel.In an advantageous embodiment of the invention it is provided that the spacer element consists of nickel steel, preferably with a share of 36% nickel.
In weiterer zweckmäßiger Ausgestaltung der Erfindung ist vorgesehen, daß das Distanzelemente ein Sinterteil ist. Das gesinterte metallische Bauteil kann mit entsprechenden Legierungselementen versehen sein, um ein Distanzelement mit einem auf den Anwendungsfall abgestimmten Wärmeausdehnungskoeffizienten zu erhalten.In a further advantageous embodiment of the invention, it is provided that 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.
In vorteilhafter Ausgestaltung der Erfindung ist vorgesehen, daß in der Pumpenringplatte ein Planetenrotorsatz exzentrisch gelagert ist, wobei der Innenrotor mit einer Antriebswelle verbunden ist und der Pumpendeckel, die Pumpenringplatte und der Pumpenflansch dichtend voneinander getrennt sind, wobei Distanzelemente vorgesehen sind, deren Höhe um den Betrag des geplanten Axialspiels größer ist als die Höhe des Planetenrotorsatzes und die Höhe der Pumpenringplatte ist um den Wärmeausdehnungsdifferenzbetrag kleiner als die Höhe des Distanzelements, wobei die zwischen Pumpendeckel, Pumpenringplatte und Pumpenflansch bestehende Dehnungsspalte durch Dichtelemente abgedichtet wird.In an advantageous embodiment of the invention, it is provided that in the pump ring plate 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.
In besonders vorteilhafter Ausgestaltung der Erfindung ist vorgesehen, daß der Pumpendeckel mit einem Bund versehen ist, der in die Pumpenringplatte hineinragt und in der Pumpenringplatte ein Planetenrotorsatz gelagert ist, wobei die Pumpenringplatte von wenigstens einem Distanzelement durchsetzt ist, welches in Kontakt mit dem Pumpendeckel und dem Pumpenflansch steht.In a particularly advantageous embodiment of the invention it is provided that 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.
In weiterer vorteilhafter Ausgestaltung der Erfindung ist vorgesehen, daß der Pumpendeckel und der Pumpenflansch mit einem Bund versehen sind, der in die Pumpenringplatte hineinragt und in der Pumpenringplatte ein Planetenrotorsatz gelagert ist, wobei die Pumpenringplatte von wenigstens einem Distanzelement durchsetzt ist, welches in Kontakt mit dem Pumpendeckel und dem Pumpenflansch steht.In a further advantageous embodiment of the invention, it is provided that 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.
Die Erfindung wird anhand schematischer Zeichnungen von Ausführungsbeispielen dargestellt. Es zeigen:
- Fig. 1.1
- einen Schnitt entlang der Linie A-A in Fig. 1.2 einer erfindungsgemäße Pumpe in Plattenbauweise,
- Fig. 1.2
- eine Draufsicht zu Fig. 1.1,
- Fig. 1.3
- eine Einzelheit X1 gemäß Fig. 1.1,
- Fig. 2.1
- einen Schnitt durch eine erste erfindungsgemäße Variante,
- Fig. 2.2
- eine Einzelheit X2 gemäß Fig. 2.1,
- Fig. 3.1
- einen Schnitt durch eine zweite erfindungsgemäße Variante,
- Fig. 3.2
- eine Einzelheit X3 gemäß Fig. 3.1,
- Fig. 4.1
- einen Schnitt durch eine dritte erfindungsgemäße Variante,
- Fig. 4.2
- eine Einzelheit X4 gemäß Fig. 4.1,
- Fig. 5.1
- einen Schnitt durch eine vierte erfindungsgemäße Variante,
- Fig. 5.2
- eine Einzelheit X5 gemäß Fig. 5.1,
- Fig. 6
- eine Grafik bezüglich der Veränderung des Axialspiels im Verhältnis zur Temperatur,
- Fig. 7
- eine Grafik bezüglich der Veränderung des volumetrischen Wirkungsgrades im Verhältnis zu Temperatur und Druck bei einer Pumpe nach dem Stand der Technik,
- Fig. 8
- eine Grafik bezüglich der Veränderung des volumetrischen Wirkungsgrades im Verhältnis zu Temperatur und Druck bei einer erfindungsgemäßen Pumpe.
- Fig. 1.1
- 3 a section along the line AA in FIG. 1.2 of a pump according to the invention in panel construction,
- Fig. 1.2
- a plan view to Fig. 1.1,
- Fig. 1.3
- a detail X1 according to FIG. 1.1,
- Fig. 2.1
- a section through a first variant according to the invention,
- Fig. 2.2
- a detail X2 according to FIG. 2.1,
- Fig. 3.1
- a section through a second variant according to the invention,
- Fig. 3.2
- a detail X3 according to FIG. 3.1,
- Fig. 4.1
- a section through a third variant according to the invention,
- Fig. 4.2
- a detail X4 according to FIG. 4.1,
- Fig. 5.1
- a section through a fourth variant according to the invention,
- Fig. 5.2
- a detail X5 according to FIG. 5.1,
- Fig. 6
- a graph showing the change of the axial play in relation to the temperature,
- Fig. 7
- a graph relating to the change in volumetric efficiency in relation to temperature and pressure in a pump according to the prior art,
- Fig. 8
- a graph relating to the change in the volumetric efficiency in relation to temperature and pressure in a pump according to the invention.
Figur 1.1 zeigt ein einen Schnitt durch ein Pumpengehäuse in Plattenbauweise, das aus einem Pumpendeckel 2, einer Pumpenringplatte 6 und einem Pumpenflansch 3 besteht. In der Pumpenringplatte 6 ist ein Planetenrotorsatz 4, bestehend aus einem Außenrotor 16, Planetenrotoren 17 und einem Innenrotor 7, exzentrisch gelagert. Über die Antriebswelle 9 wird der Innenrotor 7 angetrieben. In der Pumpenringplatte 6 sind Lagerbohrungen 14 für die Distanzbuchsen 5 vorgesehen. In Pumpendeckel 2 und Pumpenflansch 3 ist eine O-Ringnut 12 eingearbeitet, in der ein Dichtring 11 (O-Ring) eingesetzt ist, der Leckage nach außen verhindert.Figure 1.1 shows a section through a pump housing in plate construction, which consists of a
Die Distanzbuchsen 5 sind mit der Höhe des Planetenrotorsatzes so abgestimmt, daß die Distanzbuchsen 5 genau um den Betrag des geplanten Axialspiels 24 höher sind als die Höhe des Planetenrotorsatzes 4. Die Differenz der Höhe zwischen Distanzbuchsen 5 und Planetenrotorsatz 4 entspricht dem Axialspiel 24 bei Umgebungstemperatur.The
Die Pumpenringplatte 6 ist mit den Distanzbuchsen 5 so abzustimmen, daß die Pumpenringplatte 6 um den wärmeausdehnungsbetrag (Wärmeausdehnungskoeffizient(Pumpenringplatte)* Höhe(Pumpenringplatte) * Temperatur) kleiner als die Distanzbuchsen 5 ist. Dies entspricht dem Dehnungsspalt 15.The
Beim Zusammenschrauben der Pumpe 1 wird der Pumpendeckel 2 und der Pumpenflansch 3 auf die Distanzbuchsen 5 aufgepreßt. Es entsteht zwischen Pumpendeckel 2, Pumpenringplatte 6 und Pumpenflansch 3 ein Dehnungsspalte 15, der durch die elastischen O-Ringe 11.1 und 11.2 abgedichtet wird.When screwing the
Der Werkstoff für die Distanzbuchsen 5 ist so gewählt, daß der Wärmeausdehnungskoeffizient immer kleiner ist als der des Radsatzes 4 und der Pumpenringplatte 6. Im vorliegenden Fall ist es vorteilhaft als Werkstoff für die Distanzbuchsen 5 einen Nickelstahl mit 36% Nickel einzusetzen (Invar). Dieser Werkstoff besitzt einen Wärmeausdehnungskoeffizienten von 0.0000015 °C-1, welcher somit um den Faktur 10 kleiner ist als der Wärmeausdehnungskoeffizient von Sinterstahl oder Stahl. Vorteilhaft ist es auch, wenn der Radsatz 4 aus Sinter-Alu Si 14 gebildet wird.The material for the
Figur 1.2 zeigt, daß in den Pumpendeckel 2 auf einem Teilkreis acht Durchgangsbohrungen 13 und in den Pumpenflansch 3 acht Gewindebohrungen für eine Verschraubung mittels Schrauben 14 eingebracht sind. In der Pumpenringplatte 6 sind auf demselben Teilkreis des Pumpendeckels 2 und in gleicher Position wie die Durchgangsbohrungen 13, die Lagerbohrungen 14 für die Distanzelemente vorgesehen, welche als Distanzbuchsen 5 ausgebildet sind.Figure 1.2 shows that in the
Figur 1.3 zeigt eine Einzelheit gemäß Figur 1.1, wobei zwischen dem Pumpendeckel 2 und dem Pumpenflansch 3 eine Pumpenringplatte 6,ein Planetenrotorsatz 4, bestehend aus einem Außenrotor 16, Planetenrotoren 17 und einem Innenrotor 7, exzentrisch gelagert ist. In den Pumpendeckel 2 und den Pumpenflansch 3 ist eine O-Ringnut 12.1, 12.2 eingearbeitet, in der ein Dichtring 11.1, 11.2 (O-Ring) eingesetzt ist, der Leckage nach außen verhindert. Das Distanzelement 5 weist eine größere Höhe als die Pumpenringplatte 6, so daß sich ein Dehnungsspalt 15.1, 15.2 ergibt.Figure 1.3 shows a detail according to Figure 1.1, wherein between the
Bei der erfindungsgemäßen Pumpe gemäß Fig. 1.1, 1.2 und 1.3 ergeben sich bei einem Pumpentest folgende Werte:
Somit würde bei 150°C ein Axialspiel von 0,0227mm entstehen.
Es entsteht bei minus 40°C somit ein Axialspiel von 0,0625mm.
- ATF-
Getriebeöl bei 150°C ca 3,4 mm2/s(cSt) - ATF-Getriebeöl bei -40°C ca 100002 /s(cSt)
- ATF gear oil at 150 ° C approx. 3.4 mm 2 / s (cSt)
- ATF gear oil at -40 ° C approx. 10000 2 / s (cSt)
Figur 2.1 zeigt eine weitere Ausgestaltungsform der Erfindung, welche das gleiche Verhalten der Pumpe 1 gemäß Figur 1 erreicht. Diese Konstruktion ist optimal für schmale Radsätze. Der Pumpendeckel 2 ist mit einem Bund 18 versehen, der in die Pumpenringplatte 6 hineinragt. Der Bund 18 ist in die Pumpenringplatte 6 einzupassen. Da der Pumpendeckel 2 auf den Distanzbuchsen 5 aufsitzt, vergrößert sich die Bundlänge 19 bei einer Temperaturerhöhung in Richtung Radsatz 4 und beeinflußt das Axialspiel 24. Bei der Auslegung des Axialspiels 24 ist die Bundlänge 19 so anzulegen, daß sich über die Ausdehnung der Bundlänge 19 des Pumpendeckels 2 das benötigte Axialspiel 24 einstellt. Der Pumpendeckel 2 ist aus Aluminium Druckguß und der Zahnradsatz aus Stahl oder Sinterstahl. Die Pumpenringplatte 6 besteht aus Aluminium Druckguß und die Distanzbuchsen 5 aus Nickelstahl mit 36% Nickel (Invar). Der Werkstoff des Pumpenflansches 3 hat bei dieser Konstruktion keinen Einfluß auf die Ausdehnung. Der Wärmeausdehnungskoeffizient des Bundes 18 sollte möglichst hoch sein.FIG. 2.1 shows a further embodiment of the invention, which achieves the same behavior of the
Es ergeben sich für die Erfindungsgemäße Konstruktion folgende Werte:
- Ausdehnung Distanzbuchsen (Invar):
- Ausdehnung Radsatz (Sinterstahl)
- Ausdehnung Alu-Bundlänge:
Bei 150°C entsteht somit ein Axialspiel von:
- Extension of distance bushes (Invar):
- Extension of wheel set (sintered steel)
- Extension aluminum waist length:
- At 150 ° C, an axial play of:
Eine weitere konstruktive Möglichkeit besteht darin, die Pumpenringplatte aus Nickelstahl mit 36% Nickel (Invar) zu fertigen. Alternativ kann die Pumpenringplatte auch aus Messing oder Rotguß gefertigt sein, wobei der Wärmeausdehnungskoeffizient ungefähr 0.000018°C-1 betragen würde.Another design option is to make the pump ring plate from nickel steel with 36% nickel (Invar). Alternatively, the pump ring plate can also be made of brass or gunmetal, the coefficient of thermal expansion would be approximately 0.000018 ° C -1 .
Figur 3.1 zeigt einen Schnitt durch eine ähnliche Konstruktion wie Figur 2.1, wobei bei dieser Konstruktion beide Pumpen deckel 2 und Pumpenflansch 3 mit einem Bund 18.1, 18.2 verse hen sind. Pumpendeckel 2 und Pumpenflansch 3 sollten aus Alu minium sein, oder einem Werkstoff mit einem ähnlichen Wärmeausdehnungskoeffizienten. Der Wärmeausdehnungs-koeffizient des Bundes 18 sollte möglichst hoch sein.Figure 3.1 shows a section through a similar construction as Figure 2.1, wherein in this construction, both pumps cover 2 and pump
Figur 4.1 zeigt einen Schnitt durch eine weitere Konstruktion bei der die Pumpenringplatte 6 und der Pumpenflansch 3 durch ein kompaktes Pumpengehäuse 20 ersetzt werden. Der Werkstoff des Pumpengehäuses 20 kann beispielsweise Grauguß oder Aluminium Druckguß sein. Die Tiefe der Lagerbohrungen 21 für die Distanzbuchsen 5 sollte der Radsatzbreite 22 entsprechen. Durch Variieren der Tiefe der Lagerbohrungen 21 und der entsprechenden Länge der Distanzbuchsen 5 kann man zusätzlich Einfluß auf das Axialspiel 24 nehmen.Figure 4.1 shows a section through a further construction in which the
Figur 5.1 zeigt eine Ausgestaltung der Erfindung zu Figur 4.1, wobei die Tiefe der Lagerbohrung 21 und dementsprechend die Höhe des Distanzelementes geringer ist als die Radsatzbreite 22. Insbesondere bei breiten Radsätzen 4, beispielsweise > 30mm, tritt das Problem auf, daß die Wärmeausdehnungsdifferenz zwischen dem Material des Radsatzes 4 und des Distanzelementes 5 zu groß ist, wodurch das Axialspiel 24 gegen Null gehen würde. Eine Lösung ist, daß das Distanzelement 5 eine geringere Höhe aufweist als die Radsatzbreite 22. Die Ausdehnung des Distanzelementes 5 läßt sich berechnen als:
Figur 5.2 zeigt eine Einzelheit gemäß Figur 1.1FIG. 5.2 shows a detail according to FIG. 1.1
Claims (9)
- A pump (1), in particular oil pump for internal combustion engines, consisting of a pump housing, the pump housing consisting of a pump cover (2) and a pump flange (3), with at least one set of gear wheels (4) being located between the pump cover (2) and the pump flange (3) and the pump cover (2) and the pump flange (3) being connected by means of at least one spacer element (5), characterised in that the spacer element (5) has a lower coefficient of thermal expansion than the pump cover (2), the pump flange (3) and the set of gear wheels (4).
- A pump (1) according to Claim 1, characterised in that a pump ring plate (6) is arranged between the pump cover (2) and the pump flange (3), in which plate at least one set of gear wheels (4) is mounted, the pump ring plate (6) having a greater coefficient of thermal expansion than the spacer element (5).
- A pump (1) according to Claim 1 or 2, characterised in that the coefficient of thermal expansion of the spacer element (5) is smaller by at least a factor of 10 than the respective coefficient of thermal expansion of the pump cover (2), the pump flange (3), the set of wheels (4) and the pump ring plate (6).
- A pump (1) according to one of Claims 1 to 3, characterised in that the coefficient of thermal expansion of the spacer element (5) is less than 0.00002°C-1.
- A pump (1) according to one of Claims 1 to 4, characterised in that the spacer element (5) is made of nickel steel, preferably having a content of 36% nickel.
- A pump (1) according to one of Claims 1 to 5, characterised in that the spacer element (5) is a sintered component.
- A pump (1) according to one of Claims 1 to 6, characterised in that a set of planetary rotors (4) is eccentrically mounted in the pump ring plate (6), the inner rotor (7) being connected to a drive shaft (9) and the pump cover (2), the pump ring plate (6) and the pump flange (3) being hermetically separated from one another, with spacer elements (5) being provided, the height of which is greater by the amount of the planned axial clearance than the height of the set of planetary rotors (4) and the height of the pump ring plate (6) is smaller by the amount of the difference in thermal expansion than the height of the spacer element (5), the expansion gap (10) between the pump cover (2), pump ring plate (6) and pump flange (3) being sealed off by sealing elements (11).
- A pump (1) according to one of Claims 1 to 7, characterised in that the pump cover (2) is provided with a collar (12) which protrudes into the pump ring plate (6), and a set of planetary rotors (4) is mounted in the pump ring plate (6), the pump ring plate (6) having at least one spacer element (5) passing through it, which element is in contact with the pump cover (2) and the pump flange (3).
- A pump (1) according to one of Claims 1 to 8, characterised in that the pump cover (2) and the pump flange (3) are provided with a collar (12) which protrudes into the pump ring plate (6), and a set of planetary rotors (4) is mounted in the pump ring plate (6), the pump ring plate (6) having at least one spacer element (5) passing through it, which element is in contact with the pump cover (2) and the pump flange (3).
Priority Applications (1)
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PL04740962T PL1644641T3 (en) | 2003-07-14 | 2004-07-12 | Gear pump having optimal axial play |
Applications Claiming Priority (2)
Application Number | Priority Date | Filing Date | Title |
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DE10331979A DE10331979A1 (en) | 2003-07-14 | 2003-07-14 | Pump with optimized axial clearance |
PCT/EP2004/007729 WO2005005834A1 (en) | 2003-07-14 | 2004-07-12 | Gear pump having optimal axial play |
Publications (2)
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EP1644641A1 EP1644641A1 (en) | 2006-04-12 |
EP1644641B1 true EP1644641B1 (en) | 2007-05-23 |
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EP04740962A Expired - Lifetime EP1644641B1 (en) | 2003-07-14 | 2004-07-12 | Gear pump having optimal axial play |
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US (2) | US7713041B2 (en) |
EP (1) | EP1644641B1 (en) |
JP (1) | JP4489076B2 (en) |
KR (1) | KR100777961B1 (en) |
CN (1) | CN100564877C (en) |
AT (1) | ATE363028T1 (en) |
BR (1) | BRPI0412661A (en) |
DE (2) | DE10331979A1 (en) |
MX (1) | MXPA06000263A (en) |
PL (1) | PL1644641T3 (en) |
WO (1) | WO2005005834A1 (en) |
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JP4596841B2 (en) * | 2004-07-21 | 2010-12-15 | 日立オートモティブシステムズ株式会社 | Oil pump |
JP2008267333A (en) * | 2007-04-24 | 2008-11-06 | Hitachi Ltd | Oil pump |
DE102011107157B4 (en) | 2011-07-14 | 2013-02-28 | Geräte- und Pumpenbau GmbH Dr. Eugen Schmidt | Annular gear pump |
DE102013100378A1 (en) * | 2013-01-15 | 2014-07-17 | ENVA Systems GmbH | Apparatus for converting energy contained in a fluid |
DE102013016833A1 (en) | 2013-10-10 | 2015-04-16 | Daimler Ag | Pump for conveying a liquid, in particular a lubricant of an internal combustion engine for a motor vehicle |
CN104373345B (en) * | 2014-10-15 | 2017-08-08 | 哈尔滨东安发动机(集团)有限公司 | A kind of oil pump for optimizing axial gap |
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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US2312655A (en) * | 1941-05-22 | 1943-03-02 | Pump Engineering Service Corp | Pump |
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2003
- 2003-07-14 DE DE10331979A patent/DE10331979A1/en not_active Ceased
-
2004
- 2004-07-12 MX MXPA06000263A patent/MXPA06000263A/en active IP Right Grant
- 2004-07-12 AT AT04740962T patent/ATE363028T1/en not_active IP Right Cessation
- 2004-07-12 WO PCT/EP2004/007729 patent/WO2005005834A1/en active IP Right Grant
- 2004-07-12 KR KR1020067000900A patent/KR100777961B1/en not_active IP Right Cessation
- 2004-07-12 JP JP2006519860A patent/JP4489076B2/en not_active Expired - Fee Related
- 2004-07-12 EP EP04740962A patent/EP1644641B1/en not_active Expired - Lifetime
- 2004-07-12 CN CNB2004800202633A patent/CN100564877C/en not_active Expired - Fee Related
- 2004-07-12 BR BRPI0412661-0A patent/BRPI0412661A/en active Search and Examination
- 2004-07-12 DE DE502004003895T patent/DE502004003895D1/en not_active Expired - Lifetime
- 2004-07-12 PL PL04740962T patent/PL1644641T3/en unknown
-
2006
- 2006-01-13 US US11/332,523 patent/US7713041B2/en not_active Expired - Fee Related
-
2010
- 2010-04-05 US US12/754,404 patent/US7887309B2/en not_active Expired - Fee Related
Non-Patent Citations (1)
Title |
---|
None * |
Also Published As
Publication number | Publication date |
---|---|
WO2005005834A1 (en) | 2005-01-20 |
BRPI0412661A (en) | 2006-09-26 |
US20060140811A1 (en) | 2006-06-29 |
PL1644641T3 (en) | 2007-09-28 |
CN100564877C (en) | 2009-12-02 |
JP4489076B2 (en) | 2010-06-23 |
EP1644641A1 (en) | 2006-04-12 |
US20100239449A1 (en) | 2010-09-23 |
MXPA06000263A (en) | 2006-07-03 |
JP2009513859A (en) | 2009-04-02 |
US7713041B2 (en) | 2010-05-11 |
ATE363028T1 (en) | 2007-06-15 |
KR20060038444A (en) | 2006-05-03 |
CN1823224A (en) | 2006-08-23 |
DE502004003895D1 (en) | 2007-07-05 |
US7887309B2 (en) | 2011-02-15 |
DE10331979A1 (en) | 2005-02-17 |
KR100777961B1 (en) | 2007-11-21 |
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