EP1642030B1 - Pump - Google Patents
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- Publication number
- EP1642030B1 EP1642030B1 EP04738734.5A EP04738734A EP1642030B1 EP 1642030 B1 EP1642030 B1 EP 1642030B1 EP 04738734 A EP04738734 A EP 04738734A EP 1642030 B1 EP1642030 B1 EP 1642030B1
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- European Patent Office
- Prior art keywords
- region
- contour
- pump
- point
- wing
- 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
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- 238000006073 displacement reaction Methods 0.000 claims description 4
- 239000003921 oil Substances 0.000 description 7
- 238000007906 compression Methods 0.000 description 5
- 238000000034 method Methods 0.000 description 5
- 230000008569 process Effects 0.000 description 5
- 230000006835 compression Effects 0.000 description 4
- 230000007423 decrease Effects 0.000 description 4
- 239000012208 gear oil Substances 0.000 description 4
- 230000010349 pulsation Effects 0.000 description 4
- 230000000630 rising effect Effects 0.000 description 4
- 230000007704 transition Effects 0.000 description 4
- 230000008901 benefit Effects 0.000 description 3
- 230000000750 progressive effect Effects 0.000 description 3
- 230000009467 reduction Effects 0.000 description 2
- 235000015493 Chenopodium quinoa Nutrition 0.000 description 1
- 240000006162 Chenopodium quinoa Species 0.000 description 1
- 230000008859 change Effects 0.000 description 1
- 230000000295 complement effect Effects 0.000 description 1
- 230000003247 decreasing effect Effects 0.000 description 1
- 238000005187 foaming Methods 0.000 description 1
- 230000002035 prolonged effect Effects 0.000 description 1
- 238000000926 separation method Methods 0.000 description 1
Images
Classifications
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- 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
- F04C2/30—Rotary-piston machines or pumps having the characteristics covered by two or more groups F04C2/02, F04C2/08, F04C2/22, F04C2/24 or having the characteristics covered by one of these groups together with some other type of movement between co-operating members
- F04C2/34—Rotary-piston machines or pumps having the characteristics covered by two or more groups F04C2/02, F04C2/08, F04C2/22, F04C2/24 or having the characteristics covered by one of these groups together with some other type of movement between co-operating members having the movement defined in groups F04C2/08 or F04C2/22 and relative reciprocation between the co-operating members
- F04C2/344—Rotary-piston machines or pumps having the characteristics covered by two or more groups F04C2/02, F04C2/08, F04C2/22, F04C2/24 or having the characteristics covered by one of these groups together with some other type of movement between co-operating members having the movement defined in groups F04C2/08 or F04C2/22 and relative reciprocation between the co-operating members with vanes reciprocating with respect to the inner member
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
- F01C—ROTARY-PISTON OR OSCILLATING-PISTON MACHINES OR ENGINES
- F01C21/00—Component parts, details or accessories not provided for in groups F01C1/00 - F01C20/00
- F01C21/10—Outer members for co-operation with rotary pistons; Casings
- F01C21/104—Stators; Members defining the outer boundaries of the working chamber
- F01C21/106—Stators; Members defining the outer boundaries of the working chamber with a radial surface, e.g. cam rings
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- 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
- F04C13/00—Adaptations of machines or pumps for special use, e.g. for extremely high pressures
- F04C13/001—Pumps for particular liquids
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
- F04C15/00—Component parts, details or accessories of machines, pumps or pumping installations, not provided for in groups F04C2/00 - F04C14/00
- F04C15/0042—Systems for the equilibration of forces acting on the machines or pump
- F04C15/0049—Equalization of pressure pulses
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- 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
-
- 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
- F04C2/30—Rotary-piston machines or pumps having the characteristics covered by two or more groups F04C2/02, F04C2/08, F04C2/22, F04C2/24 or having the characteristics covered by one of these groups together with some other type of movement between co-operating members
- F04C2/34—Rotary-piston machines or pumps having the characteristics covered by two or more groups F04C2/02, F04C2/08, F04C2/22, F04C2/24 or having the characteristics covered by one of these groups together with some other type of movement between co-operating members having the movement defined in groups F04C2/08 or F04C2/22 and relative reciprocation between the co-operating members
- F04C2/344—Rotary-piston machines or pumps having the characteristics covered by two or more groups F04C2/02, F04C2/08, F04C2/22, F04C2/24 or having the characteristics covered by one of these groups together with some other type of movement between co-operating members having the movement defined in groups F04C2/08 or F04C2/22 and relative reciprocation between the co-operating members with vanes reciprocating with respect to the inner member
- F04C2/3446—Rotary-piston machines or pumps having the characteristics covered by two or more groups F04C2/02, F04C2/08, F04C2/22, F04C2/24 or having the characteristics covered by one of these groups together with some other type of movement between co-operating members having the movement defined in groups F04C2/08 or F04C2/22 and relative reciprocation between the co-operating members with vanes reciprocating with respect to the inner member the inner and outer member being in contact along more than one line or surface
-
- 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
- F04C2/30—Rotary-piston machines or pumps having the characteristics covered by two or more groups F04C2/02, F04C2/08, F04C2/22, F04C2/24 or having the characteristics covered by one of these groups together with some other type of movement between co-operating members
- F04C2/34—Rotary-piston machines or pumps having the characteristics covered by two or more groups F04C2/02, F04C2/08, F04C2/22, F04C2/24 or having the characteristics covered by one of these groups together with some other type of movement between co-operating members having the movement defined in groups F04C2/08 or F04C2/22 and relative reciprocation between the co-operating members
- F04C2/344—Rotary-piston machines or pumps having the characteristics covered by two or more groups F04C2/02, F04C2/08, F04C2/22, F04C2/24 or having the characteristics covered by one of these groups together with some other type of movement between co-operating members having the movement defined in groups F04C2/08 or F04C2/22 and relative reciprocation between the co-operating members with vanes reciprocating with respect to the inner member
- F04C2/3446—Rotary-piston machines or pumps having the characteristics covered by two or more groups F04C2/02, F04C2/08, F04C2/22, F04C2/24 or having the characteristics covered by one of these groups together with some other type of movement between co-operating members having the movement defined in groups F04C2/08 or F04C2/22 and relative reciprocation between the co-operating members with vanes reciprocating with respect to the inner member the inner and outer member being in contact along more than one line or surface
- F04C2/3447—Rotary-piston machines or pumps having the characteristics covered by two or more groups F04C2/02, F04C2/08, F04C2/22, F04C2/24 or having the characteristics covered by one of these groups together with some other type of movement between co-operating members having the movement defined in groups F04C2/08 or F04C2/22 and relative reciprocation between the co-operating members with vanes reciprocating with respect to the inner member the inner and outer member being in contact along more than one line or surface the vanes having the form of rollers, slippers or the like
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- 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
- F04C2250/00—Geometry
- F04C2250/30—Geometry of the stator
Definitions
- the invention relates to a pump, such as a vane pump or roller-cell pump, in particular gear pump, with doppelhubiger conveying contour, wherein the conveying contour has at least one rising area, at least one great circle area, at least one descent region and at least one small circle region and the pump within the delivery contour a rotor with radially displaceable Has wings or rollers in radial rotor slots.
- a pump such as a vane pump or roller-cell pump, in particular gear pump, with doppelhubiger conveying contour
- the conveying contour has at least one rising area, at least one great circle area, at least one descent region and at least one small circle region and the pump within the delivery contour a rotor with radially displaceable Has wings or rollers in radial rotor slots.
- the cell volume is nearly constant (apart from the case, which is a slight reduction of the blade stroke radially inward depending on the angle of rotation), and it can via pressure equalizing notches or intermediate capacities (see DE 100 27 990 A1 ) the pressure reversal can be realized soft with low pressure gradient.
- these measures are not sufficient for use with foamed gear oil.
- US 2,588,430 shows a vane pump with 12 wings and with an annular contour in which the small circle area is 40 °, the great circle area is 40 ° and both the rise area (suction) and the descent area (pressure range) 50 °. So the great circle area with 40 ° is smaller than the descent area with 50 ° and the rise area with 50 ° the same size as the descent area with 50 °.
- the application describes that thereby higher pressures and better efficiencies can be achieved. We proposed no solution to the problem of "foamed oil” or "air in oil”.
- a vane cell pump or roller cell pump having a double-stroke conveying contour, wherein the conveying contour comprises at least one rising region, which represents a suction region, at least one great circle region, which represents a first separating region, at least one descent region, which represents a pressure region, and at least one small-circle region, which represents a further separation region, and the pump within the delivery contour has a rotor with radially displaceable vanes or rollers in radial slots, wherein the angular range of the great circle of the delivery contour is greater than the angular range of the descent region, and in that the angular range of the increase region so-called suction area, larger than the angle range of the descent area.
- a pump according to the invention is characterized in that in a 10-blade pump the great circle region of the conveying contour by at least 10 ° -15 °, preferably 13 ° greater than the angular pitch of the blade positions in the rotor (36 °) of a 10-wing standard pump and in a 12-blade pump, the great circle region of the delivery contour is at least 16 ° -25 °, preferably 22 ° greater than the angular pitch of the blade positions in the rotor (30 °) of a 12-wing standard pump.
- the compression area is shortened compared to the standard pumps, and the area which is available for the pressure compensation process (pressure equalizing notches or intermediate capacities) advantageously extends by the corresponding angle or angles.
- a further pump according to the invention is characterized in that the length of the suction region remains essentially the same with respect to a standard pump. This has the advantage that no losses must be accepted by the same large suction area with respect to reaching the maximum speed.
- a pump is preferred in which, in the case of a 10-blade pump, the turning points of the Hubkonturfunktion are shifted relative to a 10-wing standard contour by about 3 ° in the direction of rotation.
- This has the advantage that the superposition of the kinematic volumetric flow pulsation of the wing and underfloor pump complement each other optimally. Otherwise, the turning points have a distance of about 2.5 x wing pitch (the wing pitch in the 10-wing pump is 36 °).
- FIG. 1 the delivery contour of a 10-wing standard pump with the corresponding rotation angle points is shown schematically.
- the conveyor contour 1 is shown in principle in the center of the picture and will now be explained schematically with reference to the angular points, these angles are not shown angularly accurate, but only their positions are explained schematically.
- the conveyor contour description begins with the angle 0 °, which is located in the middle of the small circle area.
- the small circle region goes in the angular point 5, ie at 15 °, in the rising area (contour is enlarged radially outward), in which increases the displacement between two wings and thus forms the suction area.
- the rise area has an inflection point in the Hubkonturfunktion (radius change as a function of the angle of rotation) at angle point 7 at 45 ° and finally ends at 69 ° at the angle 9.
- the position of the inflection points Hubkonturfunktion can be determined by the position of the maxima and the minima of the first derivative determine the stroke contour function above the angle of rotation (exactly). From the angle point 9, that is from 69 °, to the angle point 11, that is to say to 111 °, the so-called great circle region extends, which, however, is defined by the so-called case, i. a slight reduction of the stroke radially inwards depending on the angle of rotation, ensures that the wing heads always remain pressed against the contour.
- the great circle region with the case can also be defined such that its beginning forms the maximum of the stroke contour function and is given its end as soon as there is no tangent continuity in the first and / or second derivative of the stroke contour function.
- the actual descent region begins, which runs up to 165 °, that is to say up to the angle 15, and thus represents the pressure range of the vane pump, since the stroke volume now decreases.
- the descent region has at angular point 13, i. at 135 °, again a turning point in the Hubkonturfunktion.
- the inflection point at point 7, i. in the rise area, and the inflection point at point 13, i. in the descent, are spaced by about 90 ° from each other.
- the 10-wing pump has a wing pitch of 36 °, this corresponds to 2.5 times the wing pitch.
- the turning point in the descent area and the turning point in the next rise area are therefore also spaced by 2.5 times the wing pitch to each other.
- the location of the turning points is symmetrical to the main axis of the contour. From 165 °, i. from the angle 15, up to 180 °, i. until the angle 17, in turn, one half of the next small circle area extends. From 180 ° to 360 °, i. from the angle 17 to back to the angle 3, the conveyor contour is repeated symmetrically to the previously described votingkonturhgan.
- FIG. 2 a conveyor contour according to the invention for use in gear pumps is shown, which has a prolonged great circle area.
- the description of the conveyor contour 1 begins again at the angle 3, ie at 0 ° in the middle of the small circle area.
- the increase in the conveying contour begins and ends at the angle point 9 again at 69 °.
- the turning point of the conveyor contour function within the rise range is opposite to the FIG. 1 from 45 to 47.7 °, ie offset to about 48 ° or 3 ° in the direction of rotation and is thus at the new angular point 20.
- the great circle region of the new contour now extends from the angle point 9, ie from 69 °, to the angle point 22 at 118 °, which means that the great circle area with respect to the great circle area FIG. 1 extended by about 7 ° and this extension is now available for longer pressure equalization operations to compress unresolved air in the oil.
- the descent region of the conveying contour begins at angle point 22 at 118 ° and ends again at angle point 15 at 165 °, which means that the pressure range now by the corresponding 7 ° relative to the pressure range in FIG. 1 is shortened. It is important that the length of the suction region is maintained from the angular point 5 to the angle point 9, which is advantageous in terms of reaching the maximum speed.
- the inflection point 24 in the descent area is at 137.7 °, ie about 138 °, opposite to the inflection point off FIG. 1 advanced by 3 ° in the direction of rotation, which in turn means that both inflection points maintain their spacing of 90 ° or 2.5 x the pitch of the 10-blade pump (36 °).
- this new, inventive stroke contour is repeated symmetrically to the upper half.
- FIG. 3 a conveyor contour according to the invention of a 12-blade pump is shown.
- the description of the conveyor contour 1 begins again at 0 degrees in the angular point 3.
- the 12-wing pump has a wing pitch of 30 ° instead of 36 °
- the small circle area which has been 30 ° in the 10-wing pump to be reduced to 24 ° 6 °, whereby the rise range of the conveying contour begins after half a small circle at 12 ° in the angular point 30.
- the rising area of the conveying contour ie the suction area, is like the contours FIG. 1 and FIG. 2 maintained at 54 ° and thus ends at 66 ° at the angle of 32, so again 3 ° earlier than the 10-wing pumps.
- the inflection point of the Hubkonturfunktion in the rise area should be located advantageously in the middle of the rise range and is therefore arranged at an angle 34 at about 37.5 °.
- the great circle area of this conveyor contour now extends from the angle point 32 at 66 ° to the angle point 36 at 118 ° and is thus once again with respect to the conveyor contour FIG. 2 by 3 ° or with respect to the conveyor contour FIG. 1 extended by 10 °, which in turn represents a gain for improved pressure compensation with foamed gear oil.
- the descent region ie the pressure range of this conveying contour, extends from the angular point 36 at 118 ° to the angular point 38 at 168 °, in which the conveying contour in turn in the passes next small circle area.
- the inflection point of the Hubkonturfunktion in the descent area is arranged at angle point 40 at 141.7 ° and is thus from the inflection point at the angle 34 by 104 °, which is about 3.5 times the wing pitch of 30 ° in the 12-wing pump, spaced .
- the turning point 40 in the descent region, ie in the pressure range is spaced in the direction of rotation with respect to the next turning point at the angular point 42 by about 2.5 times the wing pitch of 30 °.
- the difference in great circle length to wing pitch is now 22 ° to 6 ° for the standard 10 wing contour and 13 ° to the improved 10 wing contour FIG. 2 ,
- the compression area may be opposite to the shortened compression area FIG. 2 even be extended by 3 °.
- the inflection points in the transition functions of the stroke contour thus have a factor x.5 of the wing pitch, which is the basis of a good overlap of under wing and wing pressure pulsation.
- the aim of the invention is to make the available angle in the great circle area as long as possible, since the noise in foamed gear oil is dominated mainly by the pressure compensation operations and not by the geometrically caused volumetric flow pulsation.
- the compression area is slightly shorter than the intake area, and the turning points are minimally a little further rotated as a pair.
- FIG. 4 is the stroke contour function of the 12-wing contour FIG. 3 shown with extended case over the rotation angle.
- point 50 corresponds to point 30 in FIG. 3
- point 54 at about 66 ° begins the great circle area 56.
- the great circle area 56 reduces the wing stroke constant with the so-called case to the point 58 (point 36 in FIG. 3 ), in which then the contour drop 60 to the point 62 (point 38 in FIG. 3 ).
- point 62 then begins the small circle region 64, which extends to point 66. Thereafter, the contour increase begins again in the same manner as from point 50.
- the great circle region 56 could be decidedly extended compared to the small circle region 64, which here now has an area in the case of the 12-wing pump extending from 30 ° minus 6 °.
- FIG. 5 is the function of deriving the wing lift according to the angle of rotation of the contour FIG. 3 shown above the angle of rotation.
- the increase in contour begins with increasing amount of derivative of the wing stroke according to the angle of rotation and has its maximum at point 72 (point 34 in FIG. 3 ), whereupon the amount of derivative of the wing lift after the angle of rotation to the point 74 (point 32 in FIG. 3 ) decreases steadily again.
- the transition to the great circle region, the derivative of which is represented by the course of line 76 then takes place.
- the great circle area 76 goes to point 78 (point 36 in FIG FIG.
- FIG. 6 is the derivative of the cell volume according to the angle of rotation of the contour FIG. 3 shown above the angle of rotation.
- a progressive increase in cell volume to point 100 and then a degressive increase in cell volume to point 102 characterize the aspiration process. Thereafter, the volume is then reduced slightly steadily in the great circle area by the case, until then from the point 104 of the actual compression process with progressive volume decrease to point 106 and then with degressive volume decrease takes place to the point 108. Thereafter, when passing through the petty rice region, an increase in volume of a progressive nature up to the point 110 occurs again, the process described here repeating itself for the second time.
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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)
Description
Die Erfindung betrifft eine Pumpe, wie beispielsweise eine Flügelzellenpumpe oder Rollenzellenpumpe, insbesondere Getriebepumpe, mit doppelhubiger Förderkontur, wobei die Förderkontur mindestens einen Anstiegsbereich, mindestens einen Großkreisbereich, mindestens einen Abstiegsbereich und mindestens einen Kleinkreisbereich aufweist und die Pumpe innerhalb der Förderkontur einen Rotor mit radial verschieblichen Flügeln oder Rollen in radialen Rotorschlitzen aufweist.The invention relates to a pump, such as a vane pump or roller-cell pump, in particular gear pump, with doppelhubiger conveying contour, wherein the conveying contour has at least one rising area, at least one great circle area, at least one descent region and at least one small circle region and the pump within the delivery contour a rotor with radially displaceable Has wings or rollers in radial rotor slots.
Derartige Pumpen sind bekannt. Das Problem dabei ist, dass Getriebepumpen mit verschäumtem Getriebeöl arbeiten. Durch die unterschiedlichen Verschäumungsgrade ergeben sich stark unterschiedliche Ölelastizitäten. Ist viel ungelöste Luft im Öl enthalten, ist das Öl sehr weich. Damit dauert der Druckausgleichsvorgang bei konstanter Umsteuergeometrie länger als bei hartem, unverschäumten Öl, und es werden längere Drehwinkel für den Druckumsteuervorgang benötigt, um auf die starke Elastizitätsstreuung zu reagieren. Diese Drehwinkel werden letztlich durch den Großkreisbereich geschaffen, dessen Winkel nur geringfügig größer ist als die Flügelteilung. In diesem Bereich ist das Zellvolumen nahezu konstant (abgesehen vom Fall, das ist eine leichte Verringerung des Flügelhubes radial nach innen in Abhängigkeit des Drehwinkels), und es kann über Druckausgleichskerben oder Zwischenkapazitäten (siehe
Es ist daher Aufgabe der Erfindung, eine Pumpe zu schaffen, die diese Probleme nicht aufweist.It is therefore an object of the invention to provide a pump which does not have these problems.
Die Aufgabe wird gelöst durch eine Flügelzellenpumpe oder Rollenzellenpumpe mit einer doppelhubigen Förderkontur, wobei die Förderkontur mindestens einen Anstiegsbereich, welcher einen Saugbereich darstellt, mindestens einen Großkreisbereich, welcher einen ersten Trennbereich darstellt, mindestens einen Abstiegsbereich, welcher einen Druckbereich darstellt, und mindestens einen Kleinkreisbereich, der einen weiteren Trennbereich darstellt, aufweist, und die Pumpe innerhalb der Förderkontur einen Rotor mit radial verschieblichen Flügeln oder Rollen in radialen Schlitzen aufweist, wobei der Winkelbereich des Großkreises der Förderkontur größer ist als der Winkelbereich des Abstiegsbereichs, und dass der Winkelbereich des Anstiegbereichs, der sogenannte Saugbereich, größer ist als der Winkelbereich des Abstiegsbereichs.The object is achieved by a vane cell pump or roller cell pump having a double-stroke conveying contour, wherein the conveying contour comprises at least one rising region, which represents a suction region, at least one great circle region, which represents a first separating region, at least one descent region, which represents a pressure region, and at least one small-circle region, which represents a further separation region, and the pump within the delivery contour has a rotor with radially displaceable vanes or rollers in radial slots, wherein the angular range of the great circle of the delivery contour is greater than the angular range of the descent region, and in that the angular range of the increase region so-called suction area, larger than the angle range of the descent area.
Eine erfindungsgemäße Pumpe zeichnet sich dadurch aus, dass bei einer 10-Flügel-Pumpe der Großkreisbereich der Förderkontur um mindestens 10°-15°, vorzugsweise 13° größer ist als die Winkelteilung der Flügelpositionen im Rotor (36°) einer 10-Flügel-Standardpumpe und bei einer 12-Flügel-Pumpe der Großkreisbereich der Förderkontur um mindestens 16°-25°, vorzugsweise 22° größer ist als die Winkelteilung der Flügelpositionen im Rotor (30°) einer 12-Flügel-Standardpumpe. Hierdurch verkürzt sich gegenüber den Standardpumpen der Verdichtungsbereich, und der Bereich, der für den Druckausgleichsvorgang (Druckausgleichskerben oder Zwischenkapazitäten) zur Verfügung steht, verlängert sich vorteilhaft um den entsprechenden Winkel bzw. die entsprechenden Winkel.A pump according to the invention is characterized in that in a 10-blade pump the great circle region of the conveying contour by at least 10 ° -15 °, preferably 13 ° greater than the angular pitch of the blade positions in the rotor (36 °) of a 10-wing standard pump and in a 12-blade pump, the great circle region of the delivery contour is at least 16 ° -25 °, preferably 22 ° greater than the angular pitch of the blade positions in the rotor (30 °) of a 12-wing standard pump. As a result, the compression area is shortened compared to the standard pumps, and the area which is available for the pressure compensation process (pressure equalizing notches or intermediate capacities) advantageously extends by the corresponding angle or angles.
Eine weitere erfindungsgemäße Pumpe zeichnet sich dadurch aus, dass die Länge des Saugbereiches gegenüber einer Standardpumpe im Wesentlichen gleich bleibt. Das hat den Vorteil, dass durch den gleich großen Saugbereich bezüglich des Erreichens der Maximaldrehzahl keine Einbußen hingenommen werden müssen.A further pump according to the invention is characterized in that the length of the suction region remains essentially the same with respect to a standard pump. This has the advantage that no losses must be accepted by the same large suction area with respect to reaching the maximum speed.
Bevorzugt wird weiterhin eine Pumpe, bei der im Falle einer 12-Flügel-Pumpe die Wendepunkte der Hubkonturfunktion in Richtung vom Saugbereich zum Druckbereich etwa einen Abstand von 3,5 x Flügelteilung (Flügelteilung = 30°) und die Wendepunkte in Richtung vom Druckbereich zum Saugbereich etwa einen Abstand von 2,5 x Flügelteilung aufweisen. Das hat den Vorteil, dass die Wendepunkte optimal etwa in der Mitte der Anstiegs- und Abfallbereiche der Förderkontur zu liegen kommen, was für eine Übergangsfunktion mit nicht zu kleinen Krümmungsradien sorgt, die sich gut schleifen läßt.In addition, in the case of a 12-blade pump, the turning points of the stroke contour function in the direction from the suction area to the pressure area are approximately 3.5 × wing pitch (wing pitch = 30 °) and the inflection points in the direction from the pressure area to the suction area have a spacing of 2.5 x wing pitch. This has the advantage that the turning points come to lie optimally approximately in the middle of the rise and fall areas of the conveyor contour, which provides a transition function with not too small radii of curvature, which can be easily sanded.
Weiterhin wird eine Pumpe bevorzugt, bei welcher im Falle einer 10-Flügel-Pumpe die Wendepunkte der Hubkonturfunktion gegenüber einer 10-Flügel-Standardkontur um ca. 3° in Drehrichtung verschoben sind. Das hat den Vorteil, dass die Überlagerung der kinematischen Volumenstrompulsation von Oberflügel- und Unterflügelpumpe sich gegenseitig optimal ergänzt. Ansonsten besitzen die Wendepunkte einen Abstand von ca. 2,5 x Flügelteilung (die Flügelteilung bei der 10-Flügel-Pumpe ist 36°).Furthermore, a pump is preferred in which, in the case of a 10-blade pump, the turning points of the Hubkonturfunktion are shifted relative to a 10-wing standard contour by about 3 ° in the direction of rotation. This has the advantage that the superposition of the kinematic volumetric flow pulsation of the wing and underfloor pump complement each other optimally. Otherwise, the turning points have a distance of about 2.5 x wing pitch (the wing pitch in the 10-wing pump is 36 °).
Die Erfindung wird nun anhand der Figuren beschrieben.
-
zeigt die Förderkontur einer 10-Flügel-Standardpumpe.Figur 1 -
Figur 2 zeigt die Förderkontur einer erfindungsgemäßen 10-Flügel-Pumpe. -
zeigt die Förderkontur einer erfindungsgemäßen 12-Flügel-Pumpe.Figur 3 -
Figur 4 zeigt die Funktion des Hubes einer erfindungsgemäßen 12-Flügel-Förderkontur über dem Drehwinkel. -
zeigt die Funktion der Ableitung des Hubes nach dem Drehwinkel einer erfindungsgemäßen 12-Flügel-Förderkontur über dem Drehwinkel.Figur 5 -
Figur 6 zeigt die Funktion der Ableitung des Zellenvolumens nach dem Drehwinkel, aufgetragen über dem Drehwinkel, einer erfindungsgemäßen 12-Flügel-Förderkontur.
-
FIG. 1 shows the conveying contour of a 10-wing standard pump. -
FIG. 2 shows the conveying contour of a 10-blade pump according to the invention. -
FIG. 3 shows the conveying contour of a 12-blade pump according to the invention. -
FIG. 4 shows the function of the stroke of a 12-wing conveyor contour according to the invention over the rotation angle. -
FIG. 5 shows the function of the derivative of the stroke according to the rotation angle of a 12-wing conveyor contour according to the invention over the rotation angle. -
FIG. 6 shows the function of the derivative of the cell volume according to the angle of rotation, plotted against the angle of rotation, a 12-wing conveyor contour according to the invention.
In
Der Anstiegsbereich hat im Winkelpunkt 7 bei 45° einen Wendepunkt in der Hubkonturfunktion (Radiusänderung als Funktion des Drehwinkels) und endet schließlich bei 69° im Winkelpunkt 9. Die Lage der Wendepunkte der Hubkonturfunktion lässt sich durch die Position der Maxima und der Minima der ersten Ableitung der Hubkonturfunktion über dem Drehwinkel (genau) bestimmen. Vom Winkelpunkt 9, also von 69°, bis zum Winkelpunkt 11, also bis 111 °, erstreckt sich der so genannte Großkreisbereich, der allerdings durch den so genannten Fall, d.h. eine leichte Verringerung des Hubes radial nach innen in Abhängigkeit des Drehwinkels, dafür sorgt, dass die Flügelköpfe immer an der Kontur angepresst bleiben. Der Großkreisbereich mit dem Fall kann auch so definiert werden, dass sein Anfang das Maximum der Hubkonturfunktion bildet und sein Ende gegeben ist, sobald keine Tangentenstetigkeit mehr in der ersten und/oder zweiten Ableitung der Hubkonturfunktion gegeben ist. Vom Punkt 11, also bei 111°, beginnt der eigentliche Abstiegsbereich, welcher bis 165°, also bis zum Winkelpunkt 15 verläuft und somit den Druckbereich der Flügelzellenpumpe darstellt, da sich nun das Hubvolumen verkleinert. Der Abstiegsbereich hat im Winkelpunkt 13, d.h. bei 135°, wiederum einen Wendepunkt in der Hubkonturfunktion. Der Wendepunkt im Punkt 7, d.h. im Anstiegsbereich, und der Wendepunkt im Punkt 13, d.h. im Abstiegsbereich, sind um ca. 90° voneinander beabstandet. Da die 10-Flügel-Pumpe eine Flügelteilung von 36° besitzt, entspricht das dem 2,5-fachen der Flügelteilung. Der Wendepunkt im Abstiegsbereich und der Wendepunkt im nächsten Anstiegsbereich sind also auch um das 2,5-fache der Flügelteilung zueinander beabstandet. Außerdem ist die Lage der Wendepunkte symmetrisch zur Hauptachse der Kontur. Von 165°, d.h. vom Winkelpunkt 15, bis zu 180°, d.h. bis zum Winkelpunkt 17, erstreckt sich wiederum eine Hälfte des nächsten Kleinkreisbereiches. Ab 180° bis 360°, d.h. vom Winkelpunkt 17 bis zurück zum Winkelpunkt 3, wiederholt sich die Förderkontur symmetrisch zur bisher beschriebenen Förderkonturhälfte.The rise area has an inflection point in the Hubkonturfunktion (radius change as a function of the angle of rotation) at
In
In
Aufgrund der geringeren Flügelteilung von 30° bei der 12-Flügel-Pumpe beträgt beispielsweise die Differenz der Großkreislänge zur Flügelteilung jetzt 22° gegenüber 6° bei der Standard-10-Flügel-Kontur und 13° gegenüber der verbesserten10-Flügel-Kontur aus
Auch bei dieser Kontur ist der Verdichtungsbereich etwas kürzer als der Ansaugbereich, und die Wendepunkte sind als Paar minimal etwas weiter gedreht.Even with this contour, the compression area is slightly shorter than the intake area, and the turning points are minimally a little further rotated as a pair.
In
In
In
Claims (5)
- Vane cell pump or roller cell pump with a double-stroke delivery contour, wherein the delivery contour has at least one rise region which constitutes a suction region, at least one large circle region which constitutes a first separating region, at least one fall region which constitutes a pressure region, and at least one small circle region which constitutes a further separating region, and the pump has, within the delivery contour, a rotor with radially displaceable vanes or rollers in radial slots, characterized in that the angular range of the large circle of the delivery contour is larger than the angular range of the fall region, and in that the angular range of the rise region, the so-called suction region, is larger than the angular range of the fall region.
- Pump according to Claim 1, characterized in that- in a pump with 10 vanes, the large circle region is substantially 49°, the rise region is substantially 54°, the fall region is substantially 47° and the small circle region is substantially 30°,- in a pump with 12 vanes, the large circle region is substantially 52°, the rise region is substantially 54°, the fall region is substantially 50° and the small circle region is substantially 24°.
- Pump according to either of the preceding claims, characterized in that the large circle region is larger than the small circle region.
- Pump according to Claim 2 or 3, characterized in that, in the 12-vane pump, the reversal points of the displacement contour function in the direction from the rise region to the fall region have approximately an angular spacing of 3.5 x vane pitch (vane pitch = 30°) and the reversal points of the displacement contour function in the direction from the fall region to the rise region have approximately an angular spacing of 2.5 x vane pitch.
- Pump according to Claim 2 or 3, characterized in that, in the 10-vane pump, the reversal points of the displacement contour function are shifted by about 3° in the direction of rotation with respect to a so-called 10-vane standard delivery contour according to Figure 1.
Applications Claiming Priority (2)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
DE10329284 | 2003-06-30 | ||
PCT/DE2004/001284 WO2005001289A2 (en) | 2003-06-30 | 2004-06-19 | Vane-cell pump or a roll-cell pump |
Publications (3)
Publication Number | Publication Date |
---|---|
EP1642030A2 EP1642030A2 (en) | 2006-04-05 |
EP1642030B1 true EP1642030B1 (en) | 2016-04-13 |
EP1642030B2 EP1642030B2 (en) | 2019-12-04 |
Family
ID=33521180
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
EP04738734.5A Expired - Lifetime EP1642030B2 (en) | 2003-06-30 | 2004-06-19 | Pump |
Country Status (7)
Country | Link |
---|---|
US (1) | US7922469B2 (en) |
EP (1) | EP1642030B2 (en) |
JP (1) | JP4653739B2 (en) |
KR (1) | KR101162780B1 (en) |
CN (1) | CN101052806B (en) |
DE (1) | DE102004030478A1 (en) |
WO (1) | WO2005001289A2 (en) |
Families Citing this family (2)
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---|---|---|---|---|
JP5762202B2 (en) * | 2011-08-02 | 2015-08-12 | 日立オートモティブシステムズ株式会社 | Variable displacement vane pump |
US10227979B2 (en) * | 2016-10-19 | 2019-03-12 | Ford Global Technologies, Llc | Vane spacing for a variable displacement oil pump |
Citations (6)
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US2588430A (en) | 1945-10-15 | 1952-03-11 | Odin Corp | Rotary blade pump |
DE1011284B (en) | 1951-10-23 | 1957-06-27 | Charles Scott Prendergast | Pump or motor |
US2831631A (en) | 1953-07-27 | 1958-04-22 | Petersen Entpr | Rotary compressor |
DE2438707A1 (en) | 1973-10-03 | 1975-04-10 | Abex Corp | ROTARY VALVE FLOW MACHINE |
DE68905742T2 (en) | 1988-10-05 | 1993-10-21 | Vickers Inc | Power drive element. |
DE4327106A1 (en) | 1993-08-12 | 1995-02-16 | Salzkotten Tankanlagen | Vane pump |
Family Cites Families (12)
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US2731919A (en) * | 1956-01-24 | Prendergast | ||
JPH0674790B2 (en) * | 1983-03-08 | 1994-09-21 | 株式会社豊田中央研究所 | Fluid pressure vane pump |
CN86206061U (en) * | 1986-08-15 | 1987-06-10 | 杨斌 | Stator for double-acting vaned oil pump |
JPH0378987U (en) * | 1989-12-04 | 1991-08-12 | ||
JP3080185B2 (en) * | 1991-07-10 | 2000-08-21 | カヤバ工業株式会社 | Vane pump device |
DE19626211C2 (en) * | 1996-06-29 | 2002-03-14 | Luk Fahrzeug Hydraulik | Vane pump |
DE19710378C1 (en) * | 1996-12-23 | 1998-03-12 | Luk Fahrzeug Hydraulik | Sliding-vane-type rotary pump |
EP0851123B1 (en) * | 1996-12-23 | 2003-07-09 | LuK Fahrzeug-Hydraulik GmbH & Co. KG | Vane pump |
DE19900926B4 (en) * | 1998-01-28 | 2015-01-22 | Magna Powertrain Bad Homburg GmbH | pump |
DE10027990A1 (en) | 2000-06-08 | 2001-12-20 | Luk Fahrzeug Hydraulik | Vane or roller pump has intermediate hydraulic capacity which can be pressurized via connection to pressure connection |
JP2003097453A (en) * | 2001-09-25 | 2003-04-03 | Hitachi Unisia Automotive Ltd | Variable displacement vane pump |
JP2003097454A (en) * | 2001-09-26 | 2003-04-03 | Hitachi Unisia Automotive Ltd | Vane pump |
-
2004
- 2004-06-19 WO PCT/DE2004/001284 patent/WO2005001289A2/en active Application Filing
- 2004-06-19 EP EP04738734.5A patent/EP1642030B2/en not_active Expired - Lifetime
- 2004-06-19 JP JP2006517945A patent/JP4653739B2/en not_active Expired - Lifetime
- 2004-06-19 CN CN2004800187205A patent/CN101052806B/en not_active Expired - Lifetime
- 2004-06-19 US US10/562,260 patent/US7922469B2/en active Active
- 2004-06-19 KR KR1020057024413A patent/KR101162780B1/en active IP Right Grant
- 2004-06-24 DE DE102004030478A patent/DE102004030478A1/en not_active Ceased
Patent Citations (6)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US2588430A (en) | 1945-10-15 | 1952-03-11 | Odin Corp | Rotary blade pump |
DE1011284B (en) | 1951-10-23 | 1957-06-27 | Charles Scott Prendergast | Pump or motor |
US2831631A (en) | 1953-07-27 | 1958-04-22 | Petersen Entpr | Rotary compressor |
DE2438707A1 (en) | 1973-10-03 | 1975-04-10 | Abex Corp | ROTARY VALVE FLOW MACHINE |
DE68905742T2 (en) | 1988-10-05 | 1993-10-21 | Vickers Inc | Power drive element. |
DE4327106A1 (en) | 1993-08-12 | 1995-02-16 | Salzkotten Tankanlagen | Vane pump |
Also Published As
Publication number | Publication date |
---|---|
WO2005001289A2 (en) | 2005-01-06 |
DE102004030478A1 (en) | 2005-01-20 |
CN101052806B (en) | 2010-12-08 |
US20070128065A1 (en) | 2007-06-07 |
WO2005001289A3 (en) | 2007-03-22 |
JP4653739B2 (en) | 2011-03-16 |
KR101162780B1 (en) | 2012-07-04 |
CN101052806A (en) | 2007-10-10 |
KR20060032597A (en) | 2006-04-17 |
EP1642030B2 (en) | 2019-12-04 |
US7922469B2 (en) | 2011-04-12 |
EP1642030A2 (en) | 2006-04-05 |
JP2007524027A (en) | 2007-08-23 |
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