EP2286088B1 - Pump - Google Patents
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- Publication number
- EP2286088B1 EP2286088B1 EP09741806A EP09741806A EP2286088B1 EP 2286088 B1 EP2286088 B1 EP 2286088B1 EP 09741806 A EP09741806 A EP 09741806A EP 09741806 A EP09741806 A EP 09741806A EP 2286088 B1 EP2286088 B1 EP 2286088B1
- Authority
- EP
- European Patent Office
- Prior art keywords
- side plate
- pump
- outer ring
- outer edge
- housing
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
- Not-in-force
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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
- 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
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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
- F04C15/0003—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
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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
- F04C2/3441—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 one line or continuous surface substantially parallel to the axis of rotation
- F04C2/3442—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 one line or continuous surface substantially parallel to the axis of rotation the surfaces of the inner and outer member, forming the working space, being surfaces of revolution
Definitions
- the invention relates to a pump, in particular vane pump with variable delivery volume, according to the preamble of claim 1.
- Pumps of the type discussed here are, for example WO 2007/036189 A1 , out DE 18 02 021 A1 or off DE 100 27 811 A1 , considered as the closest prior art, known.
- Such pumps such as vane pumps, roller-cell pumps or the like, serve to convey, for example, hydraulic oil and have a pump housing and a cam ring arranged therein, which surrounds a rotor cooperating with a shaft. They also have an outer ring and at least one cooperating with this side plate.
- Pumps of the type discussed here have to change the delivery volume on an adjustable against the force of a spring cam ring, so that the delivery volume can be reduced or increased depending on the position of the cam ring accordingly.
- the at least one side plate is arranged in the axial direction, ie in the direction of the axis of rotation of the shaft, next to the lifting ring and forms a lateral boundary of the enclosed between the wings, the rotor, the lifting ring and a second lateral boundary conveyor cells.
- the side plate is supported on the outer ring, which in turn on the pump housing or supported on the housing cover of the pump.
- the outer ring serves to ensure a defined distance between the side plate and the rotor or the lifting ring, namely the so-called design clearance. He thus serves in known pumps as a spacer between the side plate and the rotor or the cam ring and has a correspondingly small wall thickness.
- the cam ring facing away from the back of the side plate is completely or only partially applied to the pump pressure. Due to the fact that the pressurized areas on the back of the side plate are larger than that on the cam ring side facing the side plate, this deforms under the load of the hydraulic oil such that within the inner diameter of the outer ring, the distance between the rotor or the cam ring and the side plate is smaller, at the same time the side plate in the area outside the inner diameter lifts with increasing distance from the inner diameter of the outer ring.
- the side plate is pressed in a depressurized state of the pump, the side plate only by a biasing element, such as an elastic seal or a spring against the outer ring, so that the parts are in the pressureless state together and can start the pump.
- a biasing element such as an elastic seal or a spring against the outer ring
- These biasing forces are low compared to the compressive forces acting on the side plate during operation.
- Pumps that allow a change in the delivery volume include an outer ring having a large inner diameter. Due to the large inner diameter, the diameter of the side plate increases, so that the deflection of the side plate can assume considerable values, which in turn a large interpretation game, so a large distance between the side plate and the cam ring, or the rotor is required.
- the object of the invention is therefore to provide a pump which does not have the disadvantages mentioned above, which in particular has a small bearing distance and compact builds.
- a pump which has the features of claim 1.
- the pump is characterized in that the at least one side plate in the axial direction between the pump housing and the outer ring, at least in a radially outer edge region, ie in the region outside the inner diameter of the outer ring in the unpressurized and pressurized state of the pump is firmly clamped and fixed so that a lifting of the side plate under load in the outer edge region is substantially avoided, and that an edge surface of the at least one side plate in the outer edge region on the outer ring and arranged on the back, so opposite edge surface of the Side plate rests against a projection of the pump housing.
- the side plate is fixed or clamped in the outer edge region in the axial direction between the outer ring and the pump housing.
- An axial clamping of the side plate, the pump housing and the outer ring can be done by means of a screw.
- the fixed axial fixation in the region of an outer edge of the side plate leads to the reduction of the deformation of the side plate under pressurization. Because the side plate is clamped or fixed in the outer edge region in the axial direction, that is to say in the direction of the axis of rotation of the shaft, lifting of the side plate on the outer edge of the outer ring is prevented, that is to say in the region outside the inner diameter of the outer ring. making the side plate more stable overall and avoiding excessive deformation of the side plate under load.
- a pump which is characterized in that at least on the outer edge region, that is in the region outside the inner diameter of the outer ring, the at least one side plate in the axial direction a force is exerted that is so large that in the direction of Rotary axis of the shaft, the side plate is firmly fixed at least in the outer edge region in the axial direction, so that deformation of the side plate under pressure is substantially reduced.
- a further preferred pump is provided that two side plates are provided, which, viewed in the axial direction, are arranged on opposite sides of the outer ring.
- An axial tension or fixation can thus also be provided in the case of an adjustable vane-cell pump pressure-compensated on both sides.
- the side plate is clamped in an outer edge region on the outer ring so that a lifting of the side plate is avoided at the outer edge.
- a screw connection of the pump housing, the two side plates, the outer ring and the housing cover an axial clamping.
- one of the two side plates in the outer edge region on the pump housing is applied and the other side plate for generating an axial force in the outer edge region cooperates with at least one elastic element, for example with a plate spring.
- at least one elastic element for example with a plate spring.
- a pump is preferred, which is characterized in that a side plate is at least partially disposed on the pump housing and the respective other side plate on the housing cover.
- a side plate is at least partially disposed on the pump housing and the respective other side plate on the housing cover.
- the pump can be dispensed with the elastic elements.
- a pump is preferred, which is characterized in that the ratio of an outer radial section to an inner radial section of the side plate is ⁇ 0.2.
- a particularly secure axial fixation in the outer region of the side plate is possible, whereby a deformation of the side plate under pressure is substantially reduced.
- FIG. 1 shows a schematic sectional view of a known from the prior art pump 1.
- the pump 1 shown here is purely by way of example a vane pump with variable delivery volume, as for example in WO 2007/036189 A1 is described.
- Such pumps are used in particular for consumers with, depending on the operating state, greatly changing volumetric flow requirements, such as, for example, in power steering devices for motor vehicles.
- the pump 1 has a pump housing 3 and a housing cover 5. Further, a shaft 7 and a rotatably connected thereto rotor 9 are provided.
- the shaft 7 is mounted in the pump housing 3 by means of two radial bearings 11 and 11 ', which have a bearing distance a to each other.
- shaft seals 13 and 13 ' provided on the shaft 7, which prevent leakage of fluid, in particular leakage oil from the pump 1.
- At least one radial slot is provided, in which a radially displaceable wing 15 is arranged.
- the vane 15 is displaced out of the slot so that it slides along the inner surface of a cam ring 17 surrounding the rotor 9.
- an outer ring 19 is provided, on which a side plate 21 is supported, which has an opening 22 for the passage of the shaft 7.
- the cam ring 17 is freely displaceable in the outer ring 19. On the side facing away from the side plate 21 of the outer ring 19, this is supported on the housing cover 5 from.
- the outer ring 19 serves to ensure a defined distance b and b 'between the side plate 21 and the housing cover 5 and the rotor 9 and the cam ring 17, wherein the distances b and b' together give the interpretation game.
- the side plate 21 In the pressureless state of the pump 1, the side plate 21 is pressed by a biasing element, here in the form of the elastic seals 25 or even by a spring, not shown here, against the outer ring 19. In this case, the side plate rests against the end face of the outer ring. In the pressurized state of the pump 1, however, the back 23 of the side plate 21 is fully or partially applied to the pump pressure.
- the vane pump shown here is thus a one-sided pressure compensated pump 1.
- a gap S is provided, which should also ensure that the housing cover 5 cooperates with a defined stop 26 of the pump housing 3.
- FIG. 2 shows a schematic sectional view of the pump 1 according to FIG. 1 under load.
- the same parts are provided with the same reference numerals, so far as the description to FIG. 1 is referenced.
- FIG. 2 makes it clear that the forces resulting from a pressurization of the rear side 23 on the side plate 21 outweigh the forces exerted on the side plate 21 from the side facing the rotor 9.
- FIG. 2 also shows that the side plate 21 is deformed by the pressurization on the back of the side plate 21 within the inner edge K of the outer ring 19 in the direction of the rotor 9, wherein At the same time it lifts off the outer ring 19 outside the inner edge K of the outer ring 19 at the outer edge.
- the contact surface between the side plate 21 and the end face of the outer ring 19 reduces under load up to a "contact line", which is defined on the end face of the outer ring by the inner edge K.
- the distance b must therefore be so great that a contact of the side plate 21 and the rotor 9 is avoided even with a large deformation of the side plate 21, that is at maximum pump pressure and maximum swung-out cam ring. It is also possible to form the side plate 21 thicker, so that the deformation is reduced under pressure.
- both solutions have the disadvantage that the bearing distance a would increase, which in addition an enlargement of the shaft diameter would be required to prevent bending of the shaft 7. As a result, the axial and radial length and the weight of the pump 1 would increase.
- FIG. 3 shows a schematic sectional view of a pump 1 of a first embodiment of the invention. Same parts are with provided with the same reference numerals, so that reference is made to the description of the preceding figures.
- the pump 1 shown here has at least one pressure-compensated side plate 21, preferably with an enlarged diameter.
- the outer ring 19 has a larger diameter than the known from the prior art outer rings.
- the side plate 21 and the outer ring 19 extend further in the radial direction beyond the inner edge K on the end face of the outer ring 19 also, ie perpendicular to the axis of rotation D, as in the in the Figures 1 and 2 shown pumps 1.
- FIG. 3 makes it clear that the side plate 21 is supported on the outer ring 19 here as well.
- the at least one side plate 21 has a, seen in the radial direction, outer edge region 27, in which the side plate 21 is supported with a first edge surface 29 on the outer ring 19. On the side opposite the first edge surface 29, the side plate 21 is supported with a second edge surface 31 on a projection 33 of the pump housing 3. By the projection 33, the gap S between the side plate 21 and the pump housing 3 is formed.
- the side plate 21 is arranged between the projection 33 of the pump housing 3 and the outer ring 19.
- An axial clamping of the side plate 21 with the pump housing 3 and the outer ring 19 is here purely by way of example in FIG 3 merely indicated screw 35, which passes through the housing cover 5, the outer ring 19, the side plate 21 and the pump housing 3.
- screw 35 By means of the screw 35, an axial force is exerted on all the above-mentioned components, ie also on the side plate 21, so that it is clamped between the outer ring 19 and the projection 33.
- the side plate 21 between the pump housing 3 and the outer ring 19 axially, ie in the direction of the rotation axis D, fixed.
- the side plate 21 is firmly clamped at least in the outer edge region 27 in the unpressurized and pressurized state of the pump 1, in the axial direction, ie in the direction of the axis of rotation D of the shaft 7.
- An in FIG. 2 shown lifting the side plate 21 from the outer edge of the outer ring 19 is thus avoided.
- the deformation of the side plate 21 under load so when pressurizing the back 23 with hydraulic oil, significantly reduced, so that can be dispensed with an increase in the interpretation game and a thicker design of the side plate 21 to prevent excessive bending , Rather, even thinner side plates 21 can be used, which allow a shortening of the bearing distance a and thereby a reduction in the weight and the installation space of the pump 1.
- the projection 33 seen in the radial direction, is formed as wide as the outer ring 19, so that the edge surfaces 29 and 31 are the same size.
- FIG. 4 shows a schematic sectional view of a second embodiment of a pump 1 under load. Same parts are provided with the same reference numerals, so that reference is made to the description of the preceding figures.
- the embodiment according to FIG. 4 shows a double-sided pressure compensated pump 1, in which therefore two side plates 21 and 21 'are provided.
- the arrangement of the side plate 21 corresponds to the in FIG. 3 shown, so reference is made in this regard to the preceding description.
- the second side plate 21 ' is disposed through the outer ring 19 at a distance b', the so-called interpretation game, from the rotor 9 and the cam ring 17.
- the side plate 21 ' has the same radius R as the side plate 21 measured from the rotation axis D of the shaft 7 to the outer edge c of the side plates 21, 21'.
- FIG. 4 makes it clear that the side plate 21 'is arranged by the preferably integrally formed with the housing cover 5 projection 37 at a distance from the housing cover 5, so that between this and the side plate 21', a gap S 'is formed for receiving hydraulic oil, in the
- elastic sealing elements 25 'and / or a non-illustrated spring element can be arranged.
- the wall 43 of the pump housing 3 can be substantially thinner.
- FIG. 5 shows a schematic sectional view of a third embodiment of a pump 1.
- the same parts are the same Reference numerals provided so that reference is made to the description of the preceding figures.
- FIG. 5 shows a double-sided pressure compensated vane pump under load. Accordingly, according to the in FIG. 4 shown embodiment, two side plates 21, 21 'is provided. The arrangement of the side plate 21 corresponds to that in the Figures 3 and 4 shown, so here is not further discussed.
- an elastic element 45 is provided, which is formed here purely by way of example as a plate spring.
- the elastic element 45 is supported on the one hand on the housing cover 5 and on the other hand on the outer edge region 27 'on the side plate 21' from.
- the housing cover 5 is screwed to the pump housing 3 by means of a screw 47 only indicated here.
- Other types of cover and housing are also possible.
- the wall portion 43 of the pump housing 3 is thicker here in the radial direction.
- the elastic element 45 is supported on the one hand on the housing cover 5 and on the other hand in the outer edge region 27 'on the side plate 21' from. As a result, an axial force is exerted on the side plates 21 and 21 '.
- the elastic member 45 is different from the elastic members 25 and 25 '(FIG. FIG. 1 ) in that it exerts a significantly greater force on the side plates 21 and 21 '. This force is according to the invention so great that the lifting the side plates 21, 21 'in the outer edge regions 27, 27' is prevented from the outer ring 19, that is, in this embodiment, the side plates 21 and 21 'are axially clamped in the pump. It can also be provided that the elastic element 45 is supported on the side plate 21 and on the pump housing 3.
- the pump 1 according to the present invention is in the FIGS. 3 to 5 each shown under load; the side plates 21, 21 'are thus subjected to a pressure. It can be clearly seen that different than in the FIG. 2 shown conventional pump 1 in the pressurized state, the side plates 21, 21 'does not lift off at the outer edge of the outer ring 19 and the distance b, b' between the rotor 9 and the side plates 21, 21 ', although smaller, excessive bending but through the solid axial clamping of the side plates 21, 21 'is prevented.
- the pump 1 proposed here has at least one pressure-compensated side plate 21, which has a larger radius R than conventional side plates.
- the pump 1 according to the invention also preferably has an outer ring 19 with a larger diameter.
- the side plates 21, 21 ' are axially fixed in an outer edge region 27, 27' between the outer ring 19 and the pump housing 3, or the housing cover 5 or an elastic element 45, for example by means of a screw.
- the pump 1 proposed here can also be used with adjustable vane pumps, which are operated without pressure or at low pressures. In these operating conditions, there is a risk that the side plates 21, 21 'stand out from the outer ring 19 due to pressure peaks in the work chambers of the pump 1, not shown here, and thus are damaged. In the embodiments of the invention described herein, the pressing force of the side plates 21, 21 'can be increased without increasing the deformation.
Abstract
Description
Die Erfindung betrifft eine Pumpe, insbesondere Flügelzellenpumpe mit veränderbarem Fördervolumen, gemäß Oberbegriff des Anspruchs 1.The invention relates to a pump, in particular vane pump with variable delivery volume, according to the preamble of
Pumpen der hier angesprochenen Art sind beispielsweise aus
Aufgabe der Erfindung ist es daher, eine Pumpe zu schaffen, welche die oben genannten Nachteile nicht aufweist, die insbesondere einen geringen Lagerabstand aufweist und kompakt baut.The object of the invention is therefore to provide a pump which does not have the disadvantages mentioned above, which in particular has a small bearing distance and compact builds.
Zur Lösung dieser Aufgabe wird eine Pumpe vorgeschlagen, welche die Merkmale des Anspruchs 1 aufweist. Die Pumpe zeichnet sich dadurch aus, dass die mindestens eine Seitenplatte zumindest in einem in radialer Richtung gesehenen äußeren Randbereich, das heißt in dem Bereich außerhalb des Innendurchmessers des Außenrings, im drucklosen und im druckführenden Zustand der Pumpe in axialer Richtung zwischen dem Pumpengehäuse und dem Außenring so fest eingespannt und damit fixiert ist, dass ein Abheben der Seitenplatte unter Last in dem äußeren Randbereich im Wesentlichen vermieden wird, und dass eine Randfläche der mindestens einen Seitenplatte in dem äußeren Randbereich an dem Außenring und eine auf der Rückseite angeordnete, also gegenüberliegende Randfläche der Seitenplatte an einem Vorsprung des Pumpengehäuses anliegt. Auf diese Weise ist die Seitenplatte im äußeren Randbereich in axialer Richtung zwischen dem Außenring und dem Pumpengehäuse fixiert beziehungsweise eingespannt. Eine axiale Verspannung der Seitenplatte, des Pumpengehäuses und des Außenrings kann dabei mittels einer Verschraubung erfolgen. Die feste axiale Fixierung im Bereich eines äußeren Rands der Seitenplatte führt zur Reduzierung der Verformung der Seitenplatte unter Druckbeaufschlagung. Dadurch, dass die Seitenplatte in axialer Richtung, also in Richtung der Drehachse der Welle gesehen, im äußeren Randbereich eingespannt beziehungsweise fixiert ist, wird ein Abheben der Seitenplatte am Außenrand des Außenrings verhindert, das heißt in dem Bereich außerhalb des Innendurchmessers des Außenrings, wodurch die Seitenplatte insgesamt stabiler und eine übermäßige Verformung der Seitenplatte unter Last vermieden wird. Dadurch wird verhindert, dass die Seitenplatte mit dem Hubring beziehungsweise mit dem Rotor in Kontakt kommt, woraus ein Klemmen und ein Verschleiß dieser Elemente resultieren würde. Bei der Vorgabe eines festgelegten Auslegungsspiels, also des Abstands zwischen der Seitenplatte und dem Rotor, kann auf diese Weise die Seitenplatte dünner ausgestaltet sein, woraus eine Reduzierung des Lagerabstandes der Welle resultiert. Dadurch können wiederum das Gewicht der Pumpe und der Bauraum erheblich reduziert werden. Besonders bevorzugt wird eine Pumpe, die sich dadurch auszeichnet, dass zumindest auf den äußeren Randbereich, das heißt in dem Bereich außerhalb des Innendurchmessers des Außenrings, der mindestens einen Seitenplatte in axialer Richtung eine Kraft ausgeübt wird, die so groß ist, dass in Richtung der Drehachse der Welle die Seitenplatte zumindest in dem äußeren Randbereich in axialer Richtung fest fixiert ist, sodass eine Verformung der Seitenplatte unter Druckbeaufschlagung wesentlich reduziert wird.To solve this problem, a pump is proposed which has the features of
Bei einer weiteren bevorzugten Pumpe ist vorgesehen, dass zwei Seitenplatten vorgesehen sind, die, in axialer Richtung gesehenen, auf gegenüberliegenden Seiten des Außenrings angeordnet sind. Eine axiale Verspannung, beziehungsweise Fixierung, kann somit auch bei einer verstellbaren, beidseitig druckkompensierten Flügelzellenpumpe vorgesehen sein. Vorzugsweise ist auch bei dieser Ausführungsform vorgesehen, dass die Seitenplatte in einem äußeren Randbereich an dem Außenring so eingespannt ist, dass ein Abheben der Seitenplatte am Außenrand vermieden wird. Auch hier kann eine axiale Verspannung mittels einer Verschraubung des Pumpengehäuses, der beiden Seitenplatten, des Außenrings sowie des Gehäusedeckels erfolgen.In a further preferred pump is provided that two side plates are provided, which, viewed in the axial direction, are arranged on opposite sides of the outer ring. An axial tension or fixation can thus also be provided in the case of an adjustable vane-cell pump pressure-compensated on both sides. Preferably, it is also provided in this embodiment that the side plate is clamped in an outer edge region on the outer ring so that a lifting of the side plate is avoided at the outer edge. Here too can be done by means of a screw connection of the pump housing, the two side plates, the outer ring and the housing cover an axial clamping.
Bei einer weiteren bevorzugten Pumpe ist vorgesehen, dass eine der beiden Seitenplatten in dem äußeren Randbereich an dem Pumpengehäuse anliegt und die andere Seitenplatte zur Erzeugung einer axialen Kraft in dem äußeren Randbereich mit mindestens einem elastischen Element, beispielsweise mit einer Tellerfeder, zusammenwirkt. Bei dieser Ausführungsform ist es ausreichend, wenn eine Verschraubung lediglich des Pumpengehäuses mit dem Gehäusedeckel erfolgt. Eine axiale Kraft auf die beiden Seitenplatten wird lediglich durch das elastische Element erzeugt, welches zwischen mindestens einer Seitenplatte und dem Pumpengehäuse oder dem Gehäusedeckel angeordnet ist.In a further preferred pump it is provided that one of the two side plates in the outer edge region on the pump housing is applied and the other side plate for generating an axial force in the outer edge region cooperates with at least one elastic element, for example with a plate spring. In this embodiment, it is sufficient if a screw connection takes place only of the pump housing with the housing cover. An axial force on the two side plates is generated only by the elastic element, which is arranged between at least one side plate and the pump housing or the housing cover.
Weiterhin wird eine Pumpe bevorzugt, die sich dadurch auszeichnet, dass eine Seitenplatte zumindest bereichsweise an dem Pumpengehäuse und die jeweils andere Seitenplatte an dem Gehäusedeckel angeordnet ist. Bei dieser Ausführungsform der Pumpe kann auf das elastische Elemente verzichtet werden.Furthermore, a pump is preferred, which is characterized in that a side plate is at least partially disposed on the pump housing and the respective other side plate on the housing cover. In this embodiment of the pump can be dispensed with the elastic elements.
Schließlich wird eine Pumpe bevorzugt, die sich dadurch auszeichnet, dass das Verhältnis einer äußeren radialen Teilstrecke zu einer inneren radialen Teilstrecke der Seitenplatte ≥ 0,2 beträgt. Bei dieser Ausgestaltung ist eine besonders sichere axiale Fixierung im äußeren Bereich der Seitenplatte möglich, wodurch eine Verformung der Seitenplatte unter Druckbeaufschlagung wesentlich vermindert wird.Finally, a pump is preferred, which is characterized in that the ratio of an outer radial section to an inner radial section of the side plate is ≥ 0.2. In this embodiment, a particularly secure axial fixation in the outer region of the side plate is possible, whereby a deformation of the side plate under pressure is substantially reduced.
Die Erfindung wird im Folgenden anhand der Zeichnung näher erläutert. Es zeigen:
Figur 1- eine schematische Schnittdarstellung einer aus dem Stand der Technik bekannten Pumpe;
- Figur 2
- eine schematische Schnittdarstellung der Pumpe gemäß
unter Last;Figur 1 Figur 3- eine schematische Schnittdarstellung einer ersten Ausführungsform einer druckführenden Pumpe gemäß der Erfindung;
- Figur 4
- eine schematische Schnittdarstellung einer zweiten Ausführungsform einer druckführenden Pumpe gemäß der Erfindung, und
Figur 5- eine schematische Darstellung einer dritten Ausführungsform einer druckführenden Pumpe gemäß der Erfindung.
- FIG. 1
- a schematic sectional view of a known from the prior art pump;
- FIG. 2
- a schematic sectional view of the pump according to
FIG. 1 under load; - FIG. 3
- a schematic sectional view of a first embodiment of a pressurized pump according to the invention;
- FIG. 4
- a schematic sectional view of a second embodiment of a pressurized pump according to the invention, and
- FIG. 5
- a schematic representation of a third embodiment of a pressurized pump according to the invention.
Die Pumpe 1 weist ein Pumpengehäuse 3 und einen Gehäusedeckel 5 auf. Ferner sind eine Welle 7 und ein drehfest mit dieser verbundener Rotor 9 vorgesehen. Die Welle 7 ist in dem Pumpengehäuse 3 mittels zweier Radiallager 11 und 11' gelagert, die einen Lagerabstand a zueinander aufweisen. Ferner sind Wellendichtringe 13 und 13' an der Welle 7 vorgesehen, die einen Austritt von Fluid, insbesondere Leckageöl, aus der Pumpe 1 verhindern.The
In dem Rotor 9 ist mindestens ein radialer Schlitz vorgesehen, in dem ein radial verlagerbarer Flügel 15 angeordnet ist. Bei einer Rotation des Rotors 9 um die Drehachse D der Welle 7 wird der Flügel 15 aus dem Schlitz heraus verlagert, sodass er an der Innenfläche eines den Rotor 9 umgebenden Hubrings 17 entlang gleitet. Radial außerhalb des Hubrings 17 ist ein Außenring 19 vorgesehen, an dem sich eine Seitenplatte 21 abstützt, die eine Öffnung 22 zur Durchführung der Welle 7 aufweist. Der Hubring 17 ist in dem Außenring 19 frei verlagerbar. Auf der von der Seitenplatte 21 abgewandten Seite des Außenrings 19 stützt sich dieser an dem Gehäusedeckel 5 ab.In the
Der Außenring 19 dient dazu, einen definierten Abstand b und b' zwischen der Seitenplatte 21 beziehungsweise dem Gehäusedeckel 5 und dem Rotor 9 und dem Hubring 17 zu gewährleisten, wobei die Abstände b und b' zusammen das Auslegungsspiel ergeben.The
Im drucklosen Zustand der Pumpe 1 wird die Seitenplatte 21 durch ein Vorspannelement, hier in Form von den elastischen Dichtungen 25 oder aber auch durch eine hier nicht dargestellte Feder, gegen den Außenring 19 gedrückt. Dabei liegt die Seitenplatte an der Stirnseite des Außenrings an. Im druckbeaufschlagten Zustand der Pumpe 1 hingegen wird die Rückseite 23 der Seitenplatte 21 vollständig oder bereichsweise mit dem Pumpendruck beaufschlagt. Bei der hier dargestellten Flügelzellenpumpe handelt es sich somit um eine einseitig druckkompensierte Pumpe 1. Hierzu ist zwischen dem Pumpengehäuse 3 und der Seitenplatte 21 ein Spalt S vorgesehen, der außerdem sicher stellen soll, dass der Gehäusedeckel 5 mit einem definierten Anschlag 26 des Pumpengehäuses 3 zusammenwirkt. Im druckbeaufschlagten Zustand der Pumpe 1 wirken auf die Rückseite 23 der Seitenplatte 21 innerhalb des Bereichs der Dichtung 25 durch das dort vorhandene Hydrauliköl erzeugte Druckkräfte, die zu einer Verringerung des Abstands der Seitenplatte zum Rotor führen. Die Fläche des druckbeaufschlagten Bereichs der Rückseite 23 lässt sich mittels der Dichtungen 25 begrenzen.In the pressureless state of the
Insbesondere bei Pumpen, die einen großen Innendurchmesser des Außenrings 19 aufweisen, wie dies bei verstellbaren Flügelzellenpumpen der Fall ist, kann es, wie in
Wird die Durchbiegung der Seitenplatte 21 in Richtung des Rotors zu groß, besteht die Gefahr, dass die Seitenplatte 21 den Rotor 9 während dessen Drehung um die Drehachse D berührt, woraus ein Verschleiß der Seitenplatte 21 und des Rotors 9 resultiert.If the deflection of the
Bei derartigen Pumpen 1 muss der Abstand b daher so groß sein, dass eine Berührung der Seitenplatte 21 und des Rotors 9 auch bei einer großen Verformung der Seitenplatte 21, das heißt bei maximalem Pumpendruck und maximal ausgeschwenktem Hubring, vermieden wird. Es besteht auch die Möglichkeit, die Seitenplatte 21 dicker auszubilden, sodass die Verformung unter Druckbeaufschlagung vermindert wird. Beide Lösungen haben jedoch den Nachteil, dass sich der Lagerabstand a vergrößern würde, wodurch zusätzlich eine Vergrößerung des Wellendurchmessers erforderlich wäre, um ein Durchbiegen der Welle 7 zu verhindern. Dadurch würden die axiale und radiale Baulänge sowie das Gewicht der Pumpe 1 zunehmen.In
Auch eine Reduzierung der druckbelasteten Fläche auf der Rückseite 23 entweder im radial äußeren Bereich oder im radial inneren Bereich der Seitenplatte 21 führt nicht zu einer Lösung des Problems.Also, a reduction of the pressure-loaded surface on the back 23 either in the radially outer region or in the radially inner region of the
Eine Lösung des oben beschriebenen Problems bietet das in
Die mindestens eine Seitenplatte 21 weist einen, in radialer Richtung gesehen, äußeren Randbereich 27 auf, in welchem sich die Seitenplatte 21 mit einer ersten Randfläche 29 an dem Außenring 19 abstützt. Auf der der ersten Randfläche 29 gegenüberliegenden Seite stützt sich die Seitenplatte 21 mit einer zweiten Randfläche 31 an einem Vorsprung 33 des Pumpengehäuses 3 ab. Durch den Vorsprung 33 wird der Spalt S zwischen der Seitenplatte 21 und dem Pumpengehäuse 3 ausgebildet.The at least one
Auf diese Weise ist die Seitenplatte 21 zwischen dem Vorsprung 33 des Pumpengehäuses 3 und dem Außenring 19 angeordnet. Eine axiale Verspannung der Seitenplatte 21 mit dem Pumpengehäuse 3 und dem Außenring 19 erfolgt hier rein beispielhaft durch eine in Figur 3 lediglich angedeutete Schraube 35, die den Gehäusedeckel 5, den Außenring 19, die Seitenplatte 21 und das Pumpengehäuse 3 durchgreift. Mittels der Schraube 35 wird eine axiale Kraft auf alle oben genannten Bauteile, also auch auf die Seitenplatte 21 ausgeübt, sodass diese zwischen dem Außenring 19 und dem Vorsprung 33 verspannt wird. Somit ist die Seitenplatte 21 zwischen dem Pumpengehäuse 3 und dem Außenring 19 axial, also in Richtung der Drehachse D, fixiert.In this way, the
Dadurch ist gewährleistet, dass die Seitenplatte 21 zumindest in dem äußeren Randbereich 27 im drucklosen und im druckführenden Zustand der Pumpe 1, in axialer Richtung, also in Richtung der Drehachse D der Welle 7, fest eingespannt ist. Ein in
Das Ausführungsbeispiel gemäß
Vorzugsweise weist die Seitenplatte 21' den gleichen Radius R wie die Seitenplatte 21 auf, der von der Drehachse D der Welle 7 zu der äußeren Kante c der Seitenplatten 21, 21' gemessen wird. Die äußeren Randbereiche 27, 27' der Seitenplatten 21, 21', die an dem Pumpengehäuse 3 und dem Außenring 19 beziehungsweise an dem Gehäusedeckel 5 und dem Außenring 19 anliegen, erstrecken sich über eine äußere Teilstrecke I1 der Seitenplatten 21, 21', wohingegen sich der Bereich der Seitenplatten 21, 21', der nicht an dem Außenring 19 und dem Pumpengehäuse 3, beziehungsweise an dem Gehäusedeckel 5 anliegt, über eine innere Teilstrecke I2 erstreckt. Vorzugsweise ist vorgesehen, dass das Verhältnis der Teilstrecke I1 zu I2 ≥ 0,2 beträgt, um eine optimale axiale Fixierung und eine minimale Verformung der Seitenplatten 21, 21' zu erzielen.Preferably, the side plate 21 'has the same radius R as the
Eine axiale Kraft wird auch in dem hier gezeigten Ausführungsbeispiel mittels einer hier nur angedeuteten Schraube 39 auf die Seitenplatten 21, 21' ausgeübt, die den Gehäusedeckel 5, den Außenring 19, die Seitenplatten 21 und 21' und das Pumpengehäuse 3 durchgreift und diese Elemente so miteinander fest verspannt. Somit wird auch die Seitenplatte 21' fest in der Pumpe 1 eingespannt beziehungsweise in Richtung der Drehachse D fixiert, sodass eine Verformung der Seitenplatten 21 und 21' wesentlich vermindert wird. Um ein Austreten von Hydrauliköl zwischen dem Pumpengehäuse 3 und dem Gehäusedeckel 5 zu verhindern, ist eine Dichtung 41 vorgesehen.An axial force is exerted in the embodiment shown here by means of an only indicated here screw 39 on the
Es zeigt sich noch, dass durch den vergrößerten Durchmesser der Seitenplatten 21, 21' und des Außenrings 19 und deren Verspannung beispielsweise mittels einer Schraube, welche diese Elemente durchgreift, die Wandung 43 des Pumpengehäuses 3 wesentlich dünner ausgebildet sein kann.It can also be seen that, due to the enlarged diameter of the
Anders als bei dem Ausführungsbeispiel gemäß
Das elastische Element 45 stützt sich einerseits an dem Gehäusedeckel 5 und andererseits im äußeren Randbereich 27' an der Seitenplatte 21' ab. Dadurch wird eine axiale Kraft auf die Seitenplatten 21 und 21' ausgeübt. Das elastische Element 45 unterscheidet sich von den elastischen Elementen 25 und 25' (
Die Pumpe 1 gemäß der vorliegenden Erfindung ist in den
Insgesamt zeigt sich, dass die hier vorgeschlagene Pumpe 1 mindestens eine druckkompensierte Seitenplatte 21 aufweist, die einen größeren Radius R als herkömmliche Seitenplatten aufweist. Die Pumpe 1 gemäß der Erfindung weist außerdem vorzugsweise einen Außenring 19 mit einem größeren Durchmesser auf. Die Seitenplatten 21, 21' werden in einem äußeren Randbereich 27, 27' zwischen dem Außenring 19 und dem Pumpengehäuse 3, beziehungsweise dem Gehäusedeckel 5 oder einem elastischen Element 45 beispielsweise mittels einer Schraube axial fest verspannt.Overall, it turns out that the
In den äußeren Randbereichen 27, 27', die sich über eine Teilstrecke I1 der Seitenplatten 21, 21' erstrecken, werden die Seitenplatten 21, 21' daher mit so großer axialer Kraft gegen den Außenring 19 gedrückt, dass ein Abheben der Seitenplatten 21, 21' von dem Außenring 19 in den äußeren Randbereichen 27, 27' vermieden oder zumindest stark reduziert wird.In the
Auf diese Weise wird erreicht, dass eine Verformung, beziehungsweise ein Durchbiegen der Seitenplatten 21, 21' reduziert wird, wenn diese, wie in den
Die hier vorgeschlagene Pumpe 1 kann auch bei verstellbaren Flügelzellenpumpen eingesetzt werden, die drucklos beziehungsweise mit niedrigen Drücken betrieben werden. Bei diesen Betriebszuständen besteht die Gefahr, dass die Seitenplatten 21, 21' aufgrund von Druckspitzen in den hier nicht dargestellten Arbeitskammern der Pumpe 1 vom Außenring 19 instationär abheben und dadurch beschädigt werden. Bei den hier beschriebenen Ausführungsformen der Erfindung kann die Anpresskraft der Seitenplatten 21, 21' ohne Zunahme der Verformung erhöht werden.The
Eine weitere Anwendung der Erfindung ist denkbar bei verstellbaren Flügelzellenpumpen, bei denen während des Betriebs eine "Einbettung" des Hubrings 17 in die Seitenplatte 21, 21' stattfindet, aufgrund dessen das Auslegungsspiel vergrößert werden müsste.Another application of the invention is conceivable with adjustable vane pumps in which an "embedding" of the
- 11
- Pumpepump
- 33
- Pumpengehäusepump housing
- 55
- Gehäusedeckelhousing cover
- 77
- Wellewave
- 99
- Rotorrotor
- 1111
- Radiallagerradial bearings
- 11'11 '
- Radiallagerradial bearings
- 1313
- WellendichtringShaft seal
- 13'13 '
- WellendichtringShaft seal
- 1515
- Flügelwing
- 1717
- Hubringlifting ring
- 1919
- Außenringouter ring
- 2121
- Seitenplatteside plate
- 2222
- Öffnungopening
- 2323
- Rückseiteback
- 2525
- Dichtelementsealing element
- 25'25 '
- Dichtelementsealing element
- 2626
- Anschlagattack
- 2727
- äußerer Randbereichouter edge area
- 27'27 '
- äußerer Randbereichouter edge area
- 2929
- erste Randflächefirst edge surface
- 3131
- zweite Randflächesecond edge surface
- 3333
- axialer Vorsprung (Pumpengehäuse 3)axial projection (pump housing 3)
- 3535
- Schraubescrew
- 3737
- axialer Vorsprung (Gehäusedeckel 5)axial projection (housing cover 5)
- 3939
- Schraubescrew
- 4141
- Dichtungpoetry
- 4343
- Wandungwall
- 4545
- elastisches Elementelastic element
- 4747
- Schraubescrew
- aa
- Lagerabstandbearing distance
- bb
- Abstanddistance
- b'b '
- Abstanddistance
- cc
- äußere Kanteouter edge
- DD
- Drehachseaxis of rotation
- ff
- Durchbiegungdeflection
- SS
- Spaltgap
- S'S '
- Spaltgap
- RR
- Radiusradius
- I1 I 1
- äußere Teilstreckeouter leg
- I2 I 2
- innere Teilstreckeinner leg
- KK
- Innenkante an der Stirnseite des AußenringsInner edge on the front side of the outer ring
Claims (11)
- A pump (1), in particular a sliding vane pump comprising a variable conveying volume, comprising a pump housing (3) and a cam ring (17) arranged therein, which surrounds a rotor (9), which interacts with a shaft (7), as well as comprising at least one side plate (21), which interacts with an outer ring (19), which is provided radially outside of the cam ring (17), characterized in that the at least one side plate (21), at least in an outer edge area (27), viewed in radial direction, in the unpressurized state and in the pressurized state of the pump (1), is fixedly clamped in axial direction between the pump housing (3) and the outer ring (19) and is fixed thereto such that a lifting of the side plate (21) under load is substantially avoided in the outer edge area (27), and that an edge surface (29) of the at least one side plate (21) in the outer edge area (27) rests against the outer ring (19) and an opposite edge surface (31) of the side plate (21) rests against a projection (33) of the pump housing (3).
- The pump according to claim 1, characterized in that a force is exerted in axial direction at least onto the outer edge area (27) of the at least one side plate (21).
- The pump according to claim 2, characterized in that the at least one side plate (21) is screwed to the pump housing (3) and the outer ring (19) for generating the axial force.
- The pump according to any one of the preceding claims, characterized in that provision is made for two side plates (21, 21'), which are arranged on opposite sides of the outer ring (19), viewed in axial direction.
- The pump according to claim 4, characterized in that both side plates (21, 21 ') rest against the outer ring (19) in the outer edge area (27, 27').
- The pump according to any one of the preceding claims 4 or 5, characterized in that a side plate (21) rests against the pump housing (3) in the outer edge area (27) and the other side plate (21') interacts with an elastic element (45) for generating an axial force in the outer edge area (27').
- The pump according to claim 6, characterized in that the elastic element (45) is arranged between the side plate (21) and the pump housing (3).
- The pump according to claim 6, characterized in that the elastic element (45) is arranged between the side plate (21') and a housing cover (5).
- The pump according to any one of the preceding claims 4 to 8, characterized in that a side plate (21) in the outer edge area (27) is supported on a projection (33) of the pump housing (3) and the respective other side plate (21') is supported on a projection (37) of the housing cover (5).
- The pump according to claim 9, characterized in that the two side plates (21, 21'), the housing cover (5), the outer ring (19) and the pump housing (3) are screwed to one another.
- The pump according to any one of the preceding claims, characterized in that the ratio of an outer radial segment (I1) of the side plate to an inner segment (I2) of the side plate (21, 21') is ≥ 0.2.
Applications Claiming Priority (2)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
DE102008023830 | 2008-05-08 | ||
PCT/EP2009/002831 WO2009135587A2 (en) | 2008-05-08 | 2009-04-17 | Pump |
Publications (2)
Publication Number | Publication Date |
---|---|
EP2286088A2 EP2286088A2 (en) | 2011-02-23 |
EP2286088B1 true EP2286088B1 (en) | 2011-11-23 |
Family
ID=41265067
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
EP09741806A Not-in-force EP2286088B1 (en) | 2008-05-08 | 2009-04-17 | Pump |
Country Status (4)
Country | Link |
---|---|
EP (1) | EP2286088B1 (en) |
AT (1) | ATE534822T1 (en) |
DE (1) | DE112009000601A5 (en) |
WO (1) | WO2009135587A2 (en) |
Cited By (1)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
EP3081741B1 (en) | 2015-04-17 | 2019-11-13 | Schwäbische Hüttenwerke Automotive GmbH | Pump |
Families Citing this family (1)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JP2018091265A (en) * | 2016-12-06 | 2018-06-14 | Kyb株式会社 | Variable displacement vane pump |
Family Cites Families (7)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
NL290789A (en) * | ||||
DE1788270U (en) * | 1956-09-06 | 1959-05-06 | Bosch Gmbh Robert | GEAR LIQUID PUMP. |
DE1802021A1 (en) * | 1968-10-09 | 1970-06-18 | Teves Gmbh Alfred | Rotary vane pump |
DE9201060U1 (en) * | 1992-01-29 | 1992-03-19 | Voulgaris, Andres, 8164 Hausham, De | |
DE19703114C2 (en) * | 1997-01-29 | 2002-11-21 | Danfoss As | Hydraulic vane machine |
DE19904339A1 (en) * | 1999-02-03 | 2000-08-10 | Mannesmann Rexroth Ag | Hydrostatic pump |
DE10027811A1 (en) * | 2000-06-05 | 2001-12-13 | Luk Fahrzeug Hydraulik | Cellular pump with housing and pressure plates uses distance piece between pressure plate and chamber ring surfaces plus seal round between pressure-side plate and housing. |
-
2009
- 2009-04-17 DE DE112009000601T patent/DE112009000601A5/en not_active Withdrawn
- 2009-04-17 AT AT09741806T patent/ATE534822T1/en active
- 2009-04-17 EP EP09741806A patent/EP2286088B1/en not_active Not-in-force
- 2009-04-17 WO PCT/EP2009/002831 patent/WO2009135587A2/en active Application Filing
Cited By (1)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
EP3081741B1 (en) | 2015-04-17 | 2019-11-13 | Schwäbische Hüttenwerke Automotive GmbH | Pump |
Also Published As
Publication number | Publication date |
---|---|
WO2009135587A2 (en) | 2009-11-12 |
EP2286088A2 (en) | 2011-02-23 |
DE112009000601A5 (en) | 2011-03-31 |
WO2009135587A3 (en) | 2010-03-18 |
ATE534822T1 (en) | 2011-12-15 |
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