WO2009135587A2 - Pumpe - Google Patents
Pumpe Download PDFInfo
- Publication number
- WO2009135587A2 WO2009135587A2 PCT/EP2009/002831 EP2009002831W WO2009135587A2 WO 2009135587 A2 WO2009135587 A2 WO 2009135587A2 EP 2009002831 W EP2009002831 W EP 2009002831W WO 2009135587 A2 WO2009135587 A2 WO 2009135587A2
- Authority
- WO
- WIPO (PCT)
- Prior art keywords
- side plate
- pump
- outer ring
- housing
- edge region
- Prior art date
Links
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
- 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
-
- 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
- F04C2/30—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 mentioned here are known, for example, from WO 2007/036189 A1.
- 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 Fordervolumens 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 is supported on the pump housing or 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 rear side of the side plate are larger than the side of the side plate facing the cam ring, this deforms under the load of the hydraulic oil in such a way that within the inner diameter of the outer ring, the distance between the rotor or the Hubring 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 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 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 makes a large interpretation game, ie a large distance between the side plate and the cam ring, or the rotor 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 at least in a radially outer edge region, the means in the area outside the inner diameter of the outer ring, in the unpressurized and pressurized state of the pump in the axial direction is clamped so that a lifting of the side plate under load in the outer edge region is substantially avoided.
- 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.
- 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 Direction of the axis of rotation of the shaft, the side plate at least in the outer edge region in axial Direction is firmly fixed, so that deformation of the side plate under pressure is significantly reduced.
- a pump which is characterized in that an edge surface of the at least one side plate in the outer edge region on the outer ring and an arranged on the back, so opposite edge surface of the side plate rests against a projection of the pump housing.
- the side plate in the outer edge region in the axial direction between see the outer ring and the pump housing fixed or clamped.
- An axial clamping of the side plate, the pump housing and the outer ring can be done by means of a screw connection.
- 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 which is 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.
- an axial tension can be done by means of a screw connection of the pump housing, the two side plates, the outer ring and the housing cover.
- one of the two side plates in the outer edge region on the pump housing rests and the other side plate for generating an axial force in the outer edge region with at least one elastic element, for example with a plate spring cooperates.
- 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.
- Figure 1 is a schematic sectional view of a known from the prior art pump
- Figure 2 is a schematic sectional view of the pump according to Figure 1 under load
- Figure 3 is a schematic sectional view of a first embodiment of a pressurized pump according to the invention.
- Figure 4 is a schematic sectional view of a second embodiment of a pressurized pump according to the invention.
- Figure 5 is a schematic representation of a third embodiment of a pressurized pump according to the invention.
- FIG. 1 shows a schematic sectional view of a pump 1 known from the prior art.
- the pump 1 illustrated here is, purely by way of example, a variable displacement vane pump, as described, for example, in WO 2007/036189 A1.
- Such pumps are used, in particular, for consumers with greatly varying volumetric flow requirements depending on the operating state, for example in power steering systems 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. The side plate rests on the front side 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 provided, which should also ensure that the housing cover 5 cooperates with a defined stop 26 of the pump housing 3.
- a large deformation or deflection f of the side plate 21 may occur due to the pressurization of the rear side 23.
- 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 that reference is made to the description of Figure 1.
- 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 which are exerted on the side plate 21 by the side facing the rotor 9.
- Figure 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 to a "contact line" which is defined on the Stimsei- te of the outer ring by the inner edge K.
- the distance b must therefore be so great that contact of the side plate 21 and the rotor 9 is avoided even with a large deformation of the side plate 21, that is to say at maximum pump pressure and maximum swung-out stroke 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.
- a reduction of the pressure-loaded surface on the back side 23 either in the radially outer region or in the radially inner region of the side plate 21 does not lead to a solution of the problem.
- 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, ie perpendicular to the axis of rotation D, as in the case of the pumps 1 shown in Figures 1 and 2 Figure 3 makes clear in that the side plate 21 is also supported on the outer ring 19 here.
- the at least one side plate 21 has an outer edge region 27, seen in the radial direction, in which the side plate 21 is supported by 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 takes place here purely by way of example in FIG. Gur 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 abovementioned 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.
- a shown in Figure 2 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 design clearance and on a thicker design of the side plate 21 to excessive bending to prevent.
- even thinner side plates 21 can be used, which allow a shortening of the bearing distance a and thereby a reduction of 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 of Figure 4 shows a double-sided pressure-compensated pump 1, in which therefore two side plates 21 and 21 'are provided.
- the two pressure plates 21 and 21 'are arranged in the direction of the axis of rotation D on opposite sides of the outer ring 19 and are supported on this.
- the arrangement of the side plate 21 corresponds to that shown in FIG. 3, so that reference is made to the preceding description.
- the second side plate 21 ' is also arranged by the outer ring 19 at a distance b', the so-called design play, from the rotor 9 or from the lifting 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'.
- the ratio of the sections I 1 to I 2 is ⁇ 0.2 in order to achieve optimum axial fixation and minimal deformation of the side plates 21, 21 '.
- FIG. 4 makes it clear that the side plate 21 'is arranged at a distance from the housing cover 5 by the projection 37, which is preferably formed integrally with the housing cover 5, so that a gap S' is formed between the latter and the side plate 21 'for receiving hydraulic oil is in which, for example, elastic sealing elements 25 'and / or a spring element, not shown, 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.
- Figure 5 shows a double-sided pressure compensated vane pump under load. Accordingly, according to the embodiment shown in FIG. 4, two side plates 21, 21 'are provided. The arrangement of the side plate 21 corresponds to that shown in Figures 3 and 4, so that will not be discussed here in detail.
- an elastic element 45 is provided here instead of the axial projection 37 of the housing cover 5, 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'.
- 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 region 43 of the pump housing 3 is therefore thicker 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'. As a result, an axial force is exerted on the side plates 21 and 21 '.
- the elastic member 45 differs from the elastic members 25 and 25 '(Fig. 1) in that it exerts a significantly larger force on the side plates 21 and 21'. This force is so great according to the invention that the Ab ⁇
- the pump 1 according to the present invention is shown in Figures 3 to 5 respectively under load; the side plates 21, 21 'are thus subjected to a pressure. It can be clearly seen that, unlike the conventional pump 1 shown in Figure 2 in the pressurized state, the side plates 21, 21 'not at the outer edge of the outer ring 19 stand out and the distance b, b' between the rotor 9 and the side plates 21, 21 'is indeed smaller, but excessive bending is prevented by the fixed axial clamping of the side plates 21, 21'.
- 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 the case of these operating states, there is the risk that the side plates 21, 21 ', due to pressure peaks in the working chambers (not shown here) of the pump 1, will be unsteadily lifted from the outer ring 19 and thereby 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.
Landscapes
- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Details And Applications Of Rotary Liquid Pumps (AREA)
- Rotary Pumps (AREA)
- Fluid-Driven Valves (AREA)
- Eye Examination Apparatus (AREA)
Abstract
Description
Claims
Priority Applications (3)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
AT09741806T ATE534822T1 (de) | 2008-05-08 | 2009-04-17 | Pumpe |
DE112009000601T DE112009000601A5 (de) | 2008-05-08 | 2009-04-17 | Pumpe |
EP09741806A EP2286088B1 (de) | 2008-05-08 | 2009-04-17 | Pumpe |
Applications Claiming Priority (2)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
DE102008023830.9 | 2008-05-08 | ||
DE102008023830 | 2008-05-08 |
Publications (2)
Publication Number | Publication Date |
---|---|
WO2009135587A2 true WO2009135587A2 (de) | 2009-11-12 |
WO2009135587A3 WO2009135587A3 (de) | 2010-03-18 |
Family
ID=41265067
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
PCT/EP2009/002831 WO2009135587A2 (de) | 2008-05-08 | 2009-04-17 | Pumpe |
Country Status (4)
Country | Link |
---|---|
EP (1) | EP2286088B1 (de) |
AT (1) | ATE534822T1 (de) |
DE (1) | DE112009000601A5 (de) |
WO (1) | WO2009135587A2 (de) |
Cited By (1)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
WO2018105415A1 (ja) * | 2016-12-06 | 2018-06-14 | Kyb株式会社 | 可変容量形ベーンポンプ |
Families Citing this family (1)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
DE102015105933B4 (de) | 2015-04-17 | 2018-04-26 | Schwäbische Hüttenwerke Automotive GmbH | Pumpe |
Citations (7)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
NL290789A (de) * | ||||
DE1788270U (de) * | 1956-09-06 | 1959-05-06 | Bosch Gmbh Robert | Zahnradfluessigkeitspumpe. |
DE1802021A1 (de) * | 1968-10-09 | 1970-06-18 | Teves Gmbh Alfred | Drehfluegelpumpe |
DE9201060U1 (de) * | 1992-01-29 | 1992-03-19 | Voulgaris, Andres, 8164 Hausham | Hydraulischer Motor |
DE19703114A1 (de) * | 1997-01-29 | 1998-07-30 | Danfoss As | Hydraulische Flügelzellenmaschine |
EP1026401A2 (de) * | 1999-02-03 | 2000-08-09 | Siemens Aktiengesellschaft | Hydrostatische Pumpe |
DE10027811A1 (de) * | 2000-06-05 | 2001-12-13 | Luk Fahrzeug Hydraulik | Pumpe |
-
2009
- 2009-04-17 AT AT09741806T patent/ATE534822T1/de active
- 2009-04-17 DE DE112009000601T patent/DE112009000601A5/de not_active Withdrawn
- 2009-04-17 WO PCT/EP2009/002831 patent/WO2009135587A2/de active Application Filing
- 2009-04-17 EP EP09741806A patent/EP2286088B1/de not_active Not-in-force
Patent Citations (7)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
NL290789A (de) * | ||||
DE1788270U (de) * | 1956-09-06 | 1959-05-06 | Bosch Gmbh Robert | Zahnradfluessigkeitspumpe. |
DE1802021A1 (de) * | 1968-10-09 | 1970-06-18 | Teves Gmbh Alfred | Drehfluegelpumpe |
DE9201060U1 (de) * | 1992-01-29 | 1992-03-19 | Voulgaris, Andres, 8164 Hausham | Hydraulischer Motor |
DE19703114A1 (de) * | 1997-01-29 | 1998-07-30 | Danfoss As | Hydraulische Flügelzellenmaschine |
EP1026401A2 (de) * | 1999-02-03 | 2000-08-09 | Siemens Aktiengesellschaft | Hydrostatische Pumpe |
DE10027811A1 (de) * | 2000-06-05 | 2001-12-13 | Luk Fahrzeug Hydraulik | Pumpe |
Cited By (1)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
WO2018105415A1 (ja) * | 2016-12-06 | 2018-06-14 | Kyb株式会社 | 可変容量形ベーンポンプ |
Also Published As
Publication number | Publication date |
---|---|
DE112009000601A5 (de) | 2011-03-31 |
WO2009135587A3 (de) | 2010-03-18 |
ATE534822T1 (de) | 2011-12-15 |
EP2286088A2 (de) | 2011-02-23 |
EP2286088B1 (de) | 2011-11-23 |
Similar Documents
Publication | Publication Date | Title |
---|---|---|
EP2406497B1 (de) | Hydraulische zahnradmaschine | |
EP1797320B1 (de) | RADIALKOLBENPUMPE MIT ROLLENSTÖßEL | |
DE102005041579B4 (de) | Innenzahnradpumpe mit Füllstück | |
DE102005047234A1 (de) | Rollenstößel | |
DE3319822A1 (de) | Hydraulikpumpe mit vorkompressionsventil | |
WO2012034619A1 (de) | Axialkolbenmaschine | |
WO2014131393A1 (de) | Aus wenigstens zwei teilen gebildete schraubenspindelpumpe | |
EP1283971A1 (de) | Geregelte pumpe | |
DE202011052114U1 (de) | Innenzahnradpumpe | |
WO1995002125A1 (de) | Hydraulische zahnradmaschine (pumpe oder motor), insbesondere innenzahnradmaschine | |
EP2286088B1 (de) | Pumpe | |
WO2012010262A1 (de) | Kolbeneinheit | |
EP1576290A1 (de) | Zahnradmaschine mit axialen seitenplatten | |
DE102004021216B4 (de) | Hochdruck-Innenzahnradmaschine mit mehrfacher hydrostatischer Lagerung pro Hohlrad | |
DE4124466C2 (de) | Zahnradmaschine (Pumpe oder Motor) | |
DE19810318B4 (de) | Hydraulikmaschine | |
WO2008034808A1 (de) | Radialkolbenpumpe | |
EP0302190B1 (de) | Innenzahnradmaschine | |
DE19962035B4 (de) | Schwenkmotor | |
DE3307099C2 (de) | ||
EP1798415B1 (de) | Hochdruckpumpe | |
WO2001094789A1 (de) | Pumpe | |
EP2153075A1 (de) | Lager | |
EP1461534A1 (de) | Pumpe | |
EP4136354A1 (de) | Innenzahnradmaschine |
Legal Events
Date | Code | Title | Description |
---|---|---|---|
121 | Ep: the epo has been informed by wipo that ep was designated in this application |
Ref document number: 09741806 Country of ref document: EP Kind code of ref document: A2 |
|
DPE1 | Request for preliminary examination filed after expiration of 19th month from priority date (pct application filed from 20040101) | ||
WWE | Wipo information: entry into national phase |
Ref document number: 2009741806 Country of ref document: EP |
|
WWE | Wipo information: entry into national phase |
Ref document number: 1120090006019 Country of ref document: DE |
|
REF | Corresponds to |
Ref document number: 112009000601 Country of ref document: DE Date of ref document: 20110331 Kind code of ref document: P |
|
REG | Reference to national code |
Ref country code: DE Ref legal event code: R225 Ref document number: 112009000601 Country of ref document: DE Effective date: 20110331 |