EP2313656B1 - Pump unit - Google Patents
Pump unit Download PDFInfo
- Publication number
- EP2313656B1 EP2313656B1 EP09775988.0A EP09775988A EP2313656B1 EP 2313656 B1 EP2313656 B1 EP 2313656B1 EP 09775988 A EP09775988 A EP 09775988A EP 2313656 B1 EP2313656 B1 EP 2313656B1
- Authority
- EP
- European Patent Office
- Prior art keywords
- pump unit
- sleeve
- side plate
- drive shaft
- unit according
- 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.)
- Active
Links
- 230000005540 biological transmission Effects 0.000 claims description 27
- 238000007789 sealing Methods 0.000 claims description 10
- 239000000470 constituent Substances 0.000 claims 1
- 238000006073 displacement reaction Methods 0.000 description 4
- 238000009434 installation Methods 0.000 description 3
- 238000004519 manufacturing process Methods 0.000 description 3
- 230000015572 biosynthetic process Effects 0.000 description 2
- 230000006835 compression Effects 0.000 description 2
- 238000007906 compression Methods 0.000 description 2
- 239000010720 hydraulic oil Substances 0.000 description 2
- 230000006978 adaptation Effects 0.000 description 1
- 230000000694 effects Effects 0.000 description 1
- 239000012530 fluid Substances 0.000 description 1
- 239000003921 oil Substances 0.000 description 1
- 238000005086 pumping Methods 0.000 description 1
Images
Classifications
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
- 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
- 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
- F04C15/0034—Sealing arrangements in rotary-piston machines or pumps for other than the working fluid, i.e. the sealing arrangements are not between working chambers of the machine
- F04C15/0038—Shaft sealings specially adapted for 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
- F04C14/00—Control of, monitoring of, or safety arrangements for, machines, pumps or pumping installations
- F04C14/06—Control of, monitoring of, or safety arrangements for, machines, pumps or pumping installations specially adapted for stopping, starting, idling or no-load operation
-
- 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
- F04C14/00—Control of, monitoring of, or safety arrangements for, machines, pumps or pumping installations
- F04C14/28—Safety arrangements; Monitoring
-
- 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
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
- F04C2230/00—Manufacture
- F04C2230/60—Assembly methods
-
- 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
- F04C2240/00—Components
- F04C2240/30—Casings or housings
Definitions
- the invention relates to a pump unit of a vane pump without its own housing according to the preamble of claim 1.
- Pump units of the type discussed here are known. They are used for example in gear housings of a motor vehicle or other housings which require a hydraulic supply.
- Such pumping units include a drive shaft, a rotor cooperating with the drive shaft for receiving vanes which slide along a contoured ring during rotation of the rotor, with two adjacent vanes enclosing cells which rotate as the vanes rotate Increase or reduce the contour section, sucking in and ejecting oil.
- a first and second side plate is provided, which are arranged laterally of the contour ring.
- the known Getriebepurnpenhimen have the disadvantage that they disintegrate during transport and thereby the transport in a housing or other security measures are required.
- Another disadvantage of the known pump units without their own housing is the relatively complex assembly, for example in a transmission housing.
- EP 0399387 discloses a vane pump wherein the mated contour ring and the side plates form a housing.
- Object of the present invention is therefore to provide a pump unit in which a disintegration during transport of the pump unit is avoided and also a particularly simple installation of the pump unit in a housing is possible.
- a pump unit with the features of claim 1 is proposed. It is characterized in that a sleeve mounted movably on the drive shaft is provided, which is located downstream of the second side plate in the axial direction of the pump unit. It is also characterized by the fact that a securing element for axially securing the sleeve is provided on the drive shaft, whereby a falling apart of the pump unit is avoided during transport. Furthermore, the pump unit is characterized a spring element which biases the second side plate relative to the transmission housing, wherein the spring element is an integral part of the pump unit.
- the individual elements of the pump unit are securely held together during transport and also ensure during assembly of the pump in a housing for secure installation of the second side plate on the contour ring, so start-up problems of the pump unit can be avoided.
- Another advantage of the pump unit proposed here is the particularly flexible use of the pump unit in that the spring element allows tolerance compensation for dimensional deviations.
- an embodiment of the invention which is characterized in that the securing element is a cooperating with the drive shaft snap ring.
- the securing element is a cooperating with the drive shaft snap ring.
- Another preferred embodiment of the invention is characterized in that the pump unit has a drive through. In this way, a speed query can be realized if, for example, two clutches to be controlled.
- An embodiment of the invention is also preferred, which is characterized in that the spring element is designed as a plate spring, which is supported on the one hand on the second side plate and on the other hand on the sleeve.
- the sleeve is then in turn preferably supported by a collar on the transmission housing, so that the spring element biases the second side plate relative to the housing, in particular with respect to the transmission housing.
- this embodiment when the sleeve in the axial direction movable on a Extension of the second side plate is mounted.
- the spring element in particular the plate spring is provided with openings, so that flow channels, which have the lowest possible flow resistance, are formed by the pressure outlets of the pump unit to a pressure chamber.
- the sleeve and the second side plate are integrally formed.
- an axial securing of the sleeve is preferably carried out by means of a securing element.
- the spring element is designed as a compression spring, preferably as a helical spring, in particular as a frusto-conical helical spring, which is supported on the one hand on the second side plate and on the other hand on a support means movably mounted on the sleeve.
- the support means may be arbitrary, for example, as a disc formed. It is also conceivable to introduce into the sleeve a groove in which one end of the coil spring is displaceable. It is crucial that also in this embodiment, the side plate is biased relative to the housing, so that when mounting the pump unit in a housing a secure system of the individual components is guaranteed to each other, so start-up difficulties of the pump unit can be avoided.
- a further preferred embodiment of the invention is characterized in that a first thrust bearing is realized by a cooperating with the rotor shaft collar and a second thrust bearing by a cooperating with the rotor retaining ring. In this way, when pulling or pushing the drive shaft, the rotor itself serves as a thrust bearing.
- an embodiment of the invention which is characterized in that a shaft collar is provided for the axial securing of the first pressure plate.
- a shaft collar is provided for the axial securing of the first pressure plate.
- an embodiment of the invention is preferred, which is characterized in that the radial sealing of the pump unit relative to the housing O-rings are provided, wherein the first side plate, the second side plate and the sleeve preferably cooperate with at least one O-ring.
- radial shaft seals are still provided for sealing pump parts which perform a relative rotation to each other, wherein preferably a radial shaft seal between the drive shaft and the first side plate and a second radial shaft seal between the drive shaft and the sleeve are provided.
- FIG. 1 shows a schematic sectional view of a pump unit 1 of a vane pump, which is arranged in a housing, here for example in a gear housing 3, for example. It comprises a drive shaft 5, which is non-rotatably connected to a rotor 7, for example via a toothing or the like. Furthermore, a contoured ring 9 is provided, which is arranged around the rotor 7 and which is surrounded by a first side plate 11 and a second side plate 13, which is penetrated by the drive shaft 5. The exact radial position of the side plates 11 and 13 and the contouring ring 9 to each other is ensured by pins 15 which penetrate the side plates 11 and 13 and the contour ring 9.
- the drive shaft 5 is driven by means of a drive wheel, here purely by way of example by means of a gear 17. However, it is also conceivable to use a sprocket, a belt drive or the like.
- the rotor 7 serves to receive a plurality of wings 19, which slide on a rotation of the rotor 7 about the rotation axis D of the drive shaft 5 on the inside of the contour ring 9 along.
- a suction region 21 is clearly visible, from which the vane pump sucks in hydraulic oil and conveys into a pressure space 25 via pressure outlets provided in the second pressure plate 13. From there, the hydraulic oil reaches a consumer.
- the further operation of a vane pump is sufficiently described in the prior art, so it will not be discussed further here.
- the pump unit 1 has a sleeve 27 which is arranged coaxially to the drive shaft 5 and axially displaceable on this. It is also the second side plate 13 in the axial direction, ie in the direction of the axis of rotation D, downstream of the pump unit 1, that is arranged on the opposite side of the drive side of the second side plate 13.
- a securing element 29 is provided, which is preferably designed as a snap ring and prevents slipping off of the sleeve 27 of the drive shaft 5 during transport of the pump unit 1.
- FIG. 1 makes it clear that the sleeve 27 is axially displaceably mounted on a projection 35 of the second side plate 13 with a first portion 31 in the transmission housing 3 and with a second portion 33. Between the extension 35 of the second side plate 13 and the second portion 33 of the sleeve 27, an O-ring seal 53 for radial sealing of the pump unit 1 is provided.
- the pump unit 1 also has a coaxial with the drive shaft 5 arranged spring element 39, which is supported on the one hand in a radially outer region with respect to the axis of rotation D on the second side plate 13 and on the other hand in a radially inner region of the sleeve 27.
- the spring element 39 is designed here as a plate spring and provided with openings 41 in order to ensure a fluid connection between the pressure outlets 23 and the pressure chamber 25.
- the openings 41 are preferably formed so that the flow resistance of the spring element 39 is as low as possible. It is conceivable, however, the formation of the spring element 39 as a frustoconical helical spring. Decisive is the formation of the spring element 39 as a compression spring which can bias the second side plate 13 relative to the housing.
- the shaft 5 has at its end facing away from the gear 17 on a drive 43, which is provided here purely by way of example with a pole 45 in order to realize a speed query.
- the pole wheel 45 preferably comprises permanent magnets which interact with a sensor for detecting the rotational speed of the drive shaft 5.
- a first radial shaft sealing ring 47 arranged between the first side plate 11 and the drive shaft 5 and a second radial shaft sealing ring 49 arranged between the sleeve 27 and the drive shaft 5 are provided. Since these are parts that perform a relative movement in the operation of the pump unit 1 to each other, the use of O-rings would be insufficient here. Furthermore, an O-ring seal 51 is provided for radial sealing between the first side plate 11 and the transmission housing 3. Also, the second side plate 13 is opposite the transmission housing 3 sealed by means of an O-ring seal 52 in the radial direction.
- Another O-ring seal 53 is provided in the region between the second portion 33 of the sleeve 27 and the extension 35 of the second side plate 13. Finally, for radial sealing nor an O-ring seal 55 between a portion 57 of the sleeve 27, which has a relation to the remaining sleeve 27 reduced diameter, and the transmission housing 3 is arranged.
- the drive shaft 5 is provided with a shaft collar 59, so that a drop of the first side plate 11 is prevented by the drive shaft 5.
- the pump unit 1 is formed as a compact unit, in which all elements are securely mounted on the one hand by the shaft collar 59 and on the other hand by the retaining ring 29 on the drive shaft 5 and falling apart of the pump unit 1 during transport is reliably avoided.
- the spring element 39 When transporting the pump unit 1, or in the non-installed state of the pump unit 1, the spring element 39 is more relaxed, so that the sleeve 27 is displaced on the drive shaft 5 and on the extension 35 in the axial direction and pressed against the retaining ring 29.
- the reduced-diameter portion 57 of the sleeve 27 is inserted into an opening 59 provided in the transmission case 3 until the sleeve 27 abuts against the transmission case 3 with a collar 61.
- the pump unit 1 can then be moved further into the transmission housing 3 until its optimum position is reached.
- the spring element 39 is compressed, so that the second side plate 13 is biased against the sleeve 27 and thus against the transmission housing 3 and pressed against the contour ring 9, which in turn is supported on the first side plate 11, in turn in axial Direction is secured by the housing part 48.
- FIG. 1 makes it clear that the sleeve 27 in the installed state of the pump unit 1 is no longer applied to the locking ring 29, but rather is arranged by the abutment of the collar 61 on the gear housing 3 at a distance of a few millimeters to this.
- the spring element 39 unfolds its full effect. It is also particularly advantageous on the pump unit 1 proposed here that the spring element 39 forms an integral part of the pump unit 1. It is also particularly advantageous that any manufacturing tolerances are compensated by the spring element 39, which can result in the provided for receiving the pump unit 1 bore in the transmission housing 3.
- the present pump unit 1 further comprises two thrust bearings in the event that there is a depression of the shaft in the direction of the arrow 63 or to a pulling of the drive shaft 5 in the direction of the arrow 65. Although such operating conditions should be avoided during operation of the pump unit 1, it is necessary to provide thrust bearings in the event that such an operating state occurs.
- a collar 67 is provided on the drive shaft 5 in the pump unit 1 for realizing a first thrust bearing, which is arranged on the left next to the rotor 7 is and with a displacement of the drive shaft 5 in the direction of arrow 63 engages with the rotor 7 and this entrains, so that the rotor 7 is displaced in the direction of the second side plate 13.
- a locking ring 69 arranged to the right of the rotor 7 is provided on the drive shaft 5, which entrains the rotor 7 in the direction of the arrow 65 when the drive shaft 5 moves and displaces it in the direction of the first side plate 11. It can be seen that the rotor 7 serves here as a thrust bearing which cooperates with the first side plate 11 and the second side plate 13 when the shaft is loaded axially.
- FIG. 2 shows a schematic sectional view of a second embodiment of a pump unit 1.
- the same parts are provided with the same reference numerals, so far as to the description to FIG. 1 is referenced.
- FIG. 2 In contrast to FIG. 1 is in FIG. 2 only a section of the pump unit 1 shown.
- a sleeve 27 ' is formed integrally with the second side plate 13.
- a spring element 39 ' is a coaxial with the drive shaft 5 arranged frustoconical helical spring, which is supported with one end in an outer radial region with respect to the rotation axis D on the side plate 13 and at its other end in a radially inner region of a support means 71st supported.
- FIG. 3 shows for clarity an enlarged view of the corresponding area of the pump unit 1.
- the support means 71 is movably mounted on the sleeve 27 '. It must be designed so that it can not fall off the sleeve 27 '. For this purpose, it can cooperate, for example, with a suitable securing element 72 introduced into the sleeve 27 ', which is embodied here by way of example as a securing ring.
- the support means 71 may, for example, as in FIG. 2 is shown formed as a disc which serves as an abutment for the spring element 39 '.
- the drive shaft 5 can either according to the embodiment according to FIG. 1 be provided corresponding locking ring, which prevents falling out of the sleeve 27 '. But it can also be provided a locking ring 73 which is disposed between the drive shaft 5 and the sleeve 27 'and by means of an elongated annular groove-shaped region, an axial displacement of the sleeve 27' allowed.
- the sleeve 27 ' is sealed by means of an O-ring seal 55 in the radial direction relative to the transmission housing 3.
- an O-ring seal 55 is provided in order to ensure a seal between the sleeve 27 'and the drive shaft 5, according to the first embodiment according to FIG. 1 .
- a compact pump unit 1 is provided, in which the risk of disintegration during transport by a securing element, in particular by the retaining ring 73 is avoided.
- the spring element 39 also fulfills the advantageous function that the second side plate 13 is biased relative to the transmission housing 3, so that a safe investment of the individual pump elements together and a start of the pump is ensured in a pressureless state and at the same time manufacturing tolerances are compensated.
- the sleeve 27 ' In the installed state of the pump unit 1 according to FIG. 2 the sleeve 27 'is in turn arranged in the opening 59 of the transmission housing 3. In contrast to the embodiment according to FIG. 1 However, the sleeve 27 'is not supported by a collar on the transmission housing 3, but the spring element 39' is supported on the support means 71 and thus directly on the transmission housing 3 from. As a result, the spring element 39 'exerts a force on the second side plate 13, so that the side plates 11 and 13 abut against the contour ring 9.
- a pump unit is provided by the present invention, which is characterized in that on the drive shaft movably mounted sleeve 27 or 27 'is provided, which is the second side plate 13 in the axial direction of the pump unit 1 downstream, and that a securing element 29 or 73 for axially securing the sleeve 27, 27 'on the drive shaft 5 is provided.
- the spring element 39 or 39 ' is an integral part of the pump unit 1 and biases the second side plate 13 relative to the transmission housing 3.
Landscapes
- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Details And Applications Of Rotary Liquid Pumps (AREA)
- Rotary Pumps (AREA)
Description
Die Erfindung betrifft eine Pumpeneinheit einer Flügelzellenpumpe ohne eigenes Gehäuse gemäß Oberbegriff des Anspruchs 1.The invention relates to a pump unit of a vane pump without its own housing according to the preamble of
Pumpeneinheiten der hier angesprochenen Art sind bekannt. Sie werden beispielsweise in Getriebegehäusen eines Kraftfahrzeugs oder anderen Gehäusen, welche eine Hydraulikversorgung benötigen, eingesetzt. Derartige Pumpeneinheiten weisen eine Antriebswelle auf, einen mit der Antriebswelle zusammenwirkenden Rotor, der zur Aufnahme von Flügeln dient, die während einer Drehung des Rotors an einem Konturring entlang gleiten, wobei zwei benachbarte Flügel Zellen einschließen, welche sich bei einer Rotation der Flügel, je nach Konturabschnitt vergrößern oder verkleinern, und dabei Öl ansaugen und wieder ausstoßen. Des Weiteren ist eine erste und zweite Seitenplatte vorgesehen, die seitlich des Konturrings angeordnet sind. Die bekannten Getriebepurnpeneinheiten weisen den Nachteil auf, dass diese beim Transport zerfallen und dadurch der Transport in einem Gehäuse oder andere Sicherheitsmaßnahmen erforderlich sind. Ein weiterer Nachteil der bekannten Pumpeneinheiten ohne eigenes Gehäuse ist die relativ aufwändige Montage beispielsweise in einem Getriebegehäuse.Pump units of the type discussed here are known. They are used for example in gear housings of a motor vehicle or other housings which require a hydraulic supply. Such pumping units include a drive shaft, a rotor cooperating with the drive shaft for receiving vanes which slide along a contoured ring during rotation of the rotor, with two adjacent vanes enclosing cells which rotate as the vanes rotate Increase or reduce the contour section, sucking in and ejecting oil. Furthermore, a first and second side plate is provided, which are arranged laterally of the contour ring. The known Getriebepurnpeneinheiten have the disadvantage that they disintegrate during transport and thereby the transport in a housing or other security measures are required. Another disadvantage of the known pump units without their own housing is the relatively complex assembly, for example in a transmission housing.
Dokument
Aufgabe der vorliegenden Erfindung ist es daher, eine Pumpeneinheit zu schaffen, bei der ein Zerfall beim Transport der Pumpeneinheit vermieden wird und außerdem ein besonders einfacher Einbau der Pumpeneinheit in einem Gehäuse möglich ist.Object of the present invention is therefore to provide a pump unit in which a disintegration during transport of the pump unit is avoided and also a particularly simple installation of the pump unit in a housing is possible.
Zur Lösung dieser Aufgabe wird eine Pumpeneinheit mit den Merkmalen des Anspruchs 1 vorgeschlagen. Sie zeichnet sich dadurch aus, dass eine auf der Antriebswelle beweglich gelagerte Hülse vorgesehen ist, die der zweiten Seitenplatte in axialer Richtung der Pumpeneinheit nachgelagert ist. Sie zeichnet sich außerdem dadurch aus, dass ein Sicherungselement zur axialen Sicherung der Hülse auf der Antriebswelle vorgesehen ist, wodurch ein Auseinanderfallen der Pumpeneinheit beim Transport vermieden wird. Des Weiteren zeichnet sich die Pumpeneinheit durch ein Federelement aus, welches die zweite Seitenplatte gegenüber dem Getriebegehäuse vorspannt, wobei das Federelement ein fester Bestandteil der Pumpeneinheit ist. Dadurch werden die einzelnen Elemente der Pumpeneinheit auch beim Transport sicher zusammengehalten und sorgen außerdem bei der Montage der Pumpe in einem Gehäuse für eine sichere Anlage der zweiten Seitenplatte an dem Konturring, sodass Anlaufprobleme der Pumpeneinheit vermieden werden. Ein weiterer Vorteil der hier vorgeschlagenen Pumpeneinheit ist der besonders flexible Einsatz der Pumpeneinheit dadurch, dass das Federelement einen Toleranzausgleich bei Maßabweichungen ermöglicht.To solve this problem, a pump unit with the features of
Besonders bevorzugt wird ein Ausführungsbeispiel der Erfindung, das sich dadurch auszeichnet, dass das Sicherungselement ein mit der Antriebswelle zusammenwirkender Sprengring ist. Auf diese Weise erfolgt eine zuverlässige axiale Sicherung der Hülse auf der Antriebswelle, sodass die einzelnen Bauteile der Pumpeneinheit beim Transport nicht von der Antriebswelle rutschen können. Somit kann auf ein Pumpengehäuse für den Transport der Pumpeneinheit verzichtet werden. Die Pumpeneinheit kann also als kompakte Einheit ohne irgendwelche zusätzlichen Sicherungsmaßnahmen transportiert werden.Particularly preferred is an embodiment of the invention, which is characterized in that the securing element is a cooperating with the drive shaft snap ring. In this way, a reliable axial securing of the sleeve takes place on the drive shaft, so that the individual components of the pump unit can not slip from the drive shaft during transport. Thus can be dispensed with a pump housing for the transport of the pump unit. The pump unit can thus be transported as a compact unit without any additional security measures.
Ein weiteres bevorzugtes Ausführungsbeispiel der Erfindung zeichnet sich dadurch aus, dass die Pumpeneinheit einen Durchtrieb aufweist. Auf diese Weise kann eine Drehzahlabfrage realisiert werden, wenn beispielsweise zwei Kupplungen geregelt werden sollen.Another preferred embodiment of the invention is characterized in that the pump unit has a drive through. In this way, a speed query can be realized if, for example, two clutches to be controlled.
Auch wird ein Ausführungsbeispiel der Erfindung bevorzugt, das sich dadurch auszeichnet, dass das Federelement als Tellerfeder ausgebildet ist, die sich einerseits an der zweiten Seitenplatte und andererseits an der Hülse abstützt. Die Hülse stützt sich dann wiederum vorzugsweise über einen Bund an dem Getriebegehäuse ab, sodass das Federelement die zweite Seitenplatte gegenüber dem Gehäuse, insbesondere gegenüber dem Getriebegehäuse, vorspannt. Besonders vorteilhaft ist dieses Ausführungsbeispiel, wenn die Hülse in axialer Richtung beweglich auf einem Fortsatz der zweiten Seitenplatte gelagert ist. Beim Einbau der Pumpe kann auf diese Weise eine sichere Anlage der Pumpenteile gewährleistet werden.An embodiment of the invention is also preferred, which is characterized in that the spring element is designed as a plate spring, which is supported on the one hand on the second side plate and on the other hand on the sleeve. The sleeve is then in turn preferably supported by a collar on the transmission housing, so that the spring element biases the second side plate relative to the housing, in particular with respect to the transmission housing. Particularly advantageous is this embodiment, when the sleeve in the axial direction movable on a Extension of the second side plate is mounted. When installing the pump can be guaranteed in this way a safe investment of the pump parts.
Bei einem weiteren bevorzugten Ausführungsbeispiel der Erfindung ist vorgesehen, dass das Federelement, insbesondere die Tellerfeder mit Öffnungen versehen ist, sodass Durchflusskanäle, die einen möglichst geringen Strömungswiderstand aufweisen, von den Druckauslässen der Pumpeneinheit zu einem Druckraum gebildet werden.In a further preferred embodiment of the invention it is provided that the spring element, in particular the plate spring is provided with openings, so that flow channels, which have the lowest possible flow resistance, are formed by the pressure outlets of the pump unit to a pressure chamber.
Bei einem weiteren bevorzugten Ausführungsbeispiel der Erfindung ist vorgesehen, dass die Hülse und die zweite Seitenplatte einstückig ausgebildet sind. Auch bei diesem Ausführungsbeispiel erfolgt eine axiale Sicherung der Hülse vorzugsweise mittels eines Sicherungselements. Das Federelement ist als Druckfeder, vorzugsweise als Schraubenfeder, insbesondere als kegelstumpfförmige Schraubenfeder ausgebildet, die sich einerseits an der zweiten Seitenplatte und andererseits an einer beweglich auf der Hülse gelagerten Stützeinrichtung abstützt. Die Stützeinrichtung kann beliebig, beispielsweise als Scheibe, ausgebildet sein. Denkbar ist es auch, in die Hülse eine Nut einzubringen, in welcher ein Ende der Schraubenfeder verlagerbar ist. Entscheidend ist, dass auch bei dieser Ausführungsform die Seitenplatte gegenüber dem Gehäuse vorgespannt wird, sodass bei der Montage der Pumpeneinheit in einem Gehäuse eine sichere Anlage der einzelnen Bauelemente zueinander gewährleistet ist, sodass Anlaufschwierigkeiten der Pumpeneinheit vermieden werden.In a further preferred embodiment of the invention it is provided that the sleeve and the second side plate are integrally formed. Also in this embodiment, an axial securing of the sleeve is preferably carried out by means of a securing element. The spring element is designed as a compression spring, preferably as a helical spring, in particular as a frusto-conical helical spring, which is supported on the one hand on the second side plate and on the other hand on a support means movably mounted on the sleeve. The support means may be arbitrary, for example, as a disc formed. It is also conceivable to introduce into the sleeve a groove in which one end of the coil spring is displaceable. It is crucial that also in this embodiment, the side plate is biased relative to the housing, so that when mounting the pump unit in a housing a secure system of the individual components is guaranteed to each other, so start-up difficulties of the pump unit can be avoided.
Ein weiteres bevorzugtes Ausführungsbeispiel der Erfindung zeichnet sich dadurch aus, dass ein erstes Axiallager durch einen mit dem Rotor zusammenwirkenden Wellenbund und ein zweites Axiallager durch einen mit dem Rotor zusammenwirkenden Sicherungsring realisiert wird. Auf diese Weise dient bei einem Ziehen oder einem Drücken der Antriebswelle der Rotor selbst als Axiallager.A further preferred embodiment of the invention is characterized in that a first thrust bearing is realized by a cooperating with the rotor shaft collar and a second thrust bearing by a cooperating with the rotor retaining ring. In this way, when pulling or pushing the drive shaft, the rotor itself serves as a thrust bearing.
Weiterhin bevorzugt wird ein Ausführungsbeispiel der Erfindung, das sich dadurch auszeichnet, dass zur axialen Sicherung der ersten Druckplatte ein Wellenbund vorgesehen ist. Auf diese Weise sind sämtliche Elemente der Pumpeneinheit sicher auf der Antriebswelle gelagert und können von dieser nicht herunterfallen. Somit kann ein sicherer Transport der Pumpeneinheit ohne zusätzliche Sicherungsmaßnahmen erfolgen.Further preferred is an embodiment of the invention, which is characterized in that a shaft collar is provided for the axial securing of the first pressure plate. In this way, all elements of the pump unit are safe stored the drive shaft and can not fall from this. Thus, a safe transport of the pump unit can be done without additional security measures.
Schließlich wird ein Ausführungsbeispiel der Erfindung bevorzugt, das sich dadurch auszeichnet, dass zur radialen Abdichtung der Pumpeneinheit gegenüber dem Gehäuse O-Ringe vorgesehen sind, wobei die erste Seitenplatte, die zweite Seitenplatte und die Hülse vorzugsweise mit mindestens einem O-Ring zusammenwirken. Insbesondere sind zur Abdichtung von Pumpenteilen, die eine Relativdrehung zueinander durchführen, noch Radialwellendichtringe vorgesehen, wobei vorzugsweise ein Radialwellendichtring zwischen der Antriebswelle und der ersten Seitenplatte und ein zweiter Radialwellendichtring zwischen der Antriebswelle und der Hülse vorgesehen sind.Finally, an embodiment of the invention is preferred, which is characterized in that the radial sealing of the pump unit relative to the housing O-rings are provided, wherein the first side plate, the second side plate and the sleeve preferably cooperate with at least one O-ring. In particular, radial shaft seals are still provided for sealing pump parts which perform a relative rotation to each other, wherein preferably a radial shaft seal between the drive shaft and the first side plate and a second radial shaft seal between the drive shaft and the sleeve are provided.
Die Erfindung wird im Folgenden anhand der Zeichnung näher erläutert. Es zeigen:
-
eine schematische Schnittdarstellung eines ersten Ausführungsbeispiels der Pumpeneinheit;Figur 1 -
Figur 2 eine schematische Schnittdarstellung eines zweiten Ausführungsbeispiels der Pumpeneinheit, und -
eine vergrößerte Darstellung eines Ausschnitts der Pumpeneinheit gemäßFigur 3Figur 2 .
-
FIG. 1 a schematic sectional view of a first embodiment of the pump unit; -
FIG. 2 a schematic sectional view of a second embodiment of the pump unit, and -
FIG. 3 an enlarged view of a section of the pump unit according toFIG. 2 ,
Die Antriebswelle 5 wird mittels eines Antriebsrads, hier rein beispielhaft mittels eines Zahnrads 17, angetrieben. Denkbar ist jedoch auch der Einsatz eines Kettenrads, eines Riementriebs oder dergleichen.The
Der Rotor 7 dient zur Aufnahme mehrerer Flügel 19, die bei einer Drehung des Rotors 7 um die Drehachse D der Antriebswelle 5 an der Innenseite des Konturrings 9 entlang gleiten. In
Die Pumpeneinheit 1 weist eine Hülse 27 auf, die koaxial zu der Antriebswelle 5 und axial auf dieser verlagerbar angeordnet ist. Sie ist darüber hinaus der zweiten Seitenplatte 13 in axialer Richtung, also in Richtung der Drehachse D, der Pumpeneinheit 1 nachgelagert, also auf der der Antriebsseite gegenüberliegenden Seite der zweiten Seitenplatte 13 angeordnet. Zur axialen Sicherung der Hülse 27 auf der Antriebswelle 5 ist ein Sicherungselement 29 vorgesehen, welches vorzugsweise als Sprengring ausgebildet ist und das ein Herunterrutschen der Hülse 27 von der Antriebswelle 5 während des Transports der Pumpeneinheit 1 verhindert.The
Die Pumpeneinheit 1 weist außerdem ein koaxial zur Antriebswelle 5 angeordnetes Federelement 39 auf, welches sich einerseits in einem radial außen liegenden Bereich bezüglich der Drehachse D an der zweiten Seitenplatte 13 und mit andererseits in einem radial innen liegenden Bereich an der Hülse 27 abstützt. Das Federelement 39 ist hier als Tellerfeder ausgebildet und mit Öffnungen 41 versehen, um eine Fluidverbindung zwischen den Druckauslässen 23 und dem Druckraum 25 zu gewährleisten. Die Öffnungen 41 sind vorzugsweise so ausgebildet, dass der Strömungswiderstand des Federelements 39 möglichst gering ist. Denkbar ist jedoch die Ausbildung des Federelements 39 als kegelstumpfförmige Schraubenfeder. Entscheidend ist die Ausbildung des Federelements 39 als Druckfeder, welche die zweite Seitenplatte 13 gegenüber dem Gehäuse vorspannen kann.The
Die Welle 5 weist an ihrem dem Zahnrad 17 abgewandten Ende einen Durchtrieb 43 auf, der hier rein beispielhaft mit einem Polrad 45 versehen ist, um eine Drehzahlabfrage zu realisieren. Das Polrad 45 umfasst hierzu vorzugsweise Permanentmagneten, die mit einem Sensor zur Erfassung der Drehzahl der Antriebswelle 5 zusammenwirken.The
Eine axiale Sicherung der Pumpeneinheit 1 in dem Getriebegehäuse 3 erfolgt in dem Ausführungsbeispiel gemäß
Zur radialen Abdichtung der Pumpeneinheit 1 gegenüber dem Getriebegehäuse 3 ist ein zwischen der ersten Seitenplatte 11 und der Antriebswelle 5 angeordneter erster Radialwellendichtring 47 und ein zwischen der Hülse 27 und der Antriebswelle 5 angeordneter zweiter Radialwellendichtring 49 vorgesehen. Da es sich dabei um Teile handelt, die eine Relativbewegung im Betrieb der Pumpeneinheit 1 zueinander ausführen, wäre der Einsatz von O-Ringen hier ungenügend. Des Weiteren ist zur radialen Abdichtung zwischen der ersten Seitenplatte 11 und dem Getriebegehäuse 3 eine O-Ring-Dichtung 51 vorgesehen. Auch die zweite Seitenplatte 13 ist gegenüber dem Getriebegehäuse 3 mittels einer O-Ring-Dichtung 52 in radialer Richtung abgedichtet.For radial sealing of the
Eine weitere O-Ring-Dichtung 53 ist im Bereich zwischen dem zweiten Abschnitt 33 der Hülse 27 und dem Fortsatz 35 der zweiten Seitenplatte 13 vorgesehen. Schließlich ist zur radialen Abdichtung noch eine O-Ring-Dichtung 55 zwischen einem Abschnitt 57 der Hülse 27, der einen gegenüber der restlichen Hülse 27 reduzierten Durchmesser aufweist, und dem Getriebegehäuse 3 angeordnet.Another O-
Zur axialen Sicherung der ersten Seitenplatte 11 ist die Antriebswelle 5 mit einem Wellenbund 59 versehen, sodass ein Herunterfallen der ersten Seitenplatte 11 von der Antriebswelle 5 verhindert wird.For axially securing the first side plate 11, the
Insgesamt zeigt sich, dass die Pumpeneinheit 1 als kompakte Einheit ausgebildet ist, bei der sämtliche Elemente einerseits durch den Wellenbund 59 und andererseits durch den Sicherungsring 29 sicher auf der Antriebswelle 5 gelagert sind und ein Auseinanderfallen der Pumpeneinheit 1 beim Transport zuverlässig vermieden wird.Overall, it is shown that the
Beim Transport der Pumpeneinheit 1, beziehungsweise im nicht eingebauten Zustand der Pumpeneinheit 1, ist das Federelement 39 entspannter, sodass die Hülse 27 auf der Antriebswelle 5 und auf dem Fortsatz 35 in axialer Richtung verlagert und gegen den Sicherungsring 29 gepresst wird.When transporting the
Wenn die Getriebeeinheit 1 in das Getriebegehäuse 3 eingesetzt wird, wird der im Durchmesser reduzierte Abschnitt 57 der Hülse 27 in eine in dem Getriebegehäuse 3 vorgesehene Öffnung 59 eingeführt, bis die Hülse 27 mit einem Bund 61 an dem Getriebegehäuse 3 anliegt. Die Pumpeneinheit 1 kann dann weiter in das Getriebegehäuse 3 hineinverlagert werden, bis ihre optimale Position erreicht ist. In diesem eingebauten Zustand der Pumpeneinheit 1 wird das Federelement 39 zusammengedrückt, sodass die zweite Seitenplatte 13 gegenüber der Hülse 27 und damit gegenüber dem Getriebegehäuse 3 vorgespannt wird und gegen den Konturring 9 gepresst wird, der sich wiederum an der ersten Seitenplatte 11 abstützt, die ihrerseits in axialer Richtung durch das Gehäuseteil 48 gesichert ist. Durch die Federkraft des Federelements 39 wird damit bereits im drucklosen Zustand der Pumpeneinheit 1 eine sichere Anlage und Abdichtung der beiden Seitenplatten an dem Konturring 9 und damit ein Druckaufbau und ein reibungsloses Anlaufen der Pumpeneinheit 1 sichergestellt. Auch beim Transport der Pumpeneinheit 1 werden die Pumpenteile somit sicher zusammengehalten.When the
Besonders vorteilhaft ist die Ausgestaltung der hier vorgeschlagenen Pumpeneinheit 1, wenn ein Durchtrieb 43, beispielsweise zur Realisierung einer Drehzahlabfrage, vorgesehen ist.Particularly advantageous is the embodiment of the
Die vorliegende Pumpeneinheit 1 umfasst weiterhin zwei Axiallager für den Fall, dass es zu einem Drücken der Welle in Richtung des Pfeils 63 oder zu einem Ziehen der Antriebswelle 5 in Richtung des Pfeils 65 kommt. Derartige Betriebszustände sollten beim Betrieb der Pumpeneinheit 1 zwar vermieden werden, jedoch ist es notwendig, Axiallager vorzusehen, für den Fall, dass ein derartiger Betriebszustand eintritt.The
Hierzu ist bei der Pumpeneinheit 1 zur Realisierung eines ersten Axiallagers ein Bund 67 an der Antriebswelle 5 vorgesehen, der links neben dem Rotor 7 angeordnet ist und der bei einer Verlagerung der Antriebswelle 5 in Richtung des Pfeils 63 mit dem Rotor 7 in Eingriff kommt und diesen mitnimmt, sodass der Rotor 7 in Richtung der zweiten Seitenplatte 13 verlagert wird. Zur Realisierung eines zweiten Axiallagers ist ein rechts neben dem Rotor 7 angeordneter Sicherungsring 69 an der Antriebswelle 5 vorgesehen, der bei einer Bewegung der Antriebswelle 5 in Richtung des Pfeils 65 den Rotor 7 mitnimmt und diesen in Richtung der ersten Seitenplatte 11 verlagert. Es zeigt sich, dass der Rotor 7 hier als Axiallager dient, der bei einer axialen Belastung der Welle mit der ersten Seitenplatte 11 beziehungsweise mit der zweiten Seitenplatte 13 zusammenwirkt.For this purpose, a
Im Gegensatz zu
Die Stützeinrichtung 71 kann beispielsweise, wie in
Zur axialen Sicherung der Hülse 27' auf der Antriebswelle 5 kann entweder ein dem Ausführungsbeispiel gemäß
Auch bei diesem Ausführungsbeispiel ist die Hülse 27' mittels einer O-Ring-Dichtung 55 in radialer Richtung gegenüber dem Getriebegehäuse 3 abgedichtet. Um eine Abdichtung zwischen der Hülse 27' und der Antriebswelle 5 zu gewährleisten, ist entsprechend dem ersten Ausführungsbeispiel gemäß
Es wird deutlich, dass auch bei dem zweiten Ausführungsbeispiel eine kompakte Pumpeneinheit 1 geschaffen wird, bei der die Gefahr eines Zerfallens während des Transports durch ein Sicherungselement, insbesondere durch den Sicherungsring 73 vermieden wird. Des Weiteren erfüllt das Federelement 39 auch hier die vorteilhafte Funktion, dass die zweite Seitenplatte 13 gegenüber dem Getriebegehäuse 3 vorgespannt wird, sodass eine sichere Anlage der einzelnen Pumpenelemente aneinander erfolgt und ein Anlaufen der Pumpe in drucklosem Zustand sichergestellt ist und gleichzeitig Fertigungstoleranzen ausgeglichen werden.It is clear that even in the second embodiment, a
Im eingebauten Zustand der Pumpeneinheit 1 gemäß
Durch die bewegliche Anordnung des Abstützelements 71 auf der Hülse 27', wird dieses durch das Federelement 39' immer gegen das Getriebegehäuse 3 gedrückt.Due to the movable arrangement of the
Insgesamt zeigt sich, dass durch die vorliegende Erfindung eine Pumpeneinheit geschaffen wird, die sich dadurch auszeichnet, dass eine auf der Antriebswelle beweglich gelagerte Hülse 27 beziehungsweise 27' vorgesehen ist, die der zweiten Seitenplatte 13 in axialer Richtung der Pumpeneinheit 1 nachgelagert ist, und dass ein Sicherungselement 29 beziehungsweise 73 zur axialen Sicherung der Hülse 27, 27' auf der Antriebswelle 5 vorgesehen ist. Auf diese Weise kann ein Transport der Pumpeneinheit 1 ohne zusätzliche Sicherungsmaßnahmen erfolgen, da ein Zerfallen der Pumpeneinheit 1 vermieden wird. Das Federelement 39 beziehungsweise 39' ist ein fester Bestandteil der Pumpeneinheit 1 und spannt die zweite Seitenplatte 13 gegenüber dem Getriebegehäuse 3 vor. Dadurch wird ein Klaffen der Pumpenelemente im drucklosen Zustand der Pumpeneinheit 1 vermieden, und sie kann problemlos durch die Abdichtung Druck aufbauen und anlaufen. Außerdem werden durch das Federelement 39, 39' fertigungsbedingte Toleranzen ausgeglichen, die eine optimale Anpassung der Pumpeneinheit 1 erlauben, wodurch diese besonders flexibel einsetzbar ist.
Claims (12)
- Pump unit (1) of a vane cell pump without a dedicated housing, having
a drive shaft (5),
a rotor (7) for receiving vanes (19), which rotor (7) interacts with the drive shaft (5),
a contour ring (9) which surrounds the rotor (7),
a first and a second side plate (11, 13) which are arranged on the sides of the contour ring (9),
characterized in that
a sleeve (27, 27') is provided which is mounted movably on the drive shaft (5) and is arranged behind the second side plate (13) in the axial direction of the pump unit (1), in that a securing element (29, 73) is provided in the form of a circlip for axially securing the sleeve (27) on the drive shaft (5), and in that a spring element (39, 39') is provided which prestresses the second side plate (13) with respect to the transmission housing (3), the spring element (39, 39') being a fixed constituent part of the pump unit (1). - Pump unit according to Claim 1, characterized in that the pump unit (1) has a through-connected drive (43).
- Pump unit according to either of the preceding claims, characterized in that the spring element (39) is configured as a disc spring which is supported on one side on the second side plate (13) and on the other side on the sleeve (27).
- Pump unit according to Claim 3, characterized in that the spring element (39) is provided with openings (41).
- Pump unit according to one of the preceding claims, characterized in that the sleeve (27) is supported via a collar (61) on the transmission housing (3).
- Pump unit (1) according to one of the preceding claims characterized in that the sleeve (27) is mounted movably in the axial direction on a projection of the second side plate (13).
- Pump unit according to either of Claims 1 and 2, characterized in that the sleeve (27') and the second side plate (13) are configured in one piece.
- Pump unit according to Claim 7, characterized in that the spring element (39') is configured as a frustoconical helical spring which is supported on one side on the second side plate (13) and on the other side on a supporting device (71) which is mounted movably on the sleeve (27').
- Pump unit according to one of the preceding claims, characterized in that a first axial bearing is realized by way of a shaft collar (67) which interacts with the rotor (7) and a second axial bearing is realized by way of a securing ring (69) which interacts with the rotor (7).
- Pump unit according to one of the preceding claims, characterized in that a shaft collar (67) is provided for axial securing of the first pressure plate (11).
- Pump unit according to one of the preceding claims, characterized in that O-rings (52, 51, 53, 55) are provided for radial sealing of the pump unit (1), which O-rings (52, 51, 53, 55) interact with the first side plate (11), the second side plate (13) and with the sleeve (27, 27').
- Pump unit according to one of the preceding claims, characterized in that, in order to radially seal the pump unit (1), a first radial shaft seal (47) is provided between the drive shaft (5) and the first side plate (11) and a second radial shaft seal (49) is provided between the drive shaft (5) and the sleeve (27).
Applications Claiming Priority (2)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
DE102008038718 | 2008-08-12 | ||
PCT/DE2009/001012 WO2010017795A2 (en) | 2008-08-12 | 2009-07-20 | Pump unit |
Publications (2)
Publication Number | Publication Date |
---|---|
EP2313656A2 EP2313656A2 (en) | 2011-04-27 |
EP2313656B1 true EP2313656B1 (en) | 2016-02-17 |
Family
ID=41669378
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
EP09775988.0A Active EP2313656B1 (en) | 2008-08-12 | 2009-07-20 | Pump unit |
Country Status (6)
Country | Link |
---|---|
US (1) | US8932037B2 (en) |
EP (1) | EP2313656B1 (en) |
JP (1) | JP5734186B2 (en) |
CN (1) | CN102089522B (en) |
DE (1) | DE112009001697A5 (en) |
WO (1) | WO2010017795A2 (en) |
Families Citing this family (8)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
DE102012103888A1 (en) * | 2012-05-03 | 2013-11-21 | Zf Lenksysteme Gmbh | Displacement pump for conveying of pressurizing agent to consumer, particularly vane-type or roller pump for transmission of motor vehicle, has pump packet with rotor, cam ring and multiple working slides |
DE102013209877A1 (en) * | 2013-05-28 | 2014-12-04 | Mahle International Gmbh | Reciprocating vacuum pump |
DE102014212022B4 (en) * | 2013-07-08 | 2016-06-09 | Magna Powertrain Bad Homburg GmbH | pump |
US9617994B2 (en) | 2014-04-18 | 2017-04-11 | Delaware Capital Formation, Inc. | Pump with mechanical seal assembly |
DE102016204099B3 (en) * | 2016-03-11 | 2017-03-16 | Magna Powertrain Bad Homburg GmbH | Seal arrangement for switchable vane pump in cartridge design |
RU2659639C1 (en) * | 2017-05-24 | 2018-07-03 | федеральное государственное бюджетное образовательное учреждение высшего образования "Алтайский государственный технический университет им. И.И. Ползунова" (АлтГТУ) | Rotary piston internal combustion engine |
RU2666716C1 (en) * | 2017-08-03 | 2018-09-11 | федеральное государственное бюджетное образовательное учреждение высшего образования "Алтайский государственный технический университет им. И.И. Ползунова" (АлтГТУ) | Rotary piston internal combustion engine |
RU2707343C1 (en) * | 2019-05-22 | 2019-11-26 | Николай Михайлович Кривко | Six-stroke rotary-blade internal combustion engine |
Family Cites Families (19)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US2558837A (en) * | 1944-04-13 | 1951-07-03 | Bendix Aviat Corp | Pump |
US2680031A (en) * | 1951-02-03 | 1954-06-01 | Lear Inc | Shaft sealing structure |
US3104530A (en) * | 1961-10-19 | 1963-09-24 | Gen Motors Corp | Accessory drive mechanism |
US3560118A (en) * | 1969-06-11 | 1971-02-02 | Derso W Palachik | Rotary motor or pump |
USRE26856E (en) * | 1969-07-23 | 1970-04-14 | Fluid energy translating device | |
JPS6126638Y2 (en) * | 1980-12-27 | 1986-08-09 | ||
US4424014A (en) * | 1981-06-08 | 1984-01-03 | General Motors Corporation | Power steering pump drive shaft seal area drain structure |
US4419058A (en) * | 1981-06-08 | 1983-12-06 | General Motors Corporation | Hydraulic pump rotating group axial alignment structure |
US4415319A (en) * | 1981-08-11 | 1983-11-15 | Jidosha Kiki Co., Ltd. | Pump unit |
EP0399387B1 (en) * | 1989-05-24 | 1992-09-30 | Vickers Incorporated | Rotary vane machine |
US5290155A (en) * | 1991-09-03 | 1994-03-01 | Deco-Grand, Inc. | Power steering pump with balanced porting |
FR2723155B1 (en) * | 1994-07-26 | 1996-10-11 | Nacam | DEVICE FOR COUPLING TWO SHAFTS |
JPH0842464A (en) | 1994-07-29 | 1996-02-13 | Nippon Seiko Kk | Hydraulic pump |
DE19802443C1 (en) * | 1998-01-23 | 1999-05-12 | Luk Fahrzeug Hydraulik | Pump with housing in which is pump unit |
DE19952605A1 (en) * | 1999-11-02 | 2001-05-10 | Luk Fahrzeug Hydraulik | Pump for a liquid or gaseous medium |
CN1182330C (en) * | 2000-02-14 | 2004-12-29 | 伊宝成 | Oil delivering pump |
JP2002130151A (en) * | 2000-10-30 | 2002-05-09 | Unisia Jecs Corp | Vane pump |
US6655936B2 (en) * | 2001-11-14 | 2003-12-02 | Delphi Technologies, Inc. | Rotary vane pump with under-vane pump |
CN1273740C (en) * | 2002-11-19 | 2006-09-06 | 史学忠 | Power steering oil pump for automobile |
-
2009
- 2009-07-20 DE DE112009001697T patent/DE112009001697A5/en not_active Withdrawn
- 2009-07-20 EP EP09775988.0A patent/EP2313656B1/en active Active
- 2009-07-20 CN CN200980127120.5A patent/CN102089522B/en active Active
- 2009-07-20 WO PCT/DE2009/001012 patent/WO2010017795A2/en active Application Filing
- 2009-07-20 US US13/058,514 patent/US8932037B2/en active Active
- 2009-07-20 JP JP2011522379A patent/JP5734186B2/en active Active
Also Published As
Publication number | Publication date |
---|---|
WO2010017795A2 (en) | 2010-02-18 |
US20110211984A1 (en) | 2011-09-01 |
DE112009001697A5 (en) | 2011-04-07 |
WO2010017795A3 (en) | 2010-07-15 |
US8932037B2 (en) | 2015-01-13 |
JP5734186B2 (en) | 2015-06-17 |
JP2011530668A (en) | 2011-12-22 |
CN102089522A (en) | 2011-06-08 |
EP2313656A2 (en) | 2011-04-27 |
CN102089522B (en) | 2014-04-23 |
Similar Documents
Publication | Publication Date | Title |
---|---|---|
EP2313656B1 (en) | Pump unit | |
EP2098743B1 (en) | Adjustment mechanism for inserting and extracting a separation coupling with rotating curve segment | |
EP2715188B1 (en) | spindle drive | |
EP1752691A1 (en) | Control spool valve and its manufacturing process | |
WO2015176866A1 (en) | Steering gear | |
EP2345569B1 (en) | Screw gearing for the steering of a motor vehicle | |
EP1924802A1 (en) | Hydraulic coupling with a bayonet closure and a wire-form spring for rotational locking | |
WO2018224248A1 (en) | Floating bearing, steering gear, and steering system | |
WO2018077778A1 (en) | Rotary piston pump having a sealing chamber seal | |
EP1859170A1 (en) | Rotary piston machine | |
DE102019208345B4 (en) | differential lock | |
EP3916277B1 (en) | Separate valve seat | |
DE8911619U1 (en) | Electronically adjustable self-locking differential | |
DE102013113362B4 (en) | Adjustable pump for an internal combustion engine | |
DE102008064456B4 (en) | power steering device | |
DE102013216410A1 (en) | locking device | |
DE102007041342A1 (en) | driving means | |
DE1653905A1 (en) | Displacement pump | |
WO2021089212A1 (en) | Piston actuating device | |
DE102017206240B3 (en) | Screw compressor assembly | |
DE4417959C2 (en) | Device for changing the timing of an internal combustion engine | |
DE102014222590B4 (en) | Camshaft adjuster with control sleeve | |
DE102019109536B4 (en) | Vane type camshaft adjuster | |
WO2018189043A1 (en) | Screw-type compressor arrangement having an axial bearing and a radial bearing | |
EP2157318A2 (en) | Hydraulic supply unit |
Legal Events
Date | Code | Title | Description |
---|---|---|---|
PUAI | Public reference made under article 153(3) epc to a published international application that has entered the european phase |
Free format text: ORIGINAL CODE: 0009012 |
|
17P | Request for examination filed |
Effective date: 20110314 |
|
AK | Designated contracting states |
Kind code of ref document: A2 Designated state(s): AT BE BG CH CY CZ DE DK EE ES FI FR GB GR HR HU IE IS IT LI LT LU LV MC MK MT NL NO PL PT RO SE SI SK SM TR |
|
AX | Request for extension of the european patent |
Extension state: AL BA RS |
|
RIN1 | Information on inventor provided before grant (corrected) |
Inventor name: ZINKE, BORIS |
|
DAX | Request for extension of the european patent (deleted) | ||
RAP1 | Party data changed (applicant data changed or rights of an application transferred) |
Owner name: MAGNA POWERTRAIN BAD HOMBURG GMBH |
|
17Q | First examination report despatched |
Effective date: 20150413 |
|
GRAP | Despatch of communication of intention to grant a patent |
Free format text: ORIGINAL CODE: EPIDOSNIGR1 |
|
INTG | Intention to grant announced |
Effective date: 20150914 |
|
GRAS | Grant fee paid |
Free format text: ORIGINAL CODE: EPIDOSNIGR3 |
|
GRAA | (expected) grant |
Free format text: ORIGINAL CODE: 0009210 |
|
AK | Designated contracting states |
Kind code of ref document: B1 Designated state(s): AT BE BG CH CY CZ DE DK EE ES FI FR GB GR HR HU IE IS IT LI LT LU LV MC MK MT NL NO PL PT RO SE SI SK SM TR |
|
REG | Reference to a national code |
Ref country code: GB Ref legal event code: FG4D Free format text: NOT ENGLISH |
|
REG | Reference to a national code |
Ref country code: CH Ref legal event code: EP |
|
REG | Reference to a national code |
Ref country code: IE Ref legal event code: FG4D Free format text: LANGUAGE OF EP DOCUMENT: GERMAN |
|
REG | Reference to a national code |
Ref country code: AT Ref legal event code: REF Ref document number: 775793 Country of ref document: AT Kind code of ref document: T Effective date: 20160315 |
|
REG | Reference to a national code |
Ref country code: DE Ref legal event code: R096 Ref document number: 502009012147 Country of ref document: DE |
|
REG | Reference to a national code |
Ref country code: NL Ref legal event code: MP Effective date: 20160217 |
|
REG | Reference to a national code |
Ref country code: LT Ref legal event code: MG4D |
|
REG | Reference to a national code |
Ref country code: FR Ref legal event code: PLFP Year of fee payment: 8 |
|
PG25 | Lapsed in a contracting state [announced via postgrant information from national office to epo] |
Ref country code: FI Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20160217 Ref country code: IT Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20160217 Ref country code: ES Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20160217 Ref country code: NO Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20160517 Ref country code: GR Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20160518 |
|
PG25 | Lapsed in a contracting state [announced via postgrant information from national office to epo] |
Ref country code: LV Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20160217 Ref country code: NL Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20160217 Ref country code: PL Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20160217 Ref country code: LT Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20160217 Ref country code: PT Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20160617 Ref country code: SE Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20160217 |
|
PGFP | Annual fee paid to national office [announced via postgrant information from national office to epo] |
Ref country code: TR Payment date: 20160620 Year of fee payment: 8 |
|
PG25 | Lapsed in a contracting state [announced via postgrant information from national office to epo] |
Ref country code: DK Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20160217 Ref country code: EE Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20160217 |
|
REG | Reference to a national code |
Ref country code: DE Ref legal event code: R097 Ref document number: 502009012147 Country of ref document: DE |
|
PG25 | Lapsed in a contracting state [announced via postgrant information from national office to epo] |
Ref country code: CZ Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20160217 Ref country code: SM Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20160217 Ref country code: SK Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20160217 Ref country code: RO Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20160217 |
|
PGFP | Annual fee paid to national office [announced via postgrant information from national office to epo] |
Ref country code: FR Payment date: 20160721 Year of fee payment: 8 |
|
PLBE | No opposition filed within time limit |
Free format text: ORIGINAL CODE: 0009261 |
|
STAA | Information on the status of an ep patent application or granted ep patent |
Free format text: STATUS: NO OPPOSITION FILED WITHIN TIME LIMIT |
|
PG25 | Lapsed in a contracting state [announced via postgrant information from national office to epo] |
Ref country code: BE Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES Effective date: 20160731 |
|
26N | No opposition filed |
Effective date: 20161118 |
|
PG25 | Lapsed in a contracting state [announced via postgrant information from national office to epo] |
Ref country code: SI Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20160217 |
|
REG | Reference to a national code |
Ref country code: CH Ref legal event code: PL |
|
GBPC | Gb: european patent ceased through non-payment of renewal fee |
Effective date: 20160720 |
|
PG25 | Lapsed in a contracting state [announced via postgrant information from national office to epo] |
Ref country code: MC Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20160217 |
|
PG25 | Lapsed in a contracting state [announced via postgrant information from national office to epo] |
Ref country code: LI Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES Effective date: 20160731 Ref country code: CH Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES Effective date: 20160731 |
|
REG | Reference to a national code |
Ref country code: IE Ref legal event code: MM4A |
|
PG25 | Lapsed in a contracting state [announced via postgrant information from national office to epo] |
Ref country code: GB Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES Effective date: 20160720 |
|
PG25 | Lapsed in a contracting state [announced via postgrant information from national office to epo] |
Ref country code: IE Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES Effective date: 20160720 |
|
PG25 | Lapsed in a contracting state [announced via postgrant information from national office to epo] |
Ref country code: LU Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES Effective date: 20160720 |
|
REG | Reference to a national code |
Ref country code: AT Ref legal event code: MM01 Ref document number: 775793 Country of ref document: AT Kind code of ref document: T Effective date: 20160720 |
|
PG25 | Lapsed in a contracting state [announced via postgrant information from national office to epo] |
Ref country code: AT Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES Effective date: 20160720 |
|
REG | Reference to a national code |
Ref country code: FR Ref legal event code: ST Effective date: 20180330 |
|
PG25 | Lapsed in a contracting state [announced via postgrant information from national office to epo] |
Ref country code: HU Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT; INVALID AB INITIO Effective date: 20090720 Ref country code: FR Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES Effective date: 20170731 Ref country code: CY Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20160217 |
|
PG25 | Lapsed in a contracting state [announced via postgrant information from national office to epo] |
Ref country code: MK Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20160217 Ref country code: IS Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20160217 Ref country code: HR Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20160217 Ref country code: MT Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20160217 |
|
REG | Reference to a national code |
Ref country code: DE Ref legal event code: R082 Ref document number: 502009012147 Country of ref document: DE Representative=s name: HOFFMANN - EITLE PATENT- UND RECHTSANWAELTE PA, DE |
|
REG | Reference to a national code |
Ref country code: DE Ref legal event code: R082 Ref document number: 502009012147 Country of ref document: DE Representative=s name: HOFFMANN - EITLE PATENT- UND RECHTSANWAELTE PA, DE Ref country code: DE Ref legal event code: R081 Ref document number: 502009012147 Country of ref document: DE Owner name: HANON SYSTEMS EFP DEUTSCHLAND GMBH, DE Free format text: FORMER OWNER: MAGNA POWERTRAIN BAD HOMBURG GMBH, 61352 BAD HOMBURG, DE |
|
PG25 | Lapsed in a contracting state [announced via postgrant information from national office to epo] |
Ref country code: TR Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES Effective date: 20170720 |
|
P01 | Opt-out of the competence of the unified patent court (upc) registered |
Effective date: 20230613 |
|
PGFP | Annual fee paid to national office [announced via postgrant information from national office to epo] |
Ref country code: BG Payment date: 20230719 Year of fee payment: 15 |
|
PGFP | Annual fee paid to national office [announced via postgrant information from national office to epo] |
Ref country code: DE Payment date: 20230719 Year of fee payment: 15 |