EP1026401A2 - Hydrostatic pump - Google Patents

Hydrostatic pump Download PDF

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Publication number
EP1026401A2
EP1026401A2 EP00101946A EP00101946A EP1026401A2 EP 1026401 A2 EP1026401 A2 EP 1026401A2 EP 00101946 A EP00101946 A EP 00101946A EP 00101946 A EP00101946 A EP 00101946A EP 1026401 A2 EP1026401 A2 EP 1026401A2
Authority
EP
European Patent Office
Prior art keywords
side window
pump
pump according
pump housing
hydrostatic
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.)
Granted
Application number
EP00101946A
Other languages
German (de)
French (fr)
Other versions
EP1026401A3 (en
EP1026401B1 (en
Inventor
Bernhard Arnold
Franz Pawellek
Franz Wirzberger
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Siemens AG
Original Assignee
Siemens AG
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Filing date
Publication date
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Publication of EP1026401A2 publication Critical patent/EP1026401A2/en
Publication of EP1026401A3 publication Critical patent/EP1026401A3/en
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Publication of EP1026401B1 publication Critical patent/EP1026401B1/en
Anticipated expiration legal-status Critical
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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
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01C—ROTARY-PISTON OR OSCILLATING-PISTON MACHINES OR ENGINES
    • F01C21/00—Component parts, details or accessories not provided for in groups F01C1/00 - F01C20/00
    • F01C21/10—Outer members for co-operation with rotary pistons; Casings
    • F01C21/104—Stators; Members defining the outer boundaries of the working chamber
    • F01C21/108—Stators; Members defining the outer boundaries of the working chamber with an axial surface, e.g. side plates
    • 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 hydrostatic pump according to the preamble of claim 1.
  • Such hydrostatic pumps can, for example be designed as a cellular pump, as they are in DE 32 12 363 A1.
  • the well-known construction has a pump housing in which a drive shaft is rotatably mounted is. At the end section dipping into the pump housing A rotor is attached to the drive shaft Radially displaceable wing carries. The one from the rotor wings protruding in the radial direction lie on the Inner circumferential wall of a cam ring, which is eccentrically in the Pump housing is mounted. Two adjacent wings each limit a cell, the volume of which is dependent changes from the rotational angle position of the drive shaft. Face the cells are on the one hand from a pump cover and on the other hand limited by a side window.
  • the at the known solution used side window is a Spring biased into its bearing position, on a Housing cover is supported over which the pump housing is sealed at the end.
  • the spring space for those The spring tensioning the side window is filled with pressure medium, so that when pressure builds up in the cells of the vane pump the side window essentially by the fluid pressure is biased into its sealing position. That is, the spring is only required to the sealing system the side window when starting the pump.
  • the invention is based on the object to create a pump that is characterized by a minimal device technology Distinctive effort and at which the Leakage is minimal when the pump is started.
  • the front of the pump housing to seal the side window and in via a spring element The pump can preload towards the displacement chamber constructed much simpler than in the known solution in addition to the side window there is also a housing cover was required.
  • prestressing the side window into its sealing position only via the spring element so that no channels, pressure relief valve devices etc. formed in the pump housing to the spring space - as in the prior art - to be filled with pressure medium. Because of the missing housing cover the pump in the axial direction can be essential shorter than in the previously described prior art become.
  • the construction of the invention can be particularly advantageous to use in vane pumps where the cells formed between two wings on each end limited by the pump housing and the side window are, the latter against the spring element the cam ring is biased.
  • Tilting of the side window can be prevented in the spring element at a radial distance from the drive shaft, i.e. attacks on the edge area of the side window.
  • the overall length can be further reduced if the disc spring immersed in an annular recess in the side window.
  • the depth of this ring recess is that Axial length of the disc spring adjusted.
  • a ring channel can open in the area of the ring recess, over the pressure medium into a flushing channel of the pump housing is feedable. This pressure medium flow can then be used for cooling / lubrication. In this embodiment it is preferred if the disc spring with Breakthroughs are provided through which the flushing flow pass can.
  • the construction described above with a minimal axial length can be used particularly advantageously for pumps, where the vane pump is a high pressure pump is assigned, whose suction connection with the pressure connection the vane pump is connected.
  • the high pressure pump is preferably designed as a radial piston pump, the Displacer (piston) through an eccentric of the drive shaft be operated.
  • the front seal of the eccentric space is preferably carried out in this embodiment through the side window. In such an embodiment the flushing channel described above opens into the eccentric space, so that cooling / lubrication of the high pressure pump can be done.
  • the hydrostatic pump is designed as a vane pump 1.
  • the structure according to the invention can be also with other hydrostatic pumps, for example use with a gear pump etc., where the Pressure medium pressurized up to about 10 bar shall be.
  • the vane pump 1 shown in Figure 1 has a Pump housing 2, in which a drive shaft 4 rotatably mounted is. This is rotatably connected to a rotor 6, which has a plurality of radial slots in which Wing 8 are guided radially.
  • the wings 8 are hydraulic with their protruding beyond the rotor 6 End sections in contact position against the inner peripheral wall a cam ring 10 pressed.
  • This cam ring 10 is stored in the pump housing 2 and has an eccentric Inner bore in which the rotor 6 is guided, so that in the Representation according to Figure 1 between the rotor 6, the cam ring 10 and 2 adjacent wings 8 a sickle-shaped Cell 12 is limited, the volume of which is dependent changed by the angle of rotation of the drive shaft 4.
  • FIG 2 shows a section along the line A-A in Figure 1. Accordingly, the cells 12 are front of one Limited pump cover 14 and a side plate 16, which rest on the cam ring 10.
  • the pump housing 2 is provided with a receiving bore 18 provided on the peripheral walls of the cam ring 10 and Side window 16 are supported or guided.
  • the wings dive 8 in radial slots being between the bottom of the radial slot and the adjacent face of each Wing 8 a pressure chamber 20 for receiving pressure medium is provided, via which the wings 8 in their contact position be biased against the cam ring 10.
  • the inner bore 22 penetrated by the drive shaft 4 is widened towards the end faces of the rotor 6, so that the position positioning of the rotor 6 is facilitated.
  • the non-rotatable connection between drive shaft 4 and rotor 6 takes place via a suitable connecting element 24, for example a key that fits into an axial groove 26 of the rotor 6 immersed and in a pocket of the drive shaft 4 is recorded in sections.
  • a suitable connecting element 24 for example a key that fits into an axial groove 26 of the rotor 6 immersed and in a pocket of the drive shaft 4 is recorded in sections.
  • a sliding bush 28 for guiding the drive shaft 4.
  • the side window 16 via a spring element, in the present case a disc spring 30 biased into their bearing position against the cam ring 10.
  • the plate spring 30 is supported on a radial shoulder 32 of the pump housing 2.
  • the outside diameter the plate spring 30 is only slightly smaller than the inside diameter the receiving bore 18 so that the plate spring 30 applied to the side window 16 with a maximum span.
  • This broad support means that the Side window 16 reliably prevented, so that even higher drive shaft speeds a reliable system of the side part 16 on the cam ring 10 is guaranteed.
  • the plate spring 30 dips into an annular recess 34 a whose axial depth is slightly less than the axial length of the Disc spring 30 is formed.
  • An opening opens into the end face of the ring recess 34 Ring channel 36 through which a pressure medium flow through the Side window into a flushing channel 38 of the pump housing 2 can be done. Via this flushing channel 38 Pressure medium for cooling / lubricating highly stressed components the pump 1 are branched off. This optional Formation of a coolant / lubricant flow is, for example then used when the drive shaft 4 also to drive a high pressure pump, for example a radial piston pump is used that on the flushing-lubrication circuit connected.
  • the plate spring 30 is at least in the area of the flushing channel 38 provided with at least one opening 40, via the in the pressure medium through the plate spring 30 can enter the rinsing channel 38.
  • the supply and discharge of the pressure medium to and from the Cells 12 take place via a suction kidney 42 or a pressure kidney 44, which are formed in the housing cover 14 and in corresponding recesses 46, 48 in the adjacent End face of the side window 16 open.
  • the sealing of the side window 16 with respect to the housing 2 takes place via an O-ring 50 which is in an annular groove is inserted on the outer circumference of the side window 16.
  • Such a vane pump 1 is installed very easy.
  • the drive shaft 4 becomes the high pressure pump, if necessary inserted into the pump housing 2 and then the Disc spring 30 inserted so that this on the radial shoulder 32 rests. Then the side window 16 with the sliding bush 28 pushed onto the drive shaft 4, until it comes into contact position with the plate spring 30.
  • the housing cover 14 with the Pump housing 2 screwed.
  • the Housing cover 14 with the Pump housing 2 screwed.
  • the Side window 16 is by the force of Belleville washer 30 against the one against the housing cover 14 Hubring 10 biased without further attachment or Prestressing means required.
  • the tension of the plate spring 30 is designed so that the side window 16 in the over Vane pump 1 sealing maximum pressure to be applied rests on the cam ring as well as on the vanes 12 and the rotor 6, so that the leakage is minimal in this pressure range.
  • the side part 16 can also the Frontal limitation of the pump housing for the radial piston pump form. That is, in this case the side window forms 16 at least part of an end boundary of the eccentric chamber of the radial piston pump 1.
  • a hydrostatic pump is disclosed, in particular a vane pump, in which the displacement space on the front limited by a housing cover and a side window is. The latter is in its contact position via a spring element biased and forms the frontal portion of the Pump housing for the vane pump.
  • the side surface of the side plate 16, which is the rotor 6 and is assigned to the cam ring 10 is a metallic sealing surface educated.
  • the side surfaces of the rotor 6 and the cam ring 10, the side window 16 or the pump cover 14 are assigned, designed as metallic sealing surfaces.
  • the cells 12 are sealed by means of the dense one Pressure of the sealing surface of the side window 16 against the sealing surfaces of the rotor 6 and the cam ring 10.
  • the contact pressure is generated only by the plate spring 30.
  • the side window 16 has in addition to the implementation of the drive shaft 4th no through channels, so no hydraulic Connection between the two areas of the pump housing 2 is present, which is formed on both sides of the side window 16 are separated by the side window 16.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Rotary Pumps (AREA)
  • Details And Applications Of Rotary Liquid Pumps (AREA)

Abstract

The side plate(16) of the pump is loaded by a disc spring(30) in the direction of the displacement chamber, and the pump casing(2) is sealed on the end face side. The displacement component is a vane wheel. A rotor(6) is torsionally fixed on the shaft(4) and supports radially movable vanes(8), the end sections of which lie closely upon the inner circumference of a thrust ring(10) mounted in the pump casing. The side plate is preloaded against the thrust ring and cell wheel by the disc spring.

Description

Die Erfindung betrifft eine hydrostatische Pumpe gemäß dem Oberbegriff des Patentanspruch 1.The invention relates to a hydrostatic pump according to the preamble of claim 1.

Derartige hydrostatische Pumpen können beispielsweise als Zellenradpumpe ausgeführt werden, wie sie in der DE 32 12 363 A1 beschrieben ist. Die bekannte Konstruktion hat ein Pumpengehäuse, in dem eine Antriebswelle drehbar gelagert ist. An dem in das Pumpengehäuse hineintauchenden Endabschnitt der Antriebswelle ist ein Rotor befestigt, der in Radialrichtung verschiebbare Flügel trägt. Die aus dem Rotor in Radialrichtung hervorstehenden Flügel liegen an der Innenumfangswandung eines Hubrings an, der exzentrisch im Pumpengehäuse gelagert ist. Jeweils zwei benachbarte Flügel begrenzen eine Zelle, deren Volumen sich in Abhängigkeit von der Drehwinkelposition der Antriebswelle ändert. Stirnseitig sind die Zellen einerseits von einem Pumpendeckel und andererseits von einer Seitenscheibe begrenzt. Die bei der bekannten Lösung verwendete Seitenscheibe wird über eine Feder in ihre Anlageposition vorgespannt, die an einem Gehäusedeckel abgestützt ist, über den das Pumpengehäuse stirnseitigt abgedichtet ist. Der Federraum für die die Seitenscheibe vorspannende Feder ist mit Druckmittel gefüllt, so daß bei Druckaufbau in den Zellen der Flügelzellenpumpe die Seitenscheibe im wesentlichen durch den Fluiddruck in ihre Dichtposition vorgespannt ist. D.h., die Feder wird lediglich dazu benötigt, um die dichtende Anlage der Seitenscheibe beim Anfahren der Pumpe zu gewährleisten.Such hydrostatic pumps can, for example be designed as a cellular pump, as they are in DE 32 12 363 A1. The well-known construction has a pump housing in which a drive shaft is rotatably mounted is. At the end section dipping into the pump housing A rotor is attached to the drive shaft Radially displaceable wing carries. The one from the rotor wings protruding in the radial direction lie on the Inner circumferential wall of a cam ring, which is eccentrically in the Pump housing is mounted. Two adjacent wings each limit a cell, the volume of which is dependent changes from the rotational angle position of the drive shaft. Face the cells are on the one hand from a pump cover and on the other hand limited by a side window. The at the known solution used side window is a Spring biased into its bearing position, on a Housing cover is supported over which the pump housing is sealed at the end. The spring space for those The spring tensioning the side window is filled with pressure medium, so that when pressure builds up in the cells of the vane pump the side window essentially by the fluid pressure is biased into its sealing position. That is, the spring is only required to the sealing system the side window when starting the pump.

Nachteilig bei dieser Konstruktion ist, daß ein erheblicher Aufwand erforderlich ist, um das Druckmittel in den Federraum einzuleiten und dort auf ein vorbestimmtes Niveau zu begrenzen. Das erhebliche Volumen des Federraums ist auch beim Anfahren der Pumpe nachteiligt, da der Ausgangsdruck erst dann vollständig aufbaubar ist, wenn der Druck im Federraum das vorbestimmte Niveau erreicht hat und somit die Seitenscheibe die zellenstirnseitig dichtend abschließt.The disadvantage of this construction is that it is considerable Effort is required to get the pressure fluid into the Initiate spring space and there to a predetermined level to limit. The considerable volume of the spring chamber is also disadvantageous when starting the pump because of the outlet pressure is only fully buildable when the pressure has reached the predetermined level in the spring chamber and thus the side window seals the cell face.

Demgegenüber liegt der Erfindung die Aufgabe zugrunde, eine Pumpe zu schaffen, die sich durch einen minimalen vorrichtungstechnischen Aufwand auszeichnet und bei der die Leckage bereits beim Anfahren der Pumpe minimal ist.In contrast, the invention is based on the object to create a pump that is characterized by a minimal device technology Distinctive effort and at which the Leakage is minimal when the pump is started.

Diese Aufgabe wird durch eine hydrostatische Pumpe mit den Merkmalen des Patentanspruchs 1 gelöst.This task is accomplished using a hydrostatic pump solved the features of claim 1.

Durch die Maßnahme, das Pumpengehäuse stirnseitig durch die Seitenscheibe abzudichten und über ein Federelement in Richtung auf den Verdrängerraum vorzuspannen kann die Pumpe wesentlich einfacher als bei der bekannten Lösung aufgebaut werden, bei der zusätzlich zur Seitenscheibe noch ein Gehäusedeckel erforderlich war. Erfindungsgemäß erfolgte somit das Vorspannen der Seitenscheibe in ihre Dichtlage nur über das Federelement, so daß keine Kanäle, Druckbegrenzungsventileinrichtungen etc. im Pumpengehäuse ausgebildet werden müssen, um den Federraum - wie beim Stand der Technik - mit Druckmittel zu füllen. Aufgrund des fehlenden Gehäusedeckels kann die Pumpe in Axialrichtung wesentlich kürzer als beim vorbeschriebenen Stand der Technik ausgeführt werden.As a result of the measure, the front of the pump housing to seal the side window and in via a spring element The pump can preload towards the displacement chamber constructed much simpler than in the known solution in addition to the side window there is also a housing cover was required. Thus, according to the invention prestressing the side window into its sealing position only via the spring element, so that no channels, pressure relief valve devices etc. formed in the pump housing to the spring space - as in the prior art - to be filled with pressure medium. Because of the missing housing cover the pump in the axial direction can be essential shorter than in the previously described prior art become.

Die erfindungsgemäße Konstruktion läßt sich besonders vorteilhaft bei Flügelzellenpumpen einsetzen, bei denen die jeweils zwischen zwei Flügeln ausgebildeten Zellen stirnseitig durch das Pumpengehäuse und die Seitenscheibe begrenzt sind, wobei letzterer über das Federelement gegen den Hubring vorgespannt ist. The construction of the invention can be particularly advantageous to use in vane pumps where the cells formed between two wings on each end limited by the pump housing and the side window are, the latter against the spring element the cam ring is biased.

Ein Kippen der Seitenscheibe läßt sich verhindern, in dem das Federelement im Radialabstand zur Antriebswelle, d.h. am Randbereich der Seitenscheibe angreift.Tilting of the side window can be prevented in the spring element at a radial distance from the drive shaft, i.e. attacks on the edge area of the side window.

Eine besonders kurzbauende Pumpe erhält man, wenn das Federelement als am Pumpengehäuse abgestützte Tellerfeder ausgeführt ist, die die Antriebswelle im Radialabstand umgreift.You get a particularly short pump if that Spring element as a plate spring supported on the pump housing is executed, which engages around the drive shaft at a radial distance.

Die Baulänge läßt sich weiter verringern, wenn die Tellerfeder in eine Ringausnehmung der Seitenscheibe eintaucht. Die Tiefe dieser Ringausnehmung ist an die Axiallänge der Tellerfeder angepaßt.The overall length can be further reduced if the disc spring immersed in an annular recess in the side window. The depth of this ring recess is that Axial length of the disc spring adjusted.

Im Bereich der Ringausnehmung kann ein Ringkanal münden, über den Druckmittel in einen Spülkanal des Pumpengehäuses einspeisbar ist. Diese Druckmittelströmung kann dann zur Kühlung/Schmierung verwendet werden. Bei diesem Ausführungsbeispiel wird es bevorzugt, wenn die Tellerfeder mit Durchbrüchen versehen ist, durch die die Spülströmung hindurchtreten kann.A ring channel can open in the area of the ring recess, over the pressure medium into a flushing channel of the pump housing is feedable. This pressure medium flow can then be used for cooling / lubrication. In this embodiment it is preferred if the disc spring with Breakthroughs are provided through which the flushing flow pass can.

Die vorbeschriebene Konstruktion mit minimaler Axialbaulänge läßt sich besonders vorteilhaft bei Pumpen einsetzen, bei denen der Flügelzellenpumpe eine Hochdruckpumpe zugeordnet ist, deren Sauganschluß mit dem Druckanschluß der Flügelzellenpumpe verbunden ist. Die Hochdruckpumpe wird vorzugsweise als Radialkolbenpumpe ausgeführt, deren Verdränger (Kolben) durch einen Exzenter der Antriebswelle betätigt werden. Die stirnseitige Abdichtung des Exzenterraums erfolgt bei diesem Ausführungsbeispiel vorzugsweise durch die Seitenscheibe. Bei einem derartigen Ausführungsbeispiel mündet der vorbeschriebene Spülkanal in dem Exzenterraum, so daß eine Kühlung-/Schmierung der Hochdruckpumpe erfolgen kann. The construction described above with a minimal axial length can be used particularly advantageously for pumps, where the vane pump is a high pressure pump is assigned, whose suction connection with the pressure connection the vane pump is connected. The high pressure pump is preferably designed as a radial piston pump, the Displacer (piston) through an eccentric of the drive shaft be operated. The front seal of the eccentric space is preferably carried out in this embodiment through the side window. In such an embodiment the flushing channel described above opens into the eccentric space, so that cooling / lubrication of the high pressure pump can be done.

Zur Optimierung der Druckmittelzufuhr und -abfuhr sind in der dem Hubring zugewandten Stirnfläche der Seitenscheibe Taschen ausgebildet, die einen Teil der Saug- und Drucknieren ausbilden.To optimize the pressure medium supply and discharge in the end face of the side window facing the cam ring Bags formed that are part of the suction and Form pressure kidneys.

Sonstige vorteilhafte Weiterbildungen der Erfindung sind Gegenstand der weiteren Unteransprüche.Other advantageous developments of the invention are the subject of further subclaims.

Im folgenden wird ein bevorzugtes Ausführungsbeispiel der Erfindung anhand schematischer Zeichnungen näher erläutert. Es zeigen:

  • Figur 1 eine geschnittene Vorderansicht einer erfindungsgemäßen Flügelzellenpumpe und
  • Figur 2 eine geschnittene Seitenansicht der Flügelzellenpumpe aus Figur 1.
    • A preferred embodiment of the invention is explained in more detail below with the aid of schematic drawings. Show it:
  • Figure 1 is a sectional front view of a vane pump according to the invention and
  • FIG. 2 shows a sectional side view of the vane pump from FIG. 1.

    • Bei dem in Figur 1 dargestellten Ausführungsbeispiel ist die hydrostatische Pumpe als Flügelzellenpumpe 1 ausgeführt. Pinzipiell läßt sich der erfindungsgemäße Aufbau jedoch auch bei anderen hydrostatischen Pumpen, beispielsweise bei einer Zahnradpumpe etc. verwenden, bei denen das Druckmittel mit Drücken bis zu etwa 10 bar beaufschlagt werden soll.In the embodiment shown in Figure 1 the hydrostatic pump is designed as a vane pump 1. In principle, however, the structure according to the invention can be also with other hydrostatic pumps, for example use with a gear pump etc., where the Pressure medium pressurized up to about 10 bar shall be.

    Die in Figur 1 dargestellte Flügelzellenpumpe 1 hat ein Pumpengehäuse 2, in dem eine Antriebswelle 4 drehbar gelagert ist. Diese ist drehfest mit einem Rotor 6 verbunden, der eine Vielzahl von Radialschlitzen aufweist, in denen Flügel 8 radial verschiebbar geführt sind. Die Flügel 8 werden hydraulisch mit ihren über den Rotor 6 hinausstehenden Endabschnitten in Anlageposition gegen die Innenumfangswandung eines Hubrings 10 gepreßt. Dieser Hubring 10 ist im Pumpengehäuse 2 gelagert und hat eine exzentrische Innenbohrung, in der der Rotor 6 geführt ist, so daß in der Darstellung nach Figur 1 zwischen dem Rotor 6, dem Hubring 10 und jeweils 2 benachbarten Flügeln 8 eine sichelförmige Zelle 12 begrenzt ist, deren Volumen sich in Abhängigkeit von dem Drehwinkel der Antriebswelle 4 verändert.The vane pump 1 shown in Figure 1 has a Pump housing 2, in which a drive shaft 4 rotatably mounted is. This is rotatably connected to a rotor 6, which has a plurality of radial slots in which Wing 8 are guided radially. The wings 8 are hydraulic with their protruding beyond the rotor 6 End sections in contact position against the inner peripheral wall a cam ring 10 pressed. This cam ring 10 is stored in the pump housing 2 and has an eccentric Inner bore in which the rotor 6 is guided, so that in the Representation according to Figure 1 between the rotor 6, the cam ring 10 and 2 adjacent wings 8 a sickle-shaped Cell 12 is limited, the volume of which is dependent changed by the angle of rotation of the drive shaft 4.

    Figur 2 zeigt einen Schnitt entlang der Linie A-A in Figur 1. Demgemäß werden die Zellen 12 stirnseitig von einem Pumpendeckel 14 und einer Seitenscheibe 16 begrenzt, die am Hubring 10 anliegen.Figure 2 shows a section along the line A-A in Figure 1. Accordingly, the cells 12 are front of one Limited pump cover 14 and a side plate 16, which rest on the cam ring 10.

    Das Pumpengehäuse 2 ist mit einer Aufnahmebohrung 18 versehen, an deren Umfangswandungen der Hubring 10 und die Seitenscheibe 16 abgestützt bzw. geführt sind.The pump housing 2 is provided with a receiving bore 18 provided on the peripheral walls of the cam ring 10 and Side window 16 are supported or guided.

    Wie bereits vorstehend angedeutet, tauchen die Flügel 8 in Radialschlitze ein, wobei zwischen dem Boden des Radialschlitzes und der benachbarten Stirnseite des jeweiligen Flügels 8 ein Druckraum 20 zur Aufnahme von Druckmittel vorgesehen ist, über das die Flügel 8 in ihre Anlageposition gegen den Hubring 10 vorgespannt werden.As already indicated above, the wings dive 8 in radial slots, being between the bottom of the radial slot and the adjacent face of each Wing 8 a pressure chamber 20 for receiving pressure medium is provided, via which the wings 8 in their contact position be biased against the cam ring 10.

    Die von der Antriebswelle 4 durchsetzte Innenbohrung 22 ist zu den Stirnseiten des Rotors 6 hin aufgeweitet, so daß die Lagepositionierung des Rotors 6 erleichtert ist. Die drehfeste Verbindung zwischen Antriebswelle 4 und Rotor 6 erfolgt über ein geeignetes Verbindungselement 24, beispielsweise eine Paßfeder, die in eine Axialnut 26 des Rotors 6 eintaucht und in einer Tasche der Antriebswelle 4 abschnittsweise aufgenommen ist. In der Seitenscheibe 16 ist eine Gleitbuchse 28 zur Führung der Antriebswelle 4 angeordnet.The inner bore 22 penetrated by the drive shaft 4 is widened towards the end faces of the rotor 6, so that the position positioning of the rotor 6 is facilitated. The non-rotatable connection between drive shaft 4 and rotor 6 takes place via a suitable connecting element 24, for example a key that fits into an axial groove 26 of the rotor 6 immersed and in a pocket of the drive shaft 4 is recorded in sections. In the side window 16 is a sliding bush 28 for guiding the drive shaft 4.

    Wie Figur 2 entnehmbar ist, wird die Seitenscheibe 16 über ein Federelement, im vorliegenden Fall eine Tellerfeder 30 in ihre Anlageposition gegen den Hubring 10 vorgespannt. Die Tellerfeder 30 stützt sich an einer Radialschulter 32 des Pumpengehäuses 2 ab. Der Außendurchmesser der Tellerfeder 30 ist nur geringfügig kleiner als der Innendurchmesser der Aufnahmebohrung 18, so daß die Tellerfeder 30 mit maximaler Stützweite die Seitenscheibe 16 beaufschlagt. Durch diese breite Abstützung wird ein Kippen der Seitenscheibe 16 zuverlässig verhindert, so daß auch bei höheren Antriebswellendrehzahlen eine zuverlässige Anlage des Seitenteils 16 am Hubring 10 gewährleistet ist.As can be seen in FIG. 2, the side window 16 via a spring element, in the present case a disc spring 30 biased into their bearing position against the cam ring 10. The plate spring 30 is supported on a radial shoulder 32 of the pump housing 2. The outside diameter the plate spring 30 is only slightly smaller than the inside diameter the receiving bore 18 so that the plate spring 30 applied to the side window 16 with a maximum span. This broad support means that the Side window 16 reliably prevented, so that even higher drive shaft speeds a reliable system of the side part 16 on the cam ring 10 is guaranteed.

    Die Tellerfeder 30, taucht in eine Ringausnehmung 34 ein, deren Axialtiefe etwas geringer als die Axiallänge der Tellerfeder 30 ausgebildet ist.The plate spring 30 dips into an annular recess 34 a whose axial depth is slightly less than the axial length of the Disc spring 30 is formed.

    In der Stirnfläche der Ringausnehmung 34 mündet ein Ringkanal 36, über den eine Druckmittelströmung durch die Seitenscheibe hindurch in einen Spülkanal 38 des Pumpengehäuses 2 erfolgen kann. Über diesen Spülkanal 38 kann Druckmittel zur Kühlung/Schmierung von hochbelasteten Bauelementen der Pumpe 1 abgezweigt werden. Diese optionale Ausbildung einer Kühl-/Schmiermittelströmung wird beispielsweise dann eingesetzt, wenn die Antriebswelle 4 auch zum Antrieb einer Hochdruckpumpe, beispielsweise einer Radialkolbenpumpe verwendet wird, die an den Spül- Schmierkreislauf angeschlossen ist.An opening opens into the end face of the ring recess 34 Ring channel 36 through which a pressure medium flow through the Side window into a flushing channel 38 of the pump housing 2 can be done. Via this flushing channel 38 Pressure medium for cooling / lubricating highly stressed components the pump 1 are branched off. This optional Formation of a coolant / lubricant flow is, for example then used when the drive shaft 4 also to drive a high pressure pump, for example a radial piston pump is used that on the flushing-lubrication circuit connected.

    Die Tellerfeder 30 ist zumindest im Bereich des Spülkanals 38 mit zumindest einem Durchbruch 40 versehen, über den das Druckmittel durch die Tellerfeder 30 hindurch in den Spülkanal 38 eintreten kann.The plate spring 30 is at least in the area of the flushing channel 38 provided with at least one opening 40, via the in the pressure medium through the plate spring 30 can enter the rinsing channel 38.

    Selbstverständlich ist die erfindungsgemäße Konstruktion keinesfalls auf die Anwendung von Tellerfedern 30 beschränkt, sondern es können prinzipiell alle geeigneten Federbauarten vorgesehen werden, um die Seitenscheibe 16 in ihre Anlageposition vorzuspannen.Of course, the construction according to the invention in no way limited to the use of disc springs 30, in principle, all suitable spring types can be used be provided to the side window 16 in preload their investment position.

    Die Zu- und Abführung des Druckmittels zur bzw. von den Zellen 12 erfolgt über eine Saugniere 42 bzw. eine Druckniere 44, die im Gehäusedeckel 14 ausgebildet sind und in entsprechenden Ausnehmungen 46, 48 in der benachbarten Stirnfläche der Seitenscheibe 16 münden.The supply and discharge of the pressure medium to and from the Cells 12 take place via a suction kidney 42 or a pressure kidney 44, which are formed in the housing cover 14 and in corresponding recesses 46, 48 in the adjacent End face of the side window 16 open.

    Die Abdichtung der Seitenscheibe 16 gegenüber dem Gehäuse 2 erfolgt über einen O-Ring 50, der in eine Ringnut am Außenumfang der Seitenscheibe 16 eingesetzt ist.The sealing of the side window 16 with respect to the housing 2 takes place via an O-ring 50 which is in an annular groove is inserted on the outer circumference of the side window 16.

    Die Montage einer derartigen Flügelzellenpumpe 1 erfolgt denkbar einfach.Such a vane pump 1 is installed very easy.

    Zunächst wird die Antriebswelle 4 ggf. die Hochdruckpumpe ins Pumpengehäuse 2 eingesetzt und anschließend die Tellerfeder 30 eingelegt, so daß diese auf der Radialschulter 32 aufliegt. Anschließend wird die Seitenscheibe 16 mit der Gleitbuchse 28 auf die Antriebswelle 4 aufgeschoben, bis diese in Anlageposition an die Tellerfeder 30 gelangt.First, the drive shaft 4 becomes the high pressure pump, if necessary inserted into the pump housing 2 and then the Disc spring 30 inserted so that this on the radial shoulder 32 rests. Then the side window 16 with the sliding bush 28 pushed onto the drive shaft 4, until it comes into contact position with the plate spring 30.

    Nach dem Einlegen des Hubrings 10 und des Rotors 6 mit den Flügeln 12 und der drehfesten Verbindung des Rotors 6 mit der Antriebswelle 4 wird der Gehäusedeckel 14 mit dem Pumpengehäuse 2 verschraubt. Durch das Aufschrauben des Pumpengehäuses 14 wird das Paket aus Gehäusedeckel 14, Hubring 10 und Seitenscheibe 16 gegen die Tellerfeder 30 gedrückt. D.h., die Seitenscheibe 16 wird durch die Kraft der Tellerfeder 30, gegen den am Gehäusedeckel 14 anliegenden Hubring 10 vorgespannt, ohne daß es weiterer Befestigungs- oder Vorspannmittel bedarf. Die Spannung der Tellerfeder 30 ist so ausgelegt, daß die Seitenscheibe 16 bei dem über die Flügelzellenpumpe 1 aufzubringendem Maximaldruck dichtend am Hubring sowie an den Flügeln 12 und dem Rotor 6 anliegt, so daß die Leckage in diesem Druckbereich minimal ist.After inserting the cam ring 10 and the rotor 6 with the wings 12 and the rotationally fixed connection of the rotor 6 with the drive shaft 4, the housing cover 14 with the Pump housing 2 screwed. By screwing on the Pump housing 14 is the package of housing cover 14, cam ring 10 and side window 16 pressed against the plate spring 30. That is, the side window 16 is by the force of Belleville washer 30 against the one against the housing cover 14 Hubring 10 biased without further attachment or Prestressing means required. The tension of the plate spring 30 is designed so that the side window 16 in the over Vane pump 1 sealing maximum pressure to be applied rests on the cam ring as well as on the vanes 12 and the rotor 6, so that the leakage is minimal in this pressure range.

    Bei der vorbeschriebenen Variante, bei der die Antriebswelle 4 auch zum Antrieb einer Radialkolbenpumpe verwendet wird, kann das Seitenteil 16 auch gleichzeitig die stirnseitige Begrenzung des Pumpengehäuses für die Radialkolbenpumpe bilden. D.h., in diesem Fall bildet die Seitenscheibe 16 zumindest einen Teil einer stirnseitigen Begrenzung des Exzenterraums der Radialkolbenpumpe 1.In the variant described above, in which the drive shaft 4 also used to drive a radial piston pump is, the side part 16 can also the Frontal limitation of the pump housing for the radial piston pump form. That is, in this case the side window forms 16 at least part of an end boundary of the eccentric chamber of the radial piston pump 1.

    Anstelle einer einzigen Tellerfeder 30 könnten auch mehrere Druckfedern stirnseitig verteilt werden, um die Seitenscheibe 16 gegen den Hubring 10 bzw. die Flügel 12 und den Rotor 6 vorzuspannen.Instead of a single plate spring 30 could also several compression springs are distributed on the front to the side window 16 against the cam ring 10 or the wing 12 and the Preload rotor 6.

    Offenbart ist eine hydrostatische Pumpe, insbesondere eine Flügelzellenpumpe, bei der der Verdrängerraum stirnseitig durch einen Gehäusedeckel und eine Seitenscheibe begrenzt ist. Letztere wird über ein Federelement in ihre Anlageposition vorgespannt und bildet den stirnseitigen Abschnitt des Pumpengehäuses für die Flügelzellenpumpe.A hydrostatic pump is disclosed, in particular a vane pump, in which the displacement space on the front limited by a housing cover and a side window is. The latter is in its contact position via a spring element biased and forms the frontal portion of the Pump housing for the vane pump.

    Die Seitenfläche der Seitenscheibe 16, die dem Rotor 6 und dem Hubring 10 zugeordnet ist, ist als metallische Dichtfläche ausgebildet.The side surface of the side plate 16, which is the rotor 6 and is assigned to the cam ring 10 is a metallic sealing surface educated.

    Ebenso sind die Seitenflächen des Rotors 6 und des Hubrings 10, die der Seitenscheibe 16 oder dem Pumpendeckel 14 zugeordnet sind, als metallische Dichtflächen ausgebildet.Likewise, the side surfaces of the rotor 6 and the cam ring 10, the side window 16 or the pump cover 14 are assigned, designed as metallic sealing surfaces.

    Die Abdichtung der Zellen 12 erfolgt über die dichte Anpressung der Dichtfläche der Seitenscheibe 16 an die Dichtflächen des Rotors 6 und des Hubrings 10. Die Anpresskraft wird dabei nur von der Tellerfeder 30 erzeugt. Die Seitenscheibe 16 weist außer der Durchführung der Antriebswelle 4 keine durchgehenden Kanäle auf, so dass keine hydraulische Verbindung zwischen den zwei Bereichen des Pumpengehäuses 2 vorliegt, die auf beiden Seiten der Seitenscheibe 16 ausgebildet durch die Seitenscheibe 16 getrennt sind.The cells 12 are sealed by means of the dense one Pressure of the sealing surface of the side window 16 against the sealing surfaces of the rotor 6 and the cam ring 10. The contact pressure is generated only by the plate spring 30. The side window 16 has in addition to the implementation of the drive shaft 4th no through channels, so no hydraulic Connection between the two areas of the pump housing 2 is present, which is formed on both sides of the side window 16 are separated by the side window 16.

    Da der Bereich, in dem die Tellerfeder 30 angeordnet ist, vom Hochdruckbereich der Pumpe durch die Seitenscheibe 16 abgedichtet ist, entfallen weitere Dichtungen im Bereich der Tellerfeder 30. Dadurch liegt eine einfach aufgebaute Konstruktion der Pumpe vor.Because the area in which the plate spring 30 is arranged from the high pressure area of the pump through the side window 16 is sealed, there are no further seals in the area the plate spring 30. This is a simply constructed Construction of the pump.

    Weiterhin ist es dadurch möglich den Bereich, in dem die Tellerfeder 30 angeordnet ist, zu spülen, wobei das Mittel zum Spülen keinen Hochdruck aufweisen muss.It also enables the area in which the plate spring 30 is arranged to flush, the agent does not have to have high pressure for flushing.

    Claims (10)

    Hydrostatische Pumpe mit einer in einem Pumpengehäuse (2) gelagerten Antriebswelle (4), über die zumindest ein Verdränger (6, 12) antreibbar ist, um Druckmittel anzusaugen und druckbeaufschlagt über einen Druckanschluß (44) abzugeben, wobei ein Verdrängerraum einerseits durch einen Pumpendeckel (14) und andererseits durch eine im Pumpengehäuse gelagerte Seitenscheibe (16) begrenzt ist, dadurch gekennzeichnet, daß die Seitenscheibe (16) über ein Federelement (30) in Richtung auf den Verdrängerraum vorgespannt ist und das Pumpengehäuse (2) stirnseitig abdichtet.Hydrostatic pump with one in a pump housing (2) mounted drive shaft (4), via which at least a displacer (6, 12) can be driven to apply pressure medium suck in and pressurized via a pressure connection (44) to deliver, with a displacement space on the one hand through a pump cover (14) and on the other through a side window mounted in the pump housing (16) is limited, characterized in that the side window (16) via a spring element (30) in the direction is biased to the displacement chamber and the pump housing (2) seals on the face. Hydrostatische Pumpe nach Patentanspruch 1, dadurch gekennzeichnet, daß der Verdränger ein Zellenrad ist, bei dem ein drehfest mit der Welle (4) verbundener Rotor (6) radial verschiebbare Flügel (8) trägt, deren Endabschnitte dichtend am Innenumfang eines im Pumpengehäuse (2) gelagerten Hubrings (10) anliegen und den Verdrängerraum bildende Zellen (12) begrenzen, dadurch gekennzeichnet, daß die Seitenscheibe (16) über das Federelement (30) gegen den Hubring (10) und das Zellenrad vorgespannt ist.Hydrostatic pump according to claim 1, characterized in that the displacer is a cellular wheel, at which has a rotor connected to the shaft (4) in a rotationally fixed manner (6) radially displaceable wing (8) carries, the end portions sealing on the inner circumference of one in the pump housing (2) bearing ring (10) and the displacement chamber limit forming cells (12), characterized in that that the side window (16) over the spring element (30) biased against the cam ring (10) and the cellular wheel is. Hydrostatische Pumpe nach Patentanspruch 1 oder 2, dadurch gekennzeichnet, daß das Federelement (30) stirnseitig im Radialabstand zur Antriebswelle (4) an der Seitenscheibe (16) angreift.Hydrostatic pump according to claim 1 or 2, characterized characterized in that the spring element (30) on the end face at a radial distance from the drive shaft (4) on the Side window (16) attacks. Hydrostatische Pumpe nach einem der vorhergehenden Patentansprüche, dadurch gekennzeichnet, daß das Federelement eine am Pumpengehäuse (2) abgestützte Tellerfeder (30) ist. Hydrostatic pump according to one of the preceding claims, characterized in that the spring element a disc spring supported on the pump housing (2) (30) is. Hydrostatische Pumpe nach Patentanspruch 4, dadurch gekennzeichnet, daß die Teilerfeder (30) in eine Ringausnehmung (34) der Seitenscheibe (16) eintaucht.Hydrostatic pump according to claim 4, characterized in that the divider spring (30) in an annular recess (34) of the side window (16) dips. Hydrostatische Pumpe nach Patentanspruch 5, dadurch gekennzeichnet, daß in der Ringausnehmung (34) ein Ringkanal (36) mündet, über den Druckmittel durch die Seitenscheibe (16) hindurch zu einem Spülkanal (38) im Pumpengehäuse (2) führbar ist.Hydrostatic pump according to claim 5, characterized in that in the ring recess (34) an annular channel (36) opens via the pressure medium through the side window (16) through to a flushing channel (38) in the Pump housing (2) is feasible. Hydrostatische Pumpe nach Patentanspruch 6 dadurch gekennzeichnet, daß die Tellerfeder (30) zumindest einen Durchbruch (40) zur Durchführung des Druckmittels aufweist.Hydrostatic pump according to claim 6, characterized in that the plate spring (30) at least one Breakthrough (40) for carrying the pressure medium. Hydrostatische Pumpe nach einem der vorhergehenden Patentansprüche, dadurch gekennzeichnet, daß im Pumpengehäuse (2) eine Radialkolbenpumpe angeordnet ist, deren Verdränger von einem Exzenter der Antriebswelle (4) angetrieben sind und deren Exzenterraum zumindest abschnittsweise von der Seitenscheibe (16) begrenzt ist.Hydrostatic pump according to one of the preceding claims, characterized in that in the pump housing (2) a radial piston pump is arranged, the Displacer driven by an eccentric of the drive shaft (4) are and their eccentric space at least in sections is limited by the side window (16). Hydrostatische Pumpe nach Patentanspruch 6 und 8, dadurch gekennzeichnet, daß der Spülkanal (38) im Exzenterraum mündet.Hydrostatic pump according to claims 6 and 8, characterized characterized in that the flushing channel (38) in the eccentric space flows. Hydrostatische Pumpe nach einem der vorhergehenden Patentansprüche, dadurch gekennzeichnet, daß in der Seitenscheibe (16) stirnseitig Ausnehmungen (46, 48) zur Ausbildung einer Saug- bzw. Druckniere (42, 44) ausgebildet sind.Hydrostatic pump according to one of the preceding claims, characterized in that in the side window (16) recesses (46, 48) on the end face Formation of a suction or pressure kidney (42, 44) are.
    EP00101946A 1999-02-03 2000-02-01 Hydrostatic pump Expired - Lifetime EP1026401B1 (en)

    Applications Claiming Priority (2)

    Application Number Priority Date Filing Date Title
    DE19904339A DE19904339A1 (en) 1999-02-03 1999-02-03 Hydrostatic pump
    DE19904339 1999-02-03

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    EP1026401A2 true EP1026401A2 (en) 2000-08-09
    EP1026401A3 EP1026401A3 (en) 2001-09-26
    EP1026401B1 EP1026401B1 (en) 2003-06-11

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    EP00101946A Expired - Lifetime EP1026401B1 (en) 1999-02-03 2000-02-01 Hydrostatic pump

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    Cited By (3)

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    WO2009135587A2 (en) * 2008-05-08 2009-11-12 Ixetic Bad Homburg Gmbh Pump
    EP3081741A3 (en) * 2015-04-17 2017-01-04 Schwäbische Hüttenwerke Automotive GmbH Pump
    US10458406B2 (en) * 2016-03-11 2019-10-29 Magna Powertrain Bad Homburg GmbH Seal arrangement for a switchable vane cell pump of cartridge design

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    CN102251962A (en) * 2011-08-18 2011-11-23 肖义堃 Blade pump
    DE102020116748A1 (en) 2020-06-25 2022-02-17 Schwäbische Hüttenwerke Automotive GmbH Pump with axially effective spring seal

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    Cited By (7)

    * Cited by examiner, † Cited by third party
    Publication number Priority date Publication date Assignee Title
    WO2009135587A2 (en) * 2008-05-08 2009-11-12 Ixetic Bad Homburg Gmbh Pump
    WO2009135587A3 (en) * 2008-05-08 2010-03-18 Ixetic Bad Homburg Gmbh Pump
    EP3081741A3 (en) * 2015-04-17 2017-01-04 Schwäbische Hüttenwerke Automotive GmbH Pump
    US10082139B2 (en) 2015-04-17 2018-09-25 Schwäbische Hüttenwerke Automotive GmbH Pump comprising a spring
    EP3081741B1 (en) 2015-04-17 2019-11-13 Schwäbische Hüttenwerke Automotive GmbH Pump
    US11143181B2 (en) 2015-04-17 2021-10-12 Schwäbische Hüttenwerke Automotive GmbH Pump comprising a spring
    US10458406B2 (en) * 2016-03-11 2019-10-29 Magna Powertrain Bad Homburg GmbH Seal arrangement for a switchable vane cell pump of cartridge design

    Also Published As

    Publication number Publication date
    DE50002506D1 (en) 2003-07-17
    DE19904339A1 (en) 2000-08-10
    EP1026401A3 (en) 2001-09-26
    EP1026401B1 (en) 2003-06-11

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