EP1785622A1 - Hydraulic pump - Google Patents

Hydraulic pump Download PDF

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Publication number
EP1785622A1
EP1785622A1 EP06023728A EP06023728A EP1785622A1 EP 1785622 A1 EP1785622 A1 EP 1785622A1 EP 06023728 A EP06023728 A EP 06023728A EP 06023728 A EP06023728 A EP 06023728A EP 1785622 A1 EP1785622 A1 EP 1785622A1
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EP
European Patent Office
Prior art keywords
rotor
control
control pin
pump according
tank
Prior art date
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Granted
Application number
EP06023728A
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German (de)
French (fr)
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EP1785622B1 (en
Inventor
Marcus Fischer
Robert Saric
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Weber Hydraulik GmbH Germany
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Weber Hydraulik GmbH Germany
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Publication of EP1785622A1 publication Critical patent/EP1785622A1/en
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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B1/00—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders
    • F04B1/04—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders having cylinders in star- or fan-arrangement
    • F04B1/047—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders having cylinders in star- or fan-arrangement with actuating or actuated elements at the outer ends of the cylinders
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B1/00—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders
    • F04B1/04—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders having cylinders in star- or fan-arrangement
    • F04B1/10—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders having cylinders in star- or fan-arrangement the cylinders being movable, e.g. rotary
    • F04B1/107—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders having cylinders in star- or fan-arrangement the cylinders being movable, e.g. rotary with actuating or actuated elements at the outer ends of the cylinders
    • F04B1/1071—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders having cylinders in star- or fan-arrangement the cylinders being movable, e.g. rotary with actuating or actuated elements at the outer ends of the cylinders with rotary cylinder blocks
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B1/00—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders
    • F04B1/04—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders having cylinders in star- or fan-arrangement
    • F04B1/10—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders having cylinders in star- or fan-arrangement the cylinders being movable, e.g. rotary
    • F04B1/107—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders having cylinders in star- or fan-arrangement the cylinders being movable, e.g. rotary with actuating or actuated elements at the outer ends of the cylinders
    • F04B1/1071—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders having cylinders in star- or fan-arrangement the cylinders being movable, e.g. rotary with actuating or actuated elements at the outer ends of the cylinders with rotary cylinder blocks
    • F04B1/1072—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders having cylinders in star- or fan-arrangement the cylinders being movable, e.g. rotary with actuating or actuated elements at the outer ends of the cylinders with rotary cylinder blocks with cylinder blocks and actuating cams rotating together
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B23/00—Pumping installations or systems
    • F04B23/02—Pumping installations or systems having reservoirs
    • F04B23/025—Pumping installations or systems having reservoirs the pump being located directly adjacent the reservoir
    • F04B23/026—Pumping installations or systems having reservoirs the pump being located directly adjacent the reservoir a pump-side forming a wall of the reservoir

Definitions

  • the invention relates to a generic pump according to the preamble of the main claim, namely a hydraulic, preferably driven by an electric motor pump with two connections, of which in the one direction of rotation of one as a pressure and the other as a suction port and - opposite direction of rotation - vice versa with a housing with respect to a non-rotatable control pin, with a housing disposed in the housing and rotatable about a rotary axis housing rotatable rotor, comprising a plurality, preferably three radially movable, with its outer ends on an eccentric bearing supporting pump piston whose inner ends each one - close in the volume-changing piston chamber.
  • Reversible pumps for various applications for small volume flows eg 0.5 1 / min
  • high pressures eg up to 400 bar
  • clearly defined lifetimes eg 150 hours
  • Today's gear pumps are inexpensive, but do not reach the required pressure level and are not reversible at low flow rates.
  • valve-controlled single-piston pumps are also not reversible and ruled out due to the cost of the reversal by means of a solenoid valve and because of the high pulsation caused by the high noise level. In addition, they have a much higher than required by the market life and are therefore too expensive.
  • Known generic, slot-controlled radial piston pumps have a rotor with radial pump piston and a fixed control pin with two radial control slots.
  • the rotor is rotatably mounted on the control pin.
  • the bearing must also ensure the interception of the pumping forces at the joint between the rotor and the oil pressure control spigot.
  • a leakage is inevitable due to the design, which has a negative effect on the efficiency.
  • the rotor will jam on the control pin in the event of severe temperature fluctuations. Constant wear in the course of operation can increase the leakage, which has a negative effect on the efficiency and is highly undesirable.
  • the invention is based on the object Generic pump according to the preamble of the main claim easier in the production and assembly and thus cheaper educate so that it remains leaking poor in operation despite wear.
  • control pin has two control surfaces and in the axial direction next to the rotor and with the two control surfaces at one end face abuts that one each with each bore associated, parallel to the axis of rotation axially extending and opening at the end of the rotor bore is provided that in the control pin with its tank facing the tank port to a tank and with its side facing away from the tank line connection only with one of the control surfaces as well as provided with one of the two ports connectable suction check valve, while another Saugschschreibventil with its tank facing the tank connection to the tank and with its side facing away from the tank line connection only with both the other of the control surfaces and with the other Ren of the two terminals is connected, and that each line connection of the Saugschtschventile is connected to a respective provided between the housing and the jacket of the control pin disposed therein circumferential, front or rear annular channel, in particular if the annular channel at its relative
  • the annular channels are configured such that by the hydraulically effective, the end face of the rotor facing and next adjacent, formed by the control pin front annular surface with decreasing radius and the housing itself formed by the rear annular surface upon pressurization of the annular channel in the direction of the rotor acting resulting force results.
  • the inventive principle thus lies in the axial arrangement of the control pin on the end face of the rotor and the pressing of these two parts dependent on the operating pressure in the hydraulic system.
  • the connection point of these parts is not only relatively tight in operation and thus low in leakage; even with wear (abrasion) of the end face of the rotor, the required adjustment takes place automatically and automatically.
  • the invention provides a simpler in the production and assembly and thus more cost-effective pump, which is extremely low leakage even during operation despite wear.
  • the front face of the rotor adjacent the front annular channel and the end face of the rotor remote rear ring channel are connected via a respective transverse bore with the associated line connection of Saugrücktschventile, resulting in a particularly simple production.
  • this has a circular cylindrical shell and is the rear and front annular channel of two circumferential seals adjacent.
  • the pump unit formed by the actual hydraulic reversible pump 1, 2, 12 and the electric motor 9 flanged to it on one side and driving the latter has, as shown in FIG. 1, a housing 12, on the other side of which a tank 11 for the Hydraulic fluid is attached, which is preferably formed of oil.
  • the pump is provided with two ports 13,14, of which in one direction of rotation one serves as a pressure for the supply line and the other as a line connection for the return line and -in the opposite direction of rotation - vice versa, and with a connected to the tank 11 filling port 17 provided.
  • a rotor 1 is rotatably mounted, which has three radially movable, with its outer ends on an eccentric 4 supporting the pump piston 3.
  • This eccentric bearing 4 is executed in the embodiment shown as a rolling bearing.
  • the arranged in the axial direction next to the control pin 2 rotor 1 is pressed against this in a pressureless state with the force of a spring 8.
  • On its side facing away from the end face of the rotor 1 is rotatably supported by means of two deep groove ball bearings 10 about the housing-fixed axis of rotation.
  • each piston chamber has an axially extending and in the control pin 2 facing end side of the rotor 1 opening bore 3a.
  • the control pin 2 is provided with a hardened control plate 2a with two control surfaces (FIG. 2A) formed as control rods 2b, 2c or alternatively with two bores 2b, 2c (FIG. 2B) which abut against the end face of the rotor 1 in such a way that they act during the control Rotation of the rotor 1 with the opening into the end face of the rotor 1 Holes 3a are temporarily aligned.
  • the control pin 2 are also two with their tank facing tank port 5c, 6c with a tank 11 and with its tank 11 remote line connection 5d, 6d with one of the control surfaces 2b, 2c and one of the two ports 13,14 connected Saug Kohltschventile 5.6 provided.
  • the line connection 5d of the one-rear suction check valve 5 is connected to a provided between the housing 12 and the jacket of the control pin 2 disposed therein, circumferential, rear annular channel 5a via an associated transverse bore 5b.
  • the line connection 6d of the -vorderen- Saugrücktschventils 6 is connected to a provided between the housing 12 and the jacket of the control pin 2 disposed therein, circumferential, front annular channel 6a via an associated transverse bore 6b.
  • FIG. 6 shows another embodiment of the suction check valve 5, 6, whose two valve balls on each valve seat seal the through-channel, which extends between the two valve seats and open into the tank via a branch channel which is not further described.
  • the two valve balls are controlled by a valve stem 19 such that upon closure of the one suction check valve 5, i. with resting on the valve seat valve ball, the valve ball of the other suction check valve 6 is lifted by the valve stem 19 from its seat and thus opened, so either only one or the other suction check valve open and the other is closed.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Reciprocating Pumps (AREA)
  • Rotary Pumps (AREA)
  • Details And Applications Of Rotary Liquid Pumps (AREA)
  • Valve Device For Special Equipments (AREA)

Abstract

Hydraulic pump has control stub (2) which exhibits two control surfaces as well as lies in axial direction beside the rotor (1) and with two control surfaces to its front end, each of which is connected with each piston area, parallel to the axis of rotation and axially running and discharge drilling (3a), is provided at the front side of the rotor. Each line connection of the suction non return valve (5,6) is connected to front and back annular channel (5a,6a) circulating between the housing (12) and the casing of the control pin arranged therein. The front annular surface of the annular channel is formed from an area of the control pin with decreasing radius whereas the front annular surface is limiting the annular channel at its adjacent side close to the front surface of the rotor and the rearward annular surface limiting the annular channel at its side remote to the front surface of the rotor is formed from an area of the housing.

Description

Die Erfindung betrifft eine gattungsgemässe Pumpe nach dem Oberbegriff des Hauptanspruchs, nämlich eine hydraulische, vorzugsweise von einem Elektromotor angetriebene Pumpe mit zwei Anschlüssen, von denen bei der einen Drehrichtung der eine als Druck- und der andere als Sauganschluss und -bei entgegengesetzter Drehrichtung- umgekehrt dient, mit einem bezüglich eines Gehäuses drehfesten Steuerzapfen, mit einem in dem Gehäuse angeordneten Tank und mit einem um eine gehäusefeste Drehachse drehbaren Rotor, aufweisend mehrere, vorzugsweise drei radial bewegbare, sich mit ihren äusseren Enden auf einem Exzenterlager abstützende Pumpkolben, deren innere Enden je einen -sich im Volumen ändernden- Kolbenraum abschliessen.The invention relates to a generic pump according to the preamble of the main claim, namely a hydraulic, preferably driven by an electric motor pump with two connections, of which in the one direction of rotation of one as a pressure and the other as a suction port and - opposite direction of rotation - vice versa with a housing with respect to a non-rotatable control pin, with a housing disposed in the housing and rotatable about a rotary axis housing rotatable rotor, comprising a plurality, preferably three radially movable, with its outer ends on an eccentric bearing supporting pump piston whose inner ends each one - close in the volume-changing piston chamber.

Reversierbare Pumpen für verschiedene Einsatzzwecke für kleine Volumenströme (z.B. 0,5 1/min), hohe Drücke (z.B. bis 400 bar) und klar vorgegebene Lebensdauern (z.B. 150 Stunden) sind bekannt und von Interesse. Zu diesen gehören u.a. Pumpen für Anwendungen in der Mobilhydraulik wie z.B. Pumpen für Fahrerhauskippanlagen.Reversible pumps for various applications for small volume flows (eg 0.5 1 / min), high pressures (eg up to 400 bar) and clearly defined lifetimes (eg 150 hours) are known and of interest. These include pumps for applications in mobile hydraulics such as pumps for cab tilting systems.

Heutige Zahnradpumpen sind zwar kostengünstig, erreichen aber das geforderte Druckniveau nicht und sind bei kleinen Volumenströmen nicht reversierbar.Today's gear pumps are inexpensive, but do not reach the required pressure level and are not reversible at low flow rates.

Bekannte ventilgesteuerte Einkolbenpumpen sind auch nicht reversierbar und scheiden aufgrund der Kosten für die Umsteuerung mittels eines Magnetventils und wegen des durch die hohe Pulsation bedingten hohen Geräuschniveaus aus. Sie haben darüber hinaus eine deutlich höhere als vom Markt geforderte Lebensdauer und sind somit zu teuer.Known valve-controlled single-piston pumps are also not reversible and ruled out due to the cost of the reversal by means of a solenoid valve and because of the high pulsation caused by the high noise level. In addition, they have a much higher than required by the market life and are therefore too expensive.

Ventilgesteuerte Mehrkolbenpumpen nach dem heutigen Stand der Technik sind zwar vom Geräuschniveau niedriger, dafür aber -bedingt durch zwei weitere Pumpkolben und je zwei weitere Saug-Druckventile noch teurer in der Fertigung. Für die Umsteuerung wird weiterhin ein Magnetventil benötigt.Although state-of-the-art valve-controlled multi-piston pumps are lower in noise level, they are still more expensive to manufacture due to two additional pump pistons and two additional suction pressure valves. For the reversal, a solenoid valve is still required.

Bekannte gattungsgemässe, schlitzgesteuerte Radialkolbenpumpen weisen einen Rotor mit radialen Pumpkolben und einen feststehenden Steuerzapfen mit zwei radialen Steuerschlitzen auf. Der Rotor ist drehbar auf dem Steuerzapfen gelagert. Die Lagerstelle muss -neben dem Abfangen der Pumpkräftean der Verbindungsstelle zwischen dem Rotor und dem Steuerzapfen Öldichtheit sicherstellen. Trotz des hohen Fertigungsaufwandes ist jedoch eine Leckage konstruktionsbedingt unvermeidbar, die sich auf den Wirkungsgrad negativ auswirkt. Auch besteht die Gefahr, dass aufgrund unterschiedlicher Gleitpaarungen bei starken Temperaturschwankungen der Rotor auf dem Steuerzapfen klemmt. Durch ständigen verschleiss im Laufe des Betriebs kann die Leckage grösser werden, was sich negativ auf den Wirkungsgrad auswirkt und in hohem Masse unerwünscht ist.Known generic, slot-controlled radial piston pumps have a rotor with radial pump piston and a fixed control pin with two radial control slots. The rotor is rotatably mounted on the control pin. The bearing must also ensure the interception of the pumping forces at the joint between the rotor and the oil pressure control spigot. Despite the high production costs, however, a leakage is inevitable due to the design, which has a negative effect on the efficiency. There is also the danger that, due to different sliding pairings, the rotor will jam on the control pin in the event of severe temperature fluctuations. Constant wear in the course of operation can increase the leakage, which has a negative effect on the efficiency and is highly undesirable.

Der Erfindung liegt die Aufgabe zugrunde, eine gattungsgemässe Pumpe nach dem Oberbegriff des Hauptanspruchs einfacher in der Herstellung und Montage und damit kostengünstiger so weiterzubilden, dass sie im Betrieb trotz eines Verschleisses leckagearm bleibt.The invention is based on the object Generic pump according to the preamble of the main claim easier in the production and assembly and thus cheaper educate so that it remains leaking poor in operation despite wear.

Diese Aufgabe wird bei einer gattungsgemässen Pumpe nach dem Oberbegriff des Hauptanspruchs erfindungsgemäss durch dessen kennzeichnende Merkmale, also dadurch gelöst, dass der Steuerzapfen zwei Steuerflächen aufweist sowie in axialer Richtung neben dem Rotor und mit den zwei Steuerflächen an dessen einer Stirnseite anliegt, dass je eine mit jedem Kolbenraum verbundene, -parallel zu der Drehachse- axial verlaufende und an der Stirnseite des Rotors mündende Bohrung vorgesehen ist, dass in dem Steuerzapfen ein mit seinem dem Tank zugewandten Tankanschluss mit einem Tank und mit seinem dem Tank abgewandten Leitungsanschluss nur sowohl mit einer der Steuerflächen als auch mit einem der beiden Anschlüsse verbindbares Saugrückschlagventil vorgesehenen ist, währenddessen ein weiteres Saugrückschlagventil mit seinem dem Tank zugewandten Tankanschluss mit dem Tank und mit seinem dem Tank abgewandten Leitungsanschluss nur sowohl mit der anderen der Steuerflächen als auch mit dem anderen der beiden Anschlüsse verbunden ist, und dass jeder Leitungsanschluss der Saugrückschlagventile an je einen zwischen dem Gehäuse und dem Mantel des darin angeordneten Steuerzapfens vorgesehenen, umlaufenden, vorderen bzw. hinteren Ringkanal angeschlossen ist, insbesondere wenn dessen den Ringkanal an seiner bezüglich der Stirnfläche des Rotors nächst benachbarten Seite begrenzende vordere Ringfläche von einem Bereich des Steuerzapfens mit abnehmendem Radius und/oder wenn dessen den Ringkanal an seiner bezüglich der Stirnfläche des Rotors entfernten Seite begrenzende hintere Ringfläche von einem Bereich des Gehäuses gebildet ist.This object is achieved in a generic pump according to the preamble of the main claim according to the invention by its characterizing features, that the control pin has two control surfaces and in the axial direction next to the rotor and with the two control surfaces at one end face abuts that one each with each bore associated, parallel to the axis of rotation axially extending and opening at the end of the rotor bore is provided that in the control pin with its tank facing the tank port to a tank and with its side facing away from the tank line connection only with one of the control surfaces as well as provided with one of the two ports connectable suction check valve, while another Saugrückschlagventil with its tank facing the tank connection to the tank and with its side facing away from the tank line connection only with both the other of the control surfaces and with the other Ren of the two terminals is connected, and that each line connection of the Saugrückschlagventile is connected to a respective provided between the housing and the jacket of the control pin disposed therein circumferential, front or rear annular channel, in particular if the annular channel at its relative to the end face of the rotor next adjacent side limiting front annular surface of a region of the control pin with decreasing radius and / or if the annular channel at its relative to the end face of the rotor remote side limiting rear annular surface is formed by a portion of the housing.

Je nach Drehrichtung des z.B. von dem Elektromotor angetriebenen Rotors wird also nach Lehre der Erfindung während der ersten halben Umdrehung des Rotors in der einen Drehrichtung von den einzelnen Pumpkolben aus dem Tank durch die in der Stirnseite des Rotors mündende Bohrung immer dann, wenn diese eine der zwei Steuerflächen überstreicht, Hydraulikflüssigkeit, z.B. Öl, über das eine Saugrückschlagventil oder den einen Ringkanal bei gleichzeitig geschlossenem anderen Saugrückschlagventil angesaugt und während der nächsten halben Umdrehung in den anderen Ringkanal gefördert. Ändert sich die Drehrichtung, wird das Öl während der ersten halben Umdrehung über das andere Saugrückschlagventiloder den anderen Ringkanal bei gleichzeitig geschlossenem einen Saugrückschlagventil angesaugt und während der nächsten halben Umdrehung in den einen Ringkanal gefördert. Die Ringkanäle sind dabei so ausgestaltet, dass sich durch die hydraulisch wirksame, der Stirnfläche des Rotors zugewandte sowie nächst benachbarte, von dem Steuerzapfen gebildete vordere Ringfläche mit abnehmendem Radius und die von dem Gehäuse selbst gebildete hintere Ringfläche bei Druckbeaufschlagung des Ringkanals eine in Richtung des Rotors wirkende resultierende Kraft ergibt.Depending on the direction of rotation of e.g. From the electric motor driven rotor is therefore according to the teaching of the invention during the first half revolution of the rotor in the one direction of rotation of the individual pump piston from the tank through the opening in the end face of the rotor bore, whenever it covers one of the two control surfaces, hydraulic fluid , eg Oil, sucked through the one suction check valve or the one ring channel while the other closed suction check valve and promoted during the next half turn in the other ring channel. If the direction of rotation changes, the oil is sucked in during the first half revolution via the other suction check valve or the other annular channel with a suction check valve closed at the same time and conveyed into the one annular channel during the next half revolution. The annular channels are configured such that by the hydraulically effective, the end face of the rotor facing and next adjacent, formed by the control pin front annular surface with decreasing radius and the housing itself formed by the rear annular surface upon pressurization of the annular channel in the direction of the rotor acting resulting force results.

Die aus dem in dem hydraulischen System herrschenden Betriebsdruck resultierende hydraulische Kraft neigt zunächst zum Auseinanderdrücken von Rotor und Steuerzapfen. Dieser Betriebsdruck wird aber drehrichtungsabhängig auf den jeweiligen Ringkanal rückgekoppelt und erzeugt auf der einen Ringfläche des Steuerzapfens die vorstehend erwähnte resulierende Kraft, wodurch erfindungsgemäss der Steuerzapfen und der Rotor über den gesamten Betriebsdruckbereich mit einem definiert einstellbaren Kraftüberschuss aneinandergepresst werden. Die Umsteuerung des Ansaugens und Pumpens der Hydraulikflüssigkeit bei Änderung der Drehrichtung erfolgt dabei selbsttätig durch die erfindungsgemässe Anordnung der Saugrückschlagventile in dem Steuerzapfen.The hydraulic force resulting from the operating pressure prevailing in the hydraulic system initially tends to push rotor and control pin apart. However, this operating pressure is fed back depending on the direction of rotation on the respective annular channel and generates on the one annular surface of the control pin, the above-mentioned resulting force, whereby according to the invention Control pin and the rotor over the entire operating pressure range with a defined adjustable excess force are pressed together. The reversal of the suction and pumping of the hydraulic fluid when changing the direction of rotation takes place automatically by the inventive arrangement of Saugrückschlagventile in the control pin.

Das erfindungsgemässe Prinzip liegt also in der axialen Anordnung des Steuerzapfens an der Stirnseite des Rotors und dem von dem Betriebsdruck im hydraulischen System abhängigen Aneinanderpressen dieser beiden Teile. Hierdurch ist die Verbindungsstelle dieser Teile nicht nur im Betrieb vergleichsweise dicht und damit leckagearm; auch bei Verschleiss (Abrieb) der Stirnfläche des Rotors erfolgt die erforderliche Nachstellung selbsttätig und automatisch. Insgesamt wird mit der Erfindung eine einfacher in der Herstellung und Montage und damit kostengünstigere Pumpe bereitgestellt, die auch im Betrieb trotz eines Verschleisses äusserst leckagearm ist.The inventive principle thus lies in the axial arrangement of the control pin on the end face of the rotor and the pressing of these two parts dependent on the operating pressure in the hydraulic system. As a result, the connection point of these parts is not only relatively tight in operation and thus low in leakage; even with wear (abrasion) of the end face of the rotor, the required adjustment takes place automatically and automatically. Overall, the invention provides a simpler in the production and assembly and thus more cost-effective pump, which is extremely low leakage even during operation despite wear.

Zweckmässigerweise sind der der Stirnfläche des Rotors nächst benachbarte vordere Ringkanal sowie der der Stirnfläche des Rotors entferntere hintere Ringkanal über je eine Querbohrung mit dem zugehörigen Leitungsanschluss der Saugrückschlagventile verbunden, wodurch sich eine besonders einfache Herstellung ergibt.Advantageously, the front face of the rotor adjacent the front annular channel and the end face of the rotor remote rear ring channel are connected via a respective transverse bore with the associated line connection of Saugrückschlagventile, resulting in a particularly simple production.

Um eine unerwünschte Leckage aus den Ringkanälen des Steuerzapfens zu verhindern, weist dieser einen kreiszylinderförmigen Mantel auf und ist der hintere sowie vordere Ringkanal von zwei umlaufenden Dichtungen benachbart.In order to prevent unwanted leakage from the annular channels of the control pin, this has a circular cylindrical shell and is the rear and front annular channel of two circumferential seals adjacent.

Die durch den im hydraulischen System herrschenden Betriebsdruck entstehenden axialen und radialen Kräfte werden vorteilhafterweise dadurch kompensiert, dass der Rotor auf seiner der Stirnseite abgewandten Seite mittels zumindest eines als Rillenkugellager ausgebildeten Axial- und/oder Radiallagers drehbar gelagert ist.The resulting by the pressure prevailing in the hydraulic system operating pressure axial and radial forces are advantageously compensated by the fact that the rotor is rotatably mounted on its side facing away from the end face by means of at least one designed as a deep groove ball bearing axial and / or radial bearing.

Weitere zweckmässige Ausgestaltungen sowie Weiterbildungen sind in den restlichen Unteransprüchen gekennzeichnet.Further expedient refinements and further developments are characterized in the remaining subclaims.

Ein Ausführungsbeispiel der Erfindung wird nachfolgend unter Bezugnahme auf die Zeichnung erläutert. In dieser zeigt:

Figur 1
eine erste Ausführungsform Pumpe gemäss der Erfindung, im schematischen Querschnitt;
Figur 2
einen Schnitt II-II nach Figur 1;
Figur 3
einen Schnitt III-III nach Figur 1;
Figur 4
einen Schnitt IV-IV nach Figur 1;
Figur 5
eine Einzelheit in Fig. 1, im grösserem Massstab und
Figur 6
eine alternative Ausführungsform der Pumpe.
An embodiment of the invention will be explained below with reference to the drawing. In this shows:
FIG. 1
a first embodiment pump according to the invention, in schematic cross section;
FIG. 2
a section II-II of Figure 1;
FIG. 3
a section III-III of Figure 1;
FIG. 4
a section IV-IV of Figure 1;
FIG. 5
a detail in Fig. 1, on a larger scale and
FIG. 6
an alternative embodiment of the pump.

Die von der eigentlichen hydraulischen, reversierbaren Pumpe 1,2,12 und dem an diese an deren einer Seite angeflanschten und diese antreibenden Elektromotor 9 gebildete Pumpeinheit weist, wie in Figur 1 gezeigt, ein Gehäuse 12 auf, an dessen anderer Seite ein Tank 11 für die Hydraulikflüssigkeit befestigt ist, die vorzugsweise von Öl gebildet ist. Die Pumpe ist mit zwei Anschlüssen 13,14, von denen bei der einen Drehrichtung der eine als Druck- für die Zulaufleitung und der andere als Leitungsanschluss für die Rücklaufleitung und -bei entgegengesetzter Drehrichtung- umgekehrt dient, und mit einem mit dem Tank 11 verbundenen Füllanschluss 17 versehen.The pump unit formed by the actual hydraulic reversible pump 1, 2, 12 and the electric motor 9 flanged to it on one side and driving the latter has, as shown in FIG. 1, a housing 12, on the other side of which a tank 11 for the Hydraulic fluid is attached, which is preferably formed of oil. The pump is provided with two ports 13,14, of which in one direction of rotation one serves as a pressure for the supply line and the other as a line connection for the return line and -in the opposite direction of rotation - vice versa, and with a connected to the tank 11 filling port 17 provided.

In dem Gehäuse 12 ist ein bezüglich desselben drehfester Steuerzapfen 2 mit einem kreiszylindrischen Mantel vorgesehen. Um eine gehäusefeste Drehachse ist ein Rotor 1 drehbar gelagert, der drei radial bewegbare, sich mit ihren äusseren Enden auf einem Exzenterlager 4 abstützende Pumpkolben 3 aufweist. Dieses Exzenterlager 4 ist beim wiedergegebenen Ausführungsbeispiel als Wälzlager ausgeführt. Der in axialer Richtung neben dem Steuerzapfen 2 angeordnete Rotor 1 ist an diesen in drucklosem Zustand mit der Kraft einer Feder 8 angedrückt. Auf seiner der Stirnseite abgewandten Seite ist der Rotor 1 mittels zweier Rillenkugellager 10 um die gehäusefeste Drehachse drehbar gelagert.In the housing 12 with respect to the same rotationally fixed control pin 2 is provided with a circular cylindrical jacket. To a housing-fixed axis of rotation, a rotor 1 is rotatably mounted, which has three radially movable, with its outer ends on an eccentric 4 supporting the pump piston 3. This eccentric bearing 4 is executed in the embodiment shown as a rolling bearing. The arranged in the axial direction next to the control pin 2 rotor 1 is pressed against this in a pressureless state with the force of a spring 8. On its side facing away from the end face of the rotor 1 is rotatably supported by means of two deep groove ball bearings 10 about the housing-fixed axis of rotation.

Wie in Figur 3 gezeigt, schliessen die inneren Enden der Pumpkolben 3 je einen -sich im Volumen ändernden-Kolbenraum ab. Jeder Kolbenraum weist eine axial verlaufende und in der dem Steuerzapfen 2 zugewandten Stirnseite des Rotors 1 mündende Bohrung 3a auf.As shown in FIG. 3, the inner ends of the pumping pistons 3 each terminate in a volume-changing piston space. Each piston chamber has an axially extending and in the control pin 2 facing end side of the rotor 1 opening bore 3a.

Der Steuerzapfen 2 ist mit einem gehärteten Steuerspiegel 2a mit zwei als Steuernieren 2b,2c ausgebildeten Steuerflächen (Figur 2A) oder alternativ mit zwei Bohrungen 2b,2c (Figur 2B) versehen, die an der Stirnseite des Rotors 1 so anliegen, dass sie während der Drehung des Rotors 1 mit den in die Stirnseite des Rotors 1 mündenden Bohrungen 3a zeitweise fluchten. In dem Steuerzapfen 2 sind ferner zwei mit ihrem dem Tank zugewandten Tankanschluss 5c,6c mit einem Tank 11 und mit ihrem dem Tank 11 abgewandten Leitungsanschluss 5d,6d mit je einer der Steuerflächen 2b,2c und je einem der zwei Anschlüsse 13,14 verbundene Saugrückschlagventile 5,6 vorgesehenen. Für den Anschluss 13 ergibt sich dies aus Figur 4, der über eine Stichbohrung 18 mit dem vorderen Ringkanal 6a verbunden ist. Entsprechend ist der Anschluss 14 über eine nicht gezeigte Stichbohrung an den hinteren Ringkanal 5a angeschlossen. Die Steuerflächen 2b, 2c sind über je eines der Saugrückschlagventile 5,6 mit dem Tank 11 verbunden. Im drucklosen Zustand ist die Stirnfläche des Rotors 1 mit der als Federelement ausgebildeten Feder 8 öldicht an den Steuerspiegel 2a des Steuerzapfens 2 angepresst.The control pin 2 is provided with a hardened control plate 2a with two control surfaces (FIG. 2A) formed as control rods 2b, 2c or alternatively with two bores 2b, 2c (FIG. 2B) which abut against the end face of the rotor 1 in such a way that they act during the control Rotation of the rotor 1 with the opening into the end face of the rotor 1 Holes 3a are temporarily aligned. In the control pin 2 are also two with their tank facing tank port 5c, 6c with a tank 11 and with its tank 11 remote line connection 5d, 6d with one of the control surfaces 2b, 2c and one of the two ports 13,14 connected Saugrückschlagventile 5.6 provided. For the connection 13, this results from Figure 4, which is connected via a tap hole 18 with the front annular channel 6a. Accordingly, the terminal 14 is connected via a tap hole, not shown, to the rear annular channel 5a. The control surfaces 2b, 2c are each connected to the tank 11 via one of the suction check valves 5, 6. In the pressureless state, the end face of the rotor 1 is pressed with the spring 8 designed as a spring element oil-tight to the control mirror 2 a of the control pin 2.

Der Leitungsanschluss 5d des einen -hinteren-Saugrückschlagventils 5 ist an einen zwischen dem Gehäuse 12 und dem Mantel des darin angeordneten Steuerzapfens 2 vorgesehenen, umlaufenden, hinteren Ringkanal 5a über eine zugehörige Querbohrung 5b angeschlossen. Ebenso ist der Leitungsanschluss 6d des -vorderen- Saugrückschlagventils 6 ist an einen zwischen dem Gehäuse 12 und dem Mantel des darin angeordneten Steuerzapfens 2 vorgesehenen, umlaufenden, vorderen Ringkanal 6a über eine zugehörige Querbohrung 6b angeschlossen. Wie Figur 5 zeigt, ist dessen den vorderen Ringkanal 6a an seiner bezüglich der Stirnfläche des Rotors 1 nächst benachbarten Seite begrenzende vordere Ringfläche 15 von einem Bereich des Steuerzapfens 2 mit abnehmendem Radius in Form eines Absatzes gebildet, wohingegen die den vordere Ringkanal 6a an seiner bezüglich der Stirnfläche des Rotors 1 entfernten Seite begrenzende hintere Ringfläche 16 von einem Bereich des Gehäuses 12 gebildet ist. Ausserdem ist benachbart zu dem hinteren (5a) sowie dem vorderen Ringkanal 6a auf jeder Seite eine umlaufende Dichtung 9a,9b,9c angeordnet.The line connection 5d of the one-rear suction check valve 5 is connected to a provided between the housing 12 and the jacket of the control pin 2 disposed therein, circumferential, rear annular channel 5a via an associated transverse bore 5b. Likewise, the line connection 6d of the -vorderen- Saugrückschlagventils 6 is connected to a provided between the housing 12 and the jacket of the control pin 2 disposed therein, circumferential, front annular channel 6a via an associated transverse bore 6b. As FIG. 5 shows, its front annular surface 15 delimiting the front annular channel 6a on its side nearest the end face of the rotor 1 is formed by a region of the control pin 2 with decreasing radius in the form of a shoulder, whereas that of the front annular channel 6a on its relative the end face of the rotor 1 remote side limiting rear annular surface 16 is formed by a portion of the housing 12. It is also adjacent to the rear (5a) and the front annular channel 6a on each side a circumferential seal 9a, 9b, 9c arranged.

Je nach Drehrichtung des Elektromotors 9 wird während der ersten halben Umdrehung Öl aus dem Tank 11, von den einzelnen Pumpkolben 3 durch die Bohrung 3a z.B. über das eine Saugrückschlagventil 5 oder den einen hinteren Ringkanal 5a angesaugt und während der nächsten halben Umdrehung in den anderen vorderen Ringkanal 6a gefördert. Das andere Saugrückschlagventil 6 ist in diesem Fall geschlossen, so dass es aus dem einen als Druckanschluss dienenden Anschluss 13 (Figur 4) herausgepumpt wird. Ändert sich die Drehrichtung, wird Öl über das andere Saugrückschlagventil 6 oder den anderen vorderen Ringkanal 6a angesaugt und in den hinteren Ringkanal 5a gefördert. In diesem Fall ist das erstgenannte eine Saugrückschlagventil 5 geschlossen.Depending on the direction of rotation of the electric motor 9, during the first half turn, oil is removed from the tank 11, from the individual pumping pistons 3 through the bore 3a, e.g. sucked through the one suction check valve 5 or the one rear annular channel 5a and promoted during the next half turn in the other front annular channel 6a. The other suction check valve 6 is closed in this case, so that it is pumped out of the one serving as a pressure connection port 13 (Figure 4). If the direction of rotation changes, oil is sucked in via the other suction check valve 6 or the other front annular channel 6a and conveyed into the rear annular channel 5a. In this case, the former one suction check valve 5 is closed.

In Figur 6 ist eine andere Ausführungsform der Saugrückschlagventils 5,6 dagestellt, deren beide Ventilkugeln auf je einem Ventilsitz den Durchgangskanal abdichten, der sich zwischen den beiden Ventilsitzen erstreckt und in den Tank über einen -nicht näher bezeichneten- Stichkanal münden. Die beiden Ventilkugeln sind so von einem Ventilstössel 19 gesteuert, dass beim Schliessen des einen Saugrückschlagventils 5, d.h. mit auf dem Ventilsitz aufliegender Ventilkugel die Ventilkugel des anderen Saugrückschlagventils 6 durch den Ventilstössel 19 von seinem Sitz abgehoben und damit geöffnet wird, also entweder nur das eine oder aber das andrere Saugrückschlagventil geöffnet und das jeweils andere geschlossen ist.FIG. 6 shows another embodiment of the suction check valve 5, 6, whose two valve balls on each valve seat seal the through-channel, which extends between the two valve seats and open into the tank via a branch channel which is not further described. The two valve balls are controlled by a valve stem 19 such that upon closure of the one suction check valve 5, i. with resting on the valve seat valve ball, the valve ball of the other suction check valve 6 is lifted by the valve stem 19 from its seat and thus opened, so either only one or the other suction check valve open and the other is closed.

Die aus dem Systemdruck resultierende hydraulische Kraft, die den Rotor 1 und den Steuerzapfen 2 an dem Steuerspiegel 2a auseinanderdrückt wird durch Rückkoppeln des Systemdrucks drehrichtungsabhängig auf der einen, dem Steuerspiegel 2a und der Stirnfläche des Rotors nächst benachbarten Ringfläche des einen hinteren (5a) oder des anderen vorderen Ringkanals 6a kompensiert. Dadurch werden der Steuerzapfen 2 und der Rotor 1 über den gesamten Betriebsdruckbereich mit einem definierbaren Kraftüberschuss aneinandergepresst, so dass deren Verbindungsstelle im Betrieb leckagearm und damit vergleichsweise dicht ist. Bei Verschleiss (Abrieb) der Stirnfläche des Rotors erfolgt automatisch die erforderliche Nachstellung.The resulting from the system pressure hydraulic Force that presses apart the rotor 1 and the control pin 2 on the control plate 2a by feedback of the system pressure depending on the direction of rotation on the one, the control mirror 2a and the end face of the rotor next adjacent annular surface of a rear (5a) or the other front annular channel 6a compensated. As a result, the control pin 2 and the rotor 1 are pressed against each other over the entire operating pressure range with a definable excess force, so that their connection point in operation low leakage and thus is relatively dense. When wear (abrasion) of the end face of the rotor is automatically the required adjustment.

Die durch den Systemdruck entstehenden axialen und radialen Kräfte werden über die beiden Rillenkugellager 10 aufgenommen und über den Sicherungsring 7 im Gehäuse 12 abgefangen.The resulting by the system pressure axial and radial forces are absorbed by the two deep groove ball bearings 10 and intercepted via the retaining ring 7 in the housing 12.

Claims (16)

1. Hydraulische, vorzugsweise von einem Elektromotor (9) angetriebene Pumpe mit zwei Anschlüssen (13,14), von denen bei der einen Drehrichtung der eine als Druck- und der andere als Sauganschluss und -bei entgegengesetzter Drehrichtung- umgekehrt dient, mit einem bezüglich eines Gehäuses (12) drehfesten Steuerzapfen (2), mit einem in dem Gehäuse angeordneten Tank (11) und mit einem um eine gehäusefeste Drehachse drehbaren Rotor (1), aufweisend mehrere, vorzugsweise drei radial bewegbare, sich mit ihren äusseren Enden auf einem Exzenterlager (4) abstützende Pumpkolben (3), deren innere Enden je einen -sich im Volumen ändernden-Kolbenraum abschliessen, dadurch gekennzeichnet, - dass der Steuerzapfen (2) zwei Steuerflächen (2b,2c) aufweist sowie in axialer Richtung neben dem Rotor (1) und mit den zwei Steuerflächen (2b,2c) an dessen einer Stirnseite anliegt, - dass je eine mit jedem Kolbenraum verbundene, -parallel zu der Drehachse- axial verlaufende und an der Stirnseite des Rotors (1) mündende Bohrung (3a) vorgesehen ist, - dass in dem Steuerzapfen (2) ein mit seinem dem Tank zugewandten Tankanschluss (5c) mit einem Tank (11) und und mit seinem dem Tank (11) abgewandten Leitungsanschluss (5d) sowohl mit einer der Steuerflächen (2b,2c) als auch mit einem der beiden Anschlüsse (13,14) verbindbares Saugrückschlagventil (5) sowie ein mit seinem dem Tank zugewandten Tankanschluss (6c) mit dem Tank (11) und und mit seinem dem Tank (11) abgewandten Leitungsanschluss (6d) sowohl mit der anderen der Steuerflächen (2b,2c) als auch mit dem anderen der beiden Anschlüsse (13,14) verbindbares weiteres Saugrückschlagventil (6) vorgesehenen ist, - und dass jeder Leitungsanschluss der Saugrückschlagventile (5,6) an je einen zwischen dem Gehäuse (12) und dem Mantel des darin angeordneten Steuerzapfens (2) vorgesehenen, umlaufenden, vorderen bzw. hinteren Ringkanal (5a,6a) angeschlossen ist, dessen den Ringkanal an seiner bezüglich der Stirnfläche des Rotors (1) nächst benachbarten Seite begrenzende vordere Ringfläche (15) von einem Bereich des Steuerzapfens (2) mit abnehmendem Radius und dessen den Ringkanal an seiner bezüglich der Stirnfläche des Rotors (1) entfernten Seite begrenzende hintere Ringfläche (16) von einem Bereich des Gehäuses (12) gebildet ist. 1. Hydraulic, preferably by an electric motor (9) driven pump with two terminals (13,14), one of which in the one direction of rotation as a pressure and the other as a suction port and -in opposite direction of rotation - vice versa, with respect a housing (12) non-rotatable control pin (2), with a housing disposed in the tank (11) and with a housing-fixed rotation axis rotatable rotor (1), comprising a plurality, preferably three radially movable, with its outer ends on an eccentric bearing (4) supporting pump pistons (3), whose inner ends each terminate in a volume-changing piston space, characterized - That the control pin (2) has two control surfaces (2b, 2c) and in the axial direction next to the rotor (1) and with the two control surfaces (2b, 2c) rests on one end face, - That each one connected to each piston chamber, -parallel to the axis of rotation- axially extending and on the front side of the rotor (1) opening bore (3a) is provided, - That in the control pin (2) with its tank-facing tank connection (5 c) with a tank (11) and and with its the tank (11) facing away from the line connection (5d) with both the control surfaces (2b, 2c) and one of the two terminals (13,14) connectable suction check valve (5) and one with his the tank facing tank connection (6c) with the tank (11) and with its the tank (11) facing away from the line connection (6d) both with the other of the control surfaces (2b, 2c) and with the other of the two terminals (13,14) connectable further suction check valve (6) is provided, - And that each line connection of the Saugrückschlagventile (5,6) to each one between the housing (12) and the jacket of the control pin arranged therein (2) provided, circumferential, front or rear annular channel (5a, 6a) is connected, whose Ring channel at its relative to the end face of the rotor (1) next adjacent side limiting front annular surface (15) of a region of the control pin (2) with decreasing radius and the annular channel at its relative to the end face of the rotor (1) remote from the rear end annular surface (16) is formed by a portion of the housing (12). 2. Pumpe nach Anspruch 1, dadurch gekennzeichnet, dass der der Stirnfläche des Rotors (1) nächst benachbarte vordere Ringkanal (6a) sowie der der Stirnfläche des Rotors (1) entferntere hintere Ringkanal (5a) über je eine Querbohrung (5b,6b) mit dem zugehörigen Leitungsanschluss (5d,6d) der Saugrückschlagventile (5,6) verbunden sind. 2. Pump according to claim 1, characterized in that the end face of the rotor (1) next adjacent front annular channel (6a) and the end face of the rotor (1) remote rear annular channel (5a) via a respective transverse bore (5b, 6b) with the associated line connection (5d, 6d) of the suction check valves (5,6) are connected. 3. Pumpe nach Anspruch 1 oder 2, dadurch gekennzeichnet, dass der Steuerzapfen (2) einen kreiszylinderförmigen Mantel aufweist und der hintere sowie vordere Ringkanal (5a,6a) auf jeder Seite von einer umlaufenden Dichtung (9a,9b,9c) benachbart ist. 3. Pump according to claim 1 or 2, characterized in that the control pin (2) has a circular cylindrical shell and the rear and front annular channel (5a, 6a) on each side of a circumferential seal (9a, 9b, 9c) is adjacent. 4. Pumpe nach einem der Ansprüche 1 bis 3, dadurch gekennzeichnet, dass der Steuerzapfen als Steuerflächen (2b,2c) zwei Steuernieren aufweist. 4. Pump according to one of claims 1 to 3, characterized in that the control pin as control surfaces (2b, 2c) has two control kidneys. 5. Pumpe nach einem der Ansprüche 1 bis 3, dadurch gekennzeichnet, dass der Steuerzapfen als Steuerflächen (2b,2c) zwei Steuerbohrungen aufweist. 5. Pump according to one of claims 1 to 3, characterized in that the control pin as control surfaces (2 b, 2 c) has two control bores. 6. Pumpe nach einem der Ansprüche 1 bis 5, dadurch gekennzeichnet, dass der Steuerzapfen (2) einen Steuerspiegel (2a) aufweist und dass die Steuerflächen (2b,2c) des Steuerzapfens (2) innerhalb des Steuerspiegels (2a) angeordnet sind. 6. Pump according to one of claims 1 to 5, characterized in that the control pin (2) has a control mirror (2 a) and that the control surfaces (2 b, 2 c) of the control pin (2) within the control mirror (2 a) are arranged. 7. Pumpe nach Anspruch 6, dadurch gekennzeichnet, dass der Rotor (1) einen Steuerspiegel aufweist und dieser eine andere Härte als der Steuerspiegel (2a) des Steuerzapfens (2) aufweist. 7. Pump according to claim 6, characterized in that the rotor (1) has a control plate and this has a different hardness than the control mirror (2a) of the control pin (2). 8. Pumpe nach einem der Ansprüche 1 bis 7, dadurch gekennzeichnet, dass der in axialer Richtung neben dem Steuerzapfen (2) angeordnete Rotor (1) und der Steuerzapfen (2) im drucklosen Zustand mit der Kraft einer Feder (8) aneinander gedrückt sind. 8. Pump according to one of claims 1 to 7, characterized in that in the axial direction adjacent to the control pin (2) arranged rotor (1) and the control pin (2) in the unpressurized state with the force of a spring (8) are pressed together , 9. Pumpe nach einem der Ansprüche 1 bis 8,dadurch gekennzeichnet, dass das Exzenterlager (4) als Gleit- oder Wälzlager ausgebildet ist. 9. Pump according to one of claims 1 to 8, characterized in that the eccentric bearing (4) is designed as a sliding or rolling bearing. 10. Pumpe nach einem der Ansprüche 1 bis 9, dadurch gekennzeichnet, dass der Rotor (1) auf seiner der Stirnseite abgewandten Seite mittels zumindest eines Axiallagers (10) drehbar gelagert ist. 10. Pump according to one of claims 1 to 9, characterized in that the rotor (1) on its side facing away from the end face by means of at least one thrust bearing (10) is rotatably mounted. 11. Pumpe nach einem der Ansprüche 1 bis 9, dadurch gekennzeichnet, dass der Rotor (1) auf seiner der Stirnseite abgewandten Seite mittels zumindest eines Radiallagers (10) drehbar gelagert ist. 11. Pump according to one of claims 1 to 9, characterized in that the rotor (1) on its side facing away from the end face by means of at least one radial bearing (10) is rotatably mounted. 12. Pumpe nach Anspruch 10 oder 11, dadurch gekennzeichnet, dass das Axiallager und/oder das Radiallager als Rillenkugellager (10) ausgebildet ist. 12. A pump according to claim 10 or 11, characterized in that the axial bearing and / or the radial bearing is designed as a deep groove ball bearing (10). 13. Pumpe nach Anspruch 1, dadurch gekennzeichnet, dass sie als reversierbare Pumpe ausgebildet ist. 13. A pump according to claim 1, characterized in that it is designed as a reversible pump. 15. Pumpe nach Anspruch 1, dadurch gekennzeichnet, dass der Tank (11) sich an den Steuerzapfen (2) auf dessen dem Rotor (1) abgewandten Seite anschliesst. 15. A pump according to claim 1, characterized in that the tank (11) adjoins the control pin (2) on its side facing away from the rotor (1). 15. Pumpe nach Anspruch 1, dadurch gekennzeichnet, dass die in dem Steuerzapfen (2) angeordneten beiden Saugrückschlagventile (5,6) je eine auf einem Ventilsitz angeordnete, den jeweiligen, sich zwischen den beiden Ventilsitzen erstreckenden und in den Tank mündenden Durchgangskanal abdichtende Ventilkugel aufweisen, und dass die beiden Ventilkugeln so von einem Ventilstössel (19) gesteuert sind, dass beim Schliessen des einen Saugrückschlagventils (5) mit auf dem Ventilsitz aufliegender Ventilkugel jene Ventilkugel des anderen Saugrückschlagventils (6) durch den Ventilstössel (19) von seinem Sitz abgehoben und damit geöffnet wird. 15. A pump according to claim 1, characterized in that in the control pin (2) arranged two Saugrückschlagventile (5,6) each arranged on a valve seat, the respective, between the two valve seats having extending and opening into the tank passage sealing valve ball, and that the two valve balls are controlled by a valve stem (19) that upon closing of a Saugrückschlagventils (5) with resting on the valve seat valve ball that valve ball of the other Saugrückschlagventils (6) the valve stem (19) is lifted from its seat and thus opened. 16. Pumpe nach Anspruch 15, dadurch gekennzeichnet, dass der sich zwischen den beiden Ventilsitzen erstreckende Durchgangskanal über einen Stichkanal in den Tank (11) mündet. 16. A pump according to claim 15, characterized in that extending between the two valve seats through-channel via a branch channel into the tank (11) opens.
EP06023728A 2005-11-15 2006-11-15 Hydraulic pump Not-in-force EP1785622B1 (en)

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EP1785622B1 (en) 2008-01-23
DE102005054873B4 (en) 2007-08-09
ATE384870T1 (en) 2008-02-15
DE102005054873A1 (en) 2007-05-16

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