EP2253844A1 - Device for transporting a fluid in a hydraulic circuit - Google Patents

Device for transporting a fluid in a hydraulic circuit Download PDF

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Publication number
EP2253844A1
EP2253844A1 EP09006795A EP09006795A EP2253844A1 EP 2253844 A1 EP2253844 A1 EP 2253844A1 EP 09006795 A EP09006795 A EP 09006795A EP 09006795 A EP09006795 A EP 09006795A EP 2253844 A1 EP2253844 A1 EP 2253844A1
Authority
EP
European Patent Office
Prior art keywords
hydraulic pump
drive motor
clutch
hydraulic
magnetic coupling
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.)
Withdrawn
Application number
EP09006795A
Other languages
German (de)
French (fr)
Inventor
Thomas Butzki
Ralf Hartmann
Ulrich Stefan König
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.)
Walter Stauffenberg GmbH and Co KG
Original Assignee
Walter Stauffenberg GmbH and Co KG
Priority date (The priority date 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 date listed.)
Filing date
Publication date
Application filed by Walter Stauffenberg GmbH and Co KG filed Critical Walter Stauffenberg GmbH and Co KG
Priority to EP09006795A priority Critical patent/EP2253844A1/en
Priority to PCT/EP2010/003030 priority patent/WO2010133339A1/en
Priority to CN2010800329659A priority patent/CN102549263A/en
Publication of EP2253844A1 publication Critical patent/EP2253844A1/en
Withdrawn legal-status Critical Current

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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
    • F04B17/00—Pumps characterised by combination with, or adaptation to, specific driving engines or motors
    • F04B17/03—Pumps characterised by combination with, or adaptation to, specific driving engines or motors driven by electric motors
    • 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
    • F04B17/00—Pumps characterised by combination with, or adaptation to, specific driving engines or motors
    • 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
    • F04B49/00—Control, e.g. of pump delivery, or pump pressure of, or safety measures for, machines, pumps, or pumping installations, not otherwise provided for, or of interest apart from, groups F04B1/00 - F04B47/00
    • F04B49/02—Stopping, starting, unloading or idling control
    • 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
    • F04B9/00—Piston machines or pumps characterised by the driving or driven means to or from their working members
    • F04B9/02—Piston machines or pumps characterised by the driving or driven means to or from their working members the means being mechanical
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C14/00—Control of, monitoring of, or safety arrangements for, machines, pumps or pumping installations
    • F04C14/06—Control of, monitoring of, or safety arrangements for, machines, pumps or pumping installations specially adapted for stopping, starting, idling or no-load operation
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C15/00—Component parts, details or accessories of machines, pumps or pumping installations, not provided for in groups F04C2/00 - F04C14/00
    • F04C15/0057—Driving elements, brakes, couplings, transmission specially adapted for machines or pumps
    • F04C15/0061—Means for transmitting movement from the prime mover to driven parts of the pump, e.g. clutches, couplings, transmissions
    • 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
    • F04C15/0057—Driving elements, brakes, couplings, transmission specially adapted for machines or pumps
    • F04C15/0061—Means for transmitting movement from the prime mover to driven parts of the pump, e.g. clutches, couplings, transmissions
    • F04C15/0069—Magnetic couplings
    • 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
    • F04C15/0096—Heating; Cooling

Definitions

  • the invention relates to a device for conveying a fluid in a hydraulic circuit, comprising a hydraulic pump and a drive motor for driving the hydraulic pump.
  • motor-pump units a hydraulic fluid, in particular hydraulic oil, is conveyed by means of a hydraulic pump driven by a drive motor within a hydraulic circuit.
  • a field of application of such motor-pump units are by-pass filter units for filtering hydraulic fluid.
  • the invention aims to remedy this situation.
  • the invention is based on the object to provide a device for conveying a fluid in a hydraulic circuit, which allows the use of a lower-performance, designed for normal operation of the hydraulic system drive motor for use at low temperatures. According to the invention, this object is solved by the features of the characterizing part of patent claim 1.
  • a device for conveying a fluid in a hydraulic circuit which allows the use of a lower-performance, designed for normal operation of the hydraulic system drive motor for use at low temperatures. If the rated power of the drive motor is lower than the power required for driving the hydraulic pump in cold operation, when the viscosity of the hydraulic fluid is very large, the slip clutch slips, releasing heat energy. This heat energy causes a heating of the hydraulic fluid, whereby the viscosity and thus also the power required to operate the hydraulic pump decreases. With sufficient heating of the hydraulic fluid is a Coupling of the slip clutch, whereby the hydraulic pump is put into operation.
  • each friction clutch is a slip clutch that generates heat loss when slipping, which is useful for heating the hydraulic fluid.
  • the slip clutch is a magnetic clutch in the form of a hysteresis clutch. Due to the slipping of the magnetic coupling, eddy currents occur in the housing parts of the magnetic coupling, which leads to heating of the magnetic coupling. This heating of the magnetic coupling in turn leads to heating of the hydraulic pump, since the magnetic coupling between the drive motor and the hydraulic pump is connected. The hydraulic fluid in the hydraulic pump is in turn heated over time so that its viscosity decreases. Since it is a hysteresis in the magnetic coupling, a torque is transmitted to the hydraulic pump even in the case of slippage of the magnetic coupling, so that the magnetic coupling makes a rigid connection, even without having to stop the magnetic coupling.
  • Hydraulic fluid according to the invention may be any hydraulic medium, such as oil, water or an emulsion, etc.
  • a hydraulic oil with an average viscosity of 320 mm 2 / s can be used,
  • the housing of the slip clutch is attached directly to the housing of the hydraulic pump.
  • the heat transfer between slip clutch and hydraulic pump is improved.
  • the slip clutch can be flanged directly to the hydraulic pump.
  • means for heat transfer are arranged between the coupling and the hydraulic pump.
  • heat conducting elements made of metal, preferably copper, are recommended.
  • the nominal power of the drive motor corresponds approximately to the power required to drive the hydraulic pump in normal operation.
  • a sufficient dimensioning of the drive motor is achieved with minimized production costs.
  • the energy costs for operating the drive motor are reduced.
  • the motor-pump unit chosen as an exemplary embodiment consists essentially of a drive motor 1 which is connected via a magnetic coupling 2 to a hydraulic pump 3 ( FIG. 2 ).
  • the drive motor 1 has a drive shaft 12 which is rotatably mounted about a rotation axis D.
  • the drive shaft 12 is connected to an outer rotor 13 of the magnetic coupling 2.
  • the magnetic coupling 2 has an inner rotor 14, which is arranged within the outer rotor 13 and which is non-rotatably connected to a pump shaft 15 of the hydraulic pump 3.
  • the pump shaft 15 serves to drive the hydraulic pump 3.
  • the outer rotor 13 is fitted on its inner side and the inner rotor 14 on its outer side with permanent magnets of alternating polarity. At rest, the respective north and south poles of the rotors 13, 14 are opposite, wherein the magnetic field is symmetrical.
  • the Magneifefdlinien be deflected, whereby torques on the air gap between the rotors 13, 14 can be transmitted. If the maximum clutch torque is exceeded, the power transmission is interrupted, so that the two rotors 13, 14 slip through, that is, rotate relative to each other. This produces 2 eddy currents in the metal components of the magnetic coupling, which heat the magnetic coupling 2.
  • the magnetic coupling 2 is designed such that the maximum transmittable torque of the magnetic coupling 2 is less than the required torque for driving the hydraulic pump 3 in cold operation and that the maximum transmissible torque of the magnetic coupling 2 is greater than the torque required for driving the hydraulic pump. 3 in normal operation.
  • the magnetic coupling 2 slips in cold operation and transmits the full torque of the drive motor 1 in normal operation. It is understood that in this case the maximum torque of the drive motor is greater than the maximum transmissible torque of the magnetic coupling.
  • the magnetic coupling 2 is flanged directly to the drive motor 1 and the hydraulic pump.
  • the metallic housing 17 of the hydraulic pump 3 which is so directly connected to the magnetic coupling 2, as a heat transfer means, whereby the indexed by the magnetic coupling 2 heat is transmitted directly to the hydraulic pump 3.
  • a clutch bell 16 is provided, which surrounds the magnetic coupling 2.
  • the clutch bell 16 serves as a housing of the magnetic coupling 2 and is heated by the indicated eddy currents. Due to the heat-conducting connection with the housing 17 of the hydraulic pump 3, the heat is delivered to the hydraulic pump 3.
  • the hydraulic pump 3 may be provided in any type, for example as a gear pump, gear pump, screw pump, vane pump or piston pump.
  • the magnetic coupling can also be designed as a magnetic particle clutch. This is a frictionally engaged coupling.
  • a metal powder or metal gel In the gap between the drive pressure plate and the output pressure plate is a metal powder or metal gel.
  • the contained metal particles can be magnetized via an accommodated in a pressure plate electromagnet and so erected. As a result, a non-positive connection is achieved. By changing the applied voltage, a firm connection or slip can be generated.
  • FIG. 1 the use of a device according to the invention in a bypass filter unit is shown by way of example, in which hydraulic fluid in the form of a hydraulic oil is pumped through a filter unit 5.
  • the hydraulic pump 3 the input side with a hydraulic line 7 and the output side with an inlet 8, which is guided to the filter unit 5, is used.
  • a drain 11 of the filter unit 5 is connected to a further hydraulic line 9.
  • the outlet 11 and the inlet 8 are connected to each other via a bypass line 10, wherein in the bypass line 10, a bypass valve 6 is provided in the form of a check valve.
  • the bypass valve 6 opens from the inlet 8 to the outlet 11 at high pressures so as not to damage the filter unit 5 when the pressures are too high or to prevent the drive unit from overloading when the filter unit 5 has been added.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Hydraulic Clutches, Magnetic Clutches, Fluid Clutches, And Fluid Joints (AREA)

Abstract

The device has a hydraulic pump (3), and a drive motor (1) i.e. asynchronous alternating current motor, for driving the hydraulic pump, where the hydraulic pump and the drive motor are connected together by a friction clutch (2) such as multiple disk clutch and magnetic clutch i.e. hysteresis clutch. A housing (16) of the friction clutch is directly fastened with a housing (17) of the hydraulic pump. The friction clutch and the hydraulic pump are designed in such a manner that required torque for driving the pump is larger than maximum transferred torque of the friction clutch.

Description

Die Erfindung betrifft eine Vorrichtung zur Förderung eines Fluids in einem Hydraulikkreislauf, umfassend eine Hydraulikpumpe und einem Antriebsmotor zum Antrieb der Hydraulikpumpe.The invention relates to a device for conveying a fluid in a hydraulic circuit, comprising a hydraulic pump and a drive motor for driving the hydraulic pump.

In derartigen, sogenannten Motor-Pumpen-Aggregaten wird ein Hydraulikfluid, insbesondere Hydrauliköl, mittels einer von einem Antriebsmotor angetriebenen Hydraulikpumpe innerhalb eines Hydraulikkreislaufs gefördert. Ein Anwendungsgebiet solcher Motor-Pumpen-Aggregate sind Nebenstromfilter-Aggregate zur Filterung von Hydraulikflüssigkeit.In such, so-called motor-pump units, a hydraulic fluid, in particular hydraulic oil, is conveyed by means of a hydraulic pump driven by a drive motor within a hydraulic circuit. A field of application of such motor-pump units are by-pass filter units for filtering hydraulic fluid.

Bei Anwendungsfällen, in denen das Hydrauliksystem stark schwankenden Temperaturen ausgesetzt ist, ergibt sich die Problematik, dass insbesondere bei extrem niedrigen Temperaturen von -20°C bis -40°C die Viskosität der Hydraulikflüssigkeit signifikant zunimmt, so dass die Leistungsaufnahme der Hydraulikpumpe erheblich ansteigt. Um auch bei solchen niedrigen Temperaturen zu gewährleisten, dass das Hydrauliksystem funktionsfähig ist, ist es bekannt, die Leistung des Antriebsmotors auf die Bedingungen bei sehr niedrigen Temperaturen auszulegen wo die Viskosität des Hydraulikfluids sehr hoch ist (Kaltbetrieb). Dies hat zur Folge, dass ein sehr leistungsstarker Antriebsmotor zum Einsatz kommt, dessen Leistung bei Normalbetrieb, wenn die Viskosität der Hydraulikflüssigkeit auf Grund der höheren Betriebstemperaturen abgenommen hat, weit über der erforderlichen Leistung zum Antreiben der Hydraulikpumpe liegt. Insbesondere bei Verwendung von Wechselstrom-Asynchron-Motoren, die eine annähernd konstante elektrische Leistungsaufnahme über dies Ausgangsleistung aufweisen, führt die zu einer hohen Energieineffizienz.In applications in which the hydraulic system is exposed to highly fluctuating temperatures, there is the problem that, especially at extremely low temperatures of -20 ° C to -40 ° C, the viscosity of the hydraulic fluid significantly increases, so that the power consumption of the hydraulic pump increases significantly. In order to ensure that the hydraulic system is functional even at such low temperatures, it is well known that its performance of the drive motor to the conditions at very low temperatures interpret where the viscosity of the hydraulic fluid is very high (cold operation). This has the consequence that a very powerful drive motor is used, the performance in normal operation, when the viscosity of the hydraulic fluid has decreased due to the higher operating temperatures, far above the power required to drive the hydraulic pump. In particular, when using AC asynchronous motors having an approximately constant electrical power consumption over this output power, which leads to a high energy inefficiency.

Weiterhin ist es bekannt, in derartigen Anwendungsfällen eine Hydraulikflüssigkeit mit geringerer Viskosität einzusetzen. Dies ist je nach Anwendungsfall der Gesamtanlage bzw. des Gesamtsystems jedoch nicht immer möglich.Furthermore, it is known to use a hydraulic fluid with a lower viscosity in such applications. However, this is not always possible depending on the application of the overall system or the overall system.

Hier will die Erfindung Abhilfe schaffen. Der Erfindung liegt die Aufgabe zu Grunde, eine Vorrichtung zur Förderung eines Fluids in einem Hydraulikkreislauf zu schaffen, welche den Einsatz eines leistungsschwächeren, für den Normalbetrieb des Hydrauliksystems ausgelegten Antriebsmotors auch für den Einsatz bei niedrigen Temperaturen ermöglicht. Gemäß der Erfindung wird diese Aufgabe durch die Merkmale des kennzeichnenden Teils des Patentanspruchs 1 gelöst.The invention aims to remedy this situation. The invention is based on the object to provide a device for conveying a fluid in a hydraulic circuit, which allows the use of a lower-performance, designed for normal operation of the hydraulic system drive motor for use at low temperatures. According to the invention, this object is solved by the features of the characterizing part of patent claim 1.

Mit der Erfindung ist eine Vorrichtung zur Förderung eines Fluids in einem Hydraulikkreislauf geschaffen, welche den Einsatz eines leistungsschwächeren, für den Normalbetrieb des Hydrauliksystems ausgelegten Antriebsmotors auch für den Einsatz bei niedrigen Temperaturen ermöglicht. Ist die Nennleistung des Antriebsmotors geringer, als die erforderliche Leistung zum Antreiben der Hydraulikpumpe im Kaltbetrieb, wenn die Viskosität der Hydraulikflüssigkeit sehr groß ist, so erfolgt ein Durchrutschen der Rutschkupplung, wodurch Wärmeenergie frei wird. Diese Wärmeenergie bewirkt eine Erwärmung des Hydraulikfluids, wodurch die Viskosität und damit auch die zum Betrieb der Hydraulikpumpe erforderliche Leistung abnimmt. Bei hinreichender Erwärmung des Hydraulikfluids erfolgt eine Kupplung der Rutschkupplung, wodurch die Hydraulikpumpe in Betrieb genommen wird.With the invention, a device for conveying a fluid in a hydraulic circuit is provided which allows the use of a lower-performance, designed for normal operation of the hydraulic system drive motor for use at low temperatures. If the rated power of the drive motor is lower than the power required for driving the hydraulic pump in cold operation, when the viscosity of the hydraulic fluid is very large, the slip clutch slips, releasing heat energy. This heat energy causes a heating of the hydraulic fluid, whereby the viscosity and thus also the power required to operate the hydraulic pump decreases. With sufficient heating of the hydraulic fluid is a Coupling of the slip clutch, whereby the hydraulic pump is put into operation.

In Weiterbildung der Erfindung ist die Rutschkupplung als Lamellenkupplung ausgeführt. Hierdurch ist eine große Reibfläche erzielt, wodurch die beim Durchrutschen erzielte Wärmeleistung erhöht ist. Grundsätzlich ist jede Reibkupplung eine Rutschkupplung, die beim Durchrutschen Verlustwärme erzeugt, welche zur Erwärmung des Hydraulikfluids nutzbar ist.In a further development of the invention, the slip clutch is designed as a multi-plate clutch. As a result, a large friction surface is achieved, whereby the heat output achieved during slipping is increased. Basically, each friction clutch is a slip clutch that generates heat loss when slipping, which is useful for heating the hydraulic fluid.

In alternativer Ausgestaltung der Erfindung ist die Rutschkupplung eine Magnetkupplung in Form einer Hysteresekupplung. Durch das Durchrutschen der Magnetkupplung entstehen in den Gehäuseteilen der Magnetkupplung Wirbelströme, welche zur Erwärmung der Magnetkupplung führen. Diese Erwärmung der Magnetkupplung führt wiederum zur Erwärmung der Hydraulikpumpe, da die Magnetkupplung zwischen dem Antriebsmotor und der Hydraulikpumpe geschaltet ist. Die in der Hydraulikpumpe befindliche Hydraulikflüssigkeit wird wiederum im Laufe der Zeit erwärmt, so dass deren Viskosität abnimmt. Da es sich bei der Magnetkupplung um eine Hysteresekupplung handelt, wird auch im Falle des Durchrutschens der Magnetkupplung ein Drehmoment auf die Hydraulikpumpe übertragen, so dass die Magnetkupplung eine starre Verbindung herstellt, auch ohne die Magnetkupplung anhalten zu müssen.In an alternative embodiment of the invention, the slip clutch is a magnetic clutch in the form of a hysteresis clutch. Due to the slipping of the magnetic coupling, eddy currents occur in the housing parts of the magnetic coupling, which leads to heating of the magnetic coupling. This heating of the magnetic coupling in turn leads to heating of the hydraulic pump, since the magnetic coupling between the drive motor and the hydraulic pump is connected. The hydraulic fluid in the hydraulic pump is in turn heated over time so that its viscosity decreases. Since it is a hysteresis in the magnetic coupling, a torque is transmitted to the hydraulic pump even in the case of slippage of the magnetic coupling, so that the magnetic coupling makes a rigid connection, even without having to stop the magnetic coupling.

Hydraulikfluid im Sinne der Erfindung kann jedes hydraulische Medium, wie z.B. ÖI, Wasser oder eine Emulsion etc. sein. Für bestimmte Anwendungsfälle kann insbesondere ein Hydrauliköl mit einer mittleren Viskosität von 320 mm2/s eingesetzt werden,Hydraulic fluid according to the invention may be any hydraulic medium, such as oil, water or an emulsion, etc. For certain applications, in particular a hydraulic oil with an average viscosity of 320 mm 2 / s can be used,

In Weiterbildung der Erfindung ist das Gehäuse der Rutschkupplung unmittelbar an dem Gehäuse der Hydraulikpumpe befestigt. Hierdurch ist die Wärmeübertragung zwischen Rutschkupplung und Hydraulikpumpe verbessert. Beispielsweise kann die Rutschkupplung unmittelbar an die Hydraulikpumpe angeflanscht sein. Vorteilhaft sind zwischen Kupplung und Hydraulikpumpe Mittel zur Wärmeübertragung angeordnet. Hierbei empfehlen sich insbesondere Wärmeleitelemente aus Metall, vorzugsweise aus Kupfer.In a further development of the invention, the housing of the slip clutch is attached directly to the housing of the hydraulic pump. As a result, the heat transfer between slip clutch and hydraulic pump is improved. For example, the slip clutch can be flanged directly to the hydraulic pump. Advantageously, means for heat transfer are arranged between the coupling and the hydraulic pump. Here, in particular, heat conducting elements made of metal, preferably copper, are recommended.

Vorteilhaft entspricht die Nennleistung des Antriebsmotors etwa der erforderlichen Leistung zum Antreiben der Hydraulikpumpe im Normalbetrieb. Hierdurch ist eine ausreichende Dimensionierung des Antriebsmotors bei minimierten Herstellungskosten erzielt. Weiterhin sind die Energiekosten zum Betrieb des Antriebsmotors vermindert.Advantageously, the nominal power of the drive motor corresponds approximately to the power required to drive the hydraulic pump in normal operation. As a result, a sufficient dimensioning of the drive motor is achieved with minimized production costs. Furthermore, the energy costs for operating the drive motor are reduced.

Andere Weiterbildungen und Ausgestaltungen der Erfindung sind in den übrigen Unteransprüchen angegeben. Ein Ausführungsbeispiel der Erfindung ist in den Zeichnungen dargestellt und wird nachfolgend im Einzelnen beschrieben. Es zeigen:

Figur 1
die schematisch Garstellung eines Ausschnitts eines Hydraulikkreislaufs mit erfindungsgemäßer Vorrichtung und
Figur 2
die Darstellung einer erfindungsgemäßen Vorrichtung im Längs- schnitt.
Other developments and refinements of the invention are specified in the remaining subclaims. An embodiment of the invention is illustrated in the drawings and will be described in detail below. Show it:
FIG. 1
the schematic Garstellung a section of a hydraulic circuit with inventive device and
FIG. 2
the representation of a device according to the invention in longitudinal section.

Das als Ausführungsbeispiel gewählte Motor-Pumpen-Aggregat besteht im Wesentlichen aus einem Antriebsmotor 1, der über eine Magnetkupplung 2 mit einer Hydraulikpumpe 3 verbunden ist (Figur 2).The motor-pump unit chosen as an exemplary embodiment consists essentially of a drive motor 1 which is connected via a magnetic coupling 2 to a hydraulic pump 3 ( FIG. 2 ).

Der Antriebsmotor 1 weist eine Antriebswelle 12 auf, die um eine Drehachse D drehbar gelagert ist. Die Antriebswelle 12 ist mit einem Außenrotor 13 der Magnetkupplung 2 verbunden. Die Magnetkupplung 2 weist einen innerhalb des Außenrotors 13 angeordneten Innenrotor 14 auf, der mit einer Pumpenwelle 15 der Hydraulikpumpe 3 drehfest verbunden ist. Die Pumpenwelle 15 dient zum Antreiben der Hydraulikpumpe 3.The drive motor 1 has a drive shaft 12 which is rotatably mounted about a rotation axis D. The drive shaft 12 is connected to an outer rotor 13 of the magnetic coupling 2. The magnetic coupling 2 has an inner rotor 14, which is arranged within the outer rotor 13 and which is non-rotatably connected to a pump shaft 15 of the hydraulic pump 3. The pump shaft 15 serves to drive the hydraulic pump 3.

Der Außenrotor 13 ist auf seiner Innenseite und der Innenrotor 14 auf seiner Außenseite mit Permanentmagneten wechselnder Polarität bestückt. Im Ruhezustand stehen sich die jeweiligen Nord- und Südpole der Rotoren 13, 14 gegenüber, wobei das Magnetfeld symmetrisch ist. Durch Verdrehen der Rotoren 13, 14 werden die Magneifefdlinien ausgelenkt, wodurch Drehmomente über den Luftspalt zwischen den Rotoren 13, 14 übertragen werden können. Wird das maximale Kupplungsdrehmoment überschritten, so wird die Kraftübertragung unterbrochen, so dass die beiden Rotoren 13, 14 durchrutschen, das heißt relativ zueinander drehen. Hierbei entstehen in den Metallbauteilen der Magnetkupplung 2 Wirbelströme, welche die Magnetkupplung 2 erwärmen.The outer rotor 13 is fitted on its inner side and the inner rotor 14 on its outer side with permanent magnets of alternating polarity. At rest, the respective north and south poles of the rotors 13, 14 are opposite, wherein the magnetic field is symmetrical. By turning the rotors 13, 14, the Magneifefdlinien be deflected, whereby torques on the air gap between the rotors 13, 14 can be transmitted. If the maximum clutch torque is exceeded, the power transmission is interrupted, so that the two rotors 13, 14 slip through, that is, rotate relative to each other. This produces 2 eddy currents in the metal components of the magnetic coupling, which heat the magnetic coupling 2.

Die Magnetkupplung 2 ist derart ausgelegt, dass das maximal übertragbare Drehmoment der Magnetkupplung 2 geringer ist, als das erforderliche Drehmoment zum Antreiben der Hydraulikpumpe 3 im Kaltbetrieb und dass das maximal übertragbare Drehmoment der Magnetkupplung 2 größer ist, als das erforderliche Drehmoment zum Antreiben der Hydraulikpumpe 3 im Normalbetrieb. Somit rutscht die Magnetkupplung 2 im Kaltbetrieb durch und überträgt das volle Drehmoment des Antriebsmotors 1 im Normalbetrieb. Es versteht sich, dass hierbei das maximale Drehmoment des Antriebsmotors größer ist als das maximal übertragbare Drehmoment der Magnetkupplung.The magnetic coupling 2 is designed such that the maximum transmittable torque of the magnetic coupling 2 is less than the required torque for driving the hydraulic pump 3 in cold operation and that the maximum transmissible torque of the magnetic coupling 2 is greater than the torque required for driving the hydraulic pump. 3 in normal operation. Thus, the magnetic coupling 2 slips in cold operation and transmits the full torque of the drive motor 1 in normal operation. It is understood that in this case the maximum torque of the drive motor is greater than the maximum transmissible torque of the magnetic coupling.

Die Magnetkupplung 2 ist unmittelbar an den Antriebsmotor 1 sowie die Hydraulikpumpe angeflanscht. Dabei dient das metallische Gehäuse 17 der Hydraulikpumpe 3, welche so unmittelbar mit der Magnetkupplung 2 verbunden ist, als Wärmeübertragungsmittel, wodurch die von der Magnetkupplung 2 indizierte Wärme direkt zur Hydraulikpumpe 3 übertragen wird. Zusätzlich ist eine Kupplungsglocke 16 vorgesehen, welche die Magnetkupplung 2 umgibt. Die Kupplungsglocke 16 dient als Gehäuse der Magnetkupplung 2 und wird durch die indizierten Wirbelströme erwärmt. Durch die wärmeleitende Verbindung mit dem Gehäuse 17 der Hydraulikpumpe 3 wird die Wärme an die Hydraulikpumpe 3 abgegeben.The magnetic coupling 2 is flanged directly to the drive motor 1 and the hydraulic pump. In this case, the metallic housing 17 of the hydraulic pump 3, which is so directly connected to the magnetic coupling 2, as a heat transfer means, whereby the indexed by the magnetic coupling 2 heat is transmitted directly to the hydraulic pump 3. In addition, a clutch bell 16 is provided, which surrounds the magnetic coupling 2. The clutch bell 16 serves as a housing of the magnetic coupling 2 and is heated by the indicated eddy currents. Due to the heat-conducting connection with the housing 17 of the hydraulic pump 3, the heat is delivered to the hydraulic pump 3.

Die Hydraulikpumpe 3 kann in beliebiger Bauart vorgesehen sein, beispielsweise als Zahnradpumpe, Zahnringpumpe, Schraubenpumpe, Flügelpumpe oder Kolbenpumpe.The hydraulic pump 3 may be provided in any type, for example as a gear pump, gear pump, screw pump, vane pump or piston pump.

Alternativ zur beschriebenen Hysteresekupplung kann die Magnetkupplung auch als Magnetpulverkupplung ausgeführt sein. Hierbei handelt es sich um eine reibschlüssige Kupplung. Im Spalt zwischen der Antriebsdruckplatte und der Abtriebsdruckplatte befindet sich ein Metallpulver oder Metallgel. Die enthaltenen Metallteilchen können über einen in einer Druckplatte untergebrachten Elektromagneten magnetisiert und so aufgerichtet werden. Hierdurch wird eine kraftschlüssige Verbindung erreicht. Durch Ändern der angelegten Spannung kann eine feste Verbindung oder Schlupf erzeugt werden.As an alternative to the described hysteresis coupling, the magnetic coupling can also be designed as a magnetic particle clutch. This is a frictionally engaged coupling. In the gap between the drive pressure plate and the output pressure plate is a metal powder or metal gel. The contained metal particles can be magnetized via an accommodated in a pressure plate electromagnet and so erected. As a result, a non-positive connection is achieved. By changing the applied voltage, a firm connection or slip can be generated.

In Figur 1 ist beispielhaft der Einsatz einer erfindungsgemäßen Vorrichtung in einem Nebenstromfilteraggregat gezeigt, bei dem Hydraulikfluid in Form eines Hydrauliköls durch eine Filtereinheit 5 gepumpt wird. Hierzu dient die Hydraulikpumpe 3, die eingangsseitig mit einer Hydraulikleitung 7 und ausgangsseitig mit einem Zulauf 8, der zur Filtereinheit 5 geführt ist, verbunden ist. Ein Ablauf 11 der Filtereinheit 5 ist mit einer weiteren Hydraulikleitung 9 verbunden. Der Ablauf 11 und der Zulauf 8 sind über eine Bypassleitung 10 miteinander verbunden, wobei in der Bypassleitung 10 ein Bypassventil 6 in Form eines Rückschlagventils vorgesehen ist. Das Bypassventil 6 öffnet vom Zulauf 8 zum Ablauf 11 bei hohen Drücken, um bei zu hohen Drücken die Filtereinheit 5 nicht zu beschädigen oder bei zugesetzter Filtereinheit 5 eine Überlastung des Antriebs zu verhindern.In FIG. 1 the use of a device according to the invention in a bypass filter unit is shown by way of example, in which hydraulic fluid in the form of a hydraulic oil is pumped through a filter unit 5. For this purpose, the hydraulic pump 3, the input side with a hydraulic line 7 and the output side with an inlet 8, which is guided to the filter unit 5, is used. A drain 11 of the filter unit 5 is connected to a further hydraulic line 9. The outlet 11 and the inlet 8 are connected to each other via a bypass line 10, wherein in the bypass line 10, a bypass valve 6 is provided in the form of a check valve. The bypass valve 6 opens from the inlet 8 to the outlet 11 at high pressures so as not to damage the filter unit 5 when the pressures are too high or to prevent the drive unit from overloading when the filter unit 5 has been added.

Claims (9)

Vorrichtung zur Förderung eines Fluids innerhalb eines Hydraulikkreislaufs, umfassend eine Hydraulikpumpe und einen Antriebsmotor zum Antrieb der Hydraulikpumpe, dadurch gekennzeichnet, dass Hydraulikpumpe (3) und Antriebsmotor (1) über eine Rutschkupplung (2) miteinander verbunden sind.Device for conveying a fluid within a hydraulic circuit, comprising a hydraulic pump and a drive motor for driving the hydraulic pump, characterized in that the hydraulic pump (3) and drive motor (1) via a slip clutch (2) are interconnected. Vorrichtung nach dadurch gekennzeichnet, dass die Rutschkupplung (2) als Lamellenkupplung ausgeführt ist.Device according to, characterized in that the slip clutch (2) is designed as a multi-plate clutch. Vorrichtung nach Anspruch 1, dadurch gekennzeichnet, dass die Rutschkupplung (2) eine Magnetkupplung in Form einer Hysteresekupplung ist.Apparatus according to claim 1, characterized in that the slip clutch (2) is a magnetic coupling in the form of a hysteresis clutch. Vorrichtung nach einem der vorgenannten Ansprüche, dadurch gekennzeichnet, dass das Gehäuse (16) der Rutschkupplung (2) unmittelbar mit dem Gehäuse (17) der Hydraulikpumpe (3) befestigt ist.Device according to one of the preceding claims, characterized in that the housing (16) of the slip clutch (2) directly to the housing (17) of the hydraulic pump (3) is fixed. Vorrichtung nach einem der vorgenannten Ansprüche, dadurch gekennzeichnet, dass die Rutschkupplung (2) und die Hydraulikpumpe (3) derart ausgelegt sind, dass das erforderliche Drehmoment zum Antreiben der Hydraulikpumpe (3) im Kaltbetrieb größer ist, als das maximale übertragbare Drehmoment der Rutschkupplung (2).Device according to one of the preceding claims, characterized in that the slip clutch (2) and the hydraulic pump (3) designed in such a way are that the required torque for driving the hydraulic pump (3) in cold operation is greater than the maximum transmittable torque of the slip clutch (2). Vorrichtung nach einem der vorgenannten Ansprüche, dadurch gekennzeichnet, dass zwischen Kupplung (2) und Hydraulikpumpe (3) Mittel zur Wärmeübertragung angeordnet sind.Device according to one of the preceding claims, characterized in that means for heat transfer are arranged between the coupling (2) and the hydraulic pump (3). Vorrichtung nach einem der vorgenannten Ansprüche, dadurch gekennzeichnet, dass die Nennleistung des Antriebsmotors (1) geringer ist, als die erforderliche Leistung zum Antreiben der Hydraulikpumpe (3) im Kaltbetrieb.Device according to one of the preceding claims, characterized in that the rated power of the drive motor (1) is lower than the power required to drive the hydraulic pump (3) in cold operation. Vorrichtung nach Anspruch 6, dadurch gekennzeichnet, dass die Nennleistung des Antriebsmotors (1) etwa der erforderlichen Leistung zum Antreiben der Hydraulikpumpe (3) im Normalbetrieb entspricht.Apparatus according to claim 6, characterized in that the rated power of the drive motor (1) corresponds approximately to the power required for driving the hydraulic pump (3) in normal operation. Vorrichtung nach einem der vorgenannten Ansprüche, dadurch gekennzeichnet, dass der Antriebsmotor (1) ein Asynchron-Wechselstrommotor ist.Device according to one of the preceding claims, characterized in that the drive motor (1) is an asynchronous AC motor.
EP09006795A 2009-05-20 2009-05-20 Device for transporting a fluid in a hydraulic circuit Withdrawn EP2253844A1 (en)

Priority Applications (3)

Application Number Priority Date Filing Date Title
EP09006795A EP2253844A1 (en) 2009-05-20 2009-05-20 Device for transporting a fluid in a hydraulic circuit
PCT/EP2010/003030 WO2010133339A1 (en) 2009-05-20 2010-05-19 Device for delivering a fluid in a hydraulic circuit
CN2010800329659A CN102549263A (en) 2009-05-20 2010-05-19 Device for delivering a fluid in a hydraulic circuit

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
EP09006795A EP2253844A1 (en) 2009-05-20 2009-05-20 Device for transporting a fluid in a hydraulic circuit

Publications (1)

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EP2253844A1 true EP2253844A1 (en) 2010-11-24

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CN (1) CN102549263A (en)
WO (1) WO2010133339A1 (en)

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WO2010133339A1 (en) 2010-11-25

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