WO2011051055A1 - Transmission device - Google Patents

Transmission device Download PDF

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Publication number
WO2011051055A1
WO2011051055A1 PCT/EP2010/063831 EP2010063831W WO2011051055A1 WO 2011051055 A1 WO2011051055 A1 WO 2011051055A1 EP 2010063831 W EP2010063831 W EP 2010063831W WO 2011051055 A1 WO2011051055 A1 WO 2011051055A1
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WO
WIPO (PCT)
Prior art keywords
shaft
transmission device
gear
shafts
annular gap
Prior art date
Application number
PCT/EP2010/063831
Other languages
German (de)
French (fr)
Inventor
Tomas Smetana
Original Assignee
Schaeffler Technologies Gmbh & 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 Schaeffler Technologies Gmbh & Co. Kg filed Critical Schaeffler Technologies Gmbh & Co. Kg
Publication of WO2011051055A1 publication Critical patent/WO2011051055A1/en

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H57/00—General details of gearing
    • F16H57/04—Features relating to lubrication or cooling or heating
    • F16H57/042—Guidance of lubricant
    • F16H57/0427—Guidance of lubricant on rotary parts, e.g. using baffles for collecting lubricant by centrifugal force
    • F16H57/0428—Grooves with pumping effect for supplying lubricants
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H57/00—General details of gearing
    • F16H57/04—Features relating to lubrication or cooling or heating
    • F16H57/042—Guidance of lubricant
    • F16H57/043—Guidance of lubricant within rotary parts, e.g. axial channels or radial openings in shafts
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H57/00—General details of gearing
    • F16H57/04—Features relating to lubrication or cooling or heating
    • F16H57/0467—Elements of gearings to be lubricated, cooled or heated
    • F16H57/0469—Bearings or seals
    • F16H57/0471—Bearing

Definitions

  • the invention relates to a transmission device with at least two shafts, which are coaxial to a common axis of rotation, of which a first shaft is designed as a hollow shaft and of which a second shaft is arranged in the first shaft, wherein the transmission device at least one lubrication point and at least one of Lubricating oil has flowed through annular gap between the shafts to supply the lubrication point and wherein in the annular gap at least one conveying member is arranged with a helical profiling for a lubricating oil promoting effect.
  • the transmission device is designed as a planetary gear differential with an input shaft on which rotatably a planet carrier sits.
  • the planet gears of the planetary gear mesh externally with a ring gear, which is connected to an output shaft.
  • the planetary gears mesh with a sunbathing wheel.
  • the sun gear is formed at the end of a hollow shaft coaxial with the input shaft, in which the input shaft is inserted.
  • the lubrication device has an oil gutter in which spray oil of a chain is caught.
  • the trapped lubricating oil drains from the oil gutter into an annulus surrounding the inner shaft.
  • the lubricating device further has an annular gap which is formed between the annular gap of the nested waves. About this annular gap can lubricating oil to bearings of the Shafts and planetary gears as well as tooth contact in the planetary gear be promoted.
  • the lubricating oil is conveyed in the generic transmission device by means of a conveyor member through the annular gap.
  • the conveying member is a sleeve having a cylindrical portion with helical profiling and fixed relative to the housing of the transmission device. This profiling is formed on the inside of the portion of the sleeve, which is arranged in the annular gap. It consists of rib-like elevations and lies opposite the inner shaft at a gap.
  • the profiling acts upon rotation of the inner shaft in cooperation with the surface of the inner shaft like a screw conveyor, which promotes the adhering to the rotating inner shaft lubricating oil in the annular gap in the axial direction.
  • relatively high lubricating oil pressure is built up in the lubricating channel, so that the lubrication points in the planetary gear can be adequately supplied via this.
  • Throttle shaft arrangements are becoming increasingly important in modern transmission devices, such as those in transmission devices for add-on hybrid drives or in dual-clutch transmissions.
  • a mechanical transmission for example a differential or a transfer case, is also driven by an electric motor in addition to the internal combustion engine or the vehicle transmission in the so - called "add - on mode.”
  • the electric motor required for the drive can be made coaxial for reasons of space
  • the rotor shaft of the electric motor is an optionally driving hollow shaft in which the input shaft or output shaft is plugged in.
  • dual-clutch transmissions for example, two input shafts of a transmission which can be driven independently of one another are inserted into one another.
  • the coaxial nested shafts may be supported at bearings. Often that is Lubricating oil supply of these bearings on the stub shaft assembly to other bearings difficult, especially if the bearings are rolling bearings. Due to the low radial design needle bearings are preferably used at these bearings. Needle bearings are characterized by low construction, since the diameter of the rollers called needles is low relative to their length. It would be advantageous if the needle bearings could be filled at the bearings permanently with grease. However, this is only possible in arrangements in which the needle roller bearings are exposed to low operating speeds and sealed. At high speeds, the line contact of the needles in the rolling contact does not always ensure sufficient grease life. The needle bearings must therefore be supplied with lubricating oil.
  • annular gaps between the nested shafts can be provided as lubrication channels, over which it is difficult due to their length and small cross-section to transport lubricating oil to other lubrication points. Often therefore can not be dispensed with a pressure oil supply by pump.
  • the object of the invention is therefore to provide a transmission device with an effective lubrication device, with which the supply of hard-to-reach lubrication points can be adequately supplied via annular gaps of plug-shaft assemblies and which can be produced inexpensively.
  • the invention relates to all transmission device with at least two shafts, which are inserted coaxially into one another to a common axis of rotation of where a first shaft is designed as a hollow shaft and of which a second shaft is inserted in the first shaft.
  • the partially or predominantly nested over the entire length shafts are both driving shafts or a driving shaft and one is a driven shaft or both are driven shafts between which an oil-flowing through an annular gap for supplying at least one lubrication point is formed.
  • At least one helical profiling with a lubricating oil promoting action is arranged in the annular gap.
  • the helical profiling in the annular gap is rotatable about the common axis of rotation of the shafts separately from at least one of the shafts.
  • the conveyor member having the helical profiling is itself rotatably received in the transmission device about the axis of rotation and to at least one of the shafts.
  • ribs or grooves correspond with a cylindrical surface or with corresponding helical surfaces of one of the shafts, a housing or any other cylindrical surface. They correspond so that they cooperate with each other to effect upon rotation, the axial promotion of lubricating oil in the gap. It is advantageous that such profilings can be designed so that they also promote when reversing the direction of rotation about the axis of rotation. The advantage of such arrangements is, in particular, that the volume flow delivered with this profiling is not only dependent on the rotational speed of one of the shafts but is influenced, for example amplified, by the self-rotating conveyor member.
  • lubricating oil can be promoted when the shaft is stationary.
  • the helical profiling or the conveying member is driven to rotate about the axis of rotation. So it is conceivable that the conveyor member is driven with the profiling with a separate drive. As a result, the drive of the conveyor is independent of standstill or the speed of one of the waves.
  • a further embodiment of the invention provides that the helical profiling or the conveying member is drivable by means of at least one gear, wherein the gear is rotatably mounted on one of the shafts.
  • Such a drive is particularly advantageous if the gear is rotatably connected to the first shaft. Since, in this case, the first shaft is a driven or driving shaft, the supply of lubricating oil is ensured even when the second inner shaft is at a standstill.
  • the gear is arranged in a power train of the transmission device. In this case, no separate drive of the conveyor link is necessary because the drive is protected by the power supplied by the gear device.
  • a further embodiment of the invention provides that the gear is a sun gear of a planetary gear of the transmission device. This arrangement is particularly advantageous when the sun gear is fixedly connected to the first shaft, and the first shaft is the rotor shaft of the electric motor. In this case, depending on the power flow, the conveying member is driven either by the electric motor or by power from the planetary gear. The latter applies, for example, when the rotor is dragged along and the electric motor is used as brake or generator. Alternatively, at standstill of the sun gear, the conveying effect by speed the other wave maintained. The latter is true when the profiling is directed to the inner shaft and lubricating oil corresponds with the surface thereof. Description of the drawings
  • Figure 1 shows a partial section of a transmission device 1 shown in simplified form with a planetary gear of a differential with an electric motor 2.
  • the planetary gear is shown partially with the sun gear 3 and planetary gears 4.
  • a rotor 5 of the electric motor 2 is seated on a first shaft 6.
  • the first shaft 6 is rotatably supported in the housing 9 of the transmission device 1 by means of angular contact ball bearings 7 and 8.
  • the first shaft 6 is hollow inside and has a through hole 17.
  • the sun gear 3 is rotatably attached.
  • the sun gear 3 is meshed with a gear 15 with the planetary gears 4, which are integrated in the power train of the differential and has a shaft 16.
  • the shaft 16 and the gear 15 are hollow inside.
  • a second shaft 12 is inserted in the through hole 17 of the first shaft 6 and a through hole 18 of the sun gear 3 and is rotatably supported at two bearings 10 and 1 1 in the first shaft 6,.
  • the bearings 10 and 1 1 each have a designed as a needle bearing 13 and 14 bearings.
  • the needle bearings 13 and 14 are each formed of a sleeve 19 and 20 of rolling elements in the form of needles.
  • an annular gap 21 is formed between the first shaft 6 and the second shaft 12.
  • Another annular gap 22 between the sun gear 3 and the second shaft 12 is formed.
  • the cross section of the annular gap 22 is smaller than the cross section of the annular gap 21.
  • the rotationally symmetrical shaft 16 of Sun gear 3 is a conveying member 23 which is provided for conveying lubricating oil inside in the through hole 18 with a helical profiling 24 which faces the second shaft 12 and rotates about this.
  • the flow direction of the lubricating oil is indicated by means of the directional arrows.
  • FIG. 4 shows a section through the sun gear 3 along the axis of rotation.
  • the helical profiling on the inside of the shaft 16 is a spirally extending groove 30, which promotes axially in the direction of the lubrication points 27 and 28 upon rotation of the second shaft 12 in forward rotation in a direction of rotation with, for example, high speeds, even by relative speeds of the two shafts ,
  • the conveying member 23 is rotatably arranged with the helical profiling 24 in the annular gap 21 about the common axis of rotation 25 of the shafts 6 and 12 and is driven during operation of the electric motor 2 by means of the first shaft 6 designed as a rotor shaft.
  • Lubricating oil passes through the shaft end 26 into the annular gap 22 and is conveyed from there by the conveying action of the helical profiling 24 in the annular gap 21 and the lubrication points 27 and 28, which are the bearings 10 and 1 1 and whose cross section is narrower than the cross section of the annular gap 22.
  • the lubricating oil is conveyed via the transverse bores 29 into the lubricating channel 35 and from there into the planetary gearbox.
  • Figure 5 shows an alternative embodiment of a sun gear 31, wherein the helical profiling 24 and thus the groove 30 is not formed directly on a shaft, but on a separate sleeve 33.
  • the sleeve 33 is pressed into the through hole 32.
  • a sun gear 31 designed in this way can be produced more easily, since the groove 30 is not introduced into the shaft 34, for example, by machining, for example must be, but is formed, for example, on a sleeve 33 produced by rolling sheet metal.

Abstract

The invention relates to a transmission device (1) having at least two shafts (6, 12) which are coaxial to a common axis of rotation (25), of which a first shaft (6) is designed as a hollow shaft and of which a second shaft (12) is arranged in the first shaft (6), wherein the transmission device (1) has at least one lubrication point (27, 28) and at least one annular gap (21, 22), through which lubrication oil flows, between the shafts (6, 12) for supplying the lubrication point (27, 28) and wherein at least one conveying member (23) having a helically wound profile (24) is arranged in the annular gap (21, 22) for a lubricating oil conveying effect.

Description

Bezeichnung der Erfindung  Name of the invention
Getriebevorrichtung Beschreibung Transmission device description
Gebiet der Erfindung Field of the invention
Die Erfindung betrifft eine Getriebevorrichtung mit mindestens zwei Wellen, die zu einer gemeinsamen Rotationsachse koaxial sind, von denen eine erste Welle als Hohlwelle ausgeführt ist und von denen eine zweite Welle in der ersten Welle angeordnet ist, wobei die Getriebevorrichtung wenigstens eine Schmierstelle und mindestens einen von Schmieröl durchflossenen Ringspalt zwischen den Wellen zur Versorgung der Schmierstelle aufweist und wobei in dem Ring- spalt wenigstens ein Förderglied mit einer schraubenlinienförmige Profilierung für eine Schmieröl fördernden Wirkung angeordnet ist. The invention relates to a transmission device with at least two shafts, which are coaxial to a common axis of rotation, of which a first shaft is designed as a hollow shaft and of which a second shaft is arranged in the first shaft, wherein the transmission device at least one lubrication point and at least one of Lubricating oil has flowed through annular gap between the shafts to supply the lubrication point and wherein in the annular gap at least one conveying member is arranged with a helical profiling for a lubricating oil promoting effect.
Hintergrund der Erfindung DE 37 05 064 C2 zeigt eine gattungsbildende Getriebevorrichtung mit einer Schmiereinrichtung. Die Getriebevorrichtung ist ein als Planetengetriebe ausgebildetes Differenzial mit einer Eingangswelle, auf der drehbar ein Planetenträger sitzt. Die Planetenräder des Planetengetriebes kämmen außen mit einem Hohlrad, welches mit einer Ausgangswelle verbunden ist. Innen kämmen die Planetenräder mit einem Sonnerad. Das Sonnenrad ist am Ende einer zur Eingangswelle koaxialen Hohlwelle ausgebildet, in der die Eingangswelle steckt. BACKGROUND OF THE INVENTION DE 37 05 064 C2 shows a generic transmission device with a lubrication device. The transmission device is designed as a planetary gear differential with an input shaft on which rotatably a planet carrier sits. The planet gears of the planetary gear mesh externally with a ring gear, which is connected to an output shaft. Inside, the planetary gears mesh with a sunbathing wheel. The sun gear is formed at the end of a hollow shaft coaxial with the input shaft, in which the input shaft is inserted.
Die Schmiereinrichtung weist eine Ölfangrinne auf, in der Spritzöl einer Kette gefangen wird. Das aufgefangene Schmieröl rinnt aus der Ölfangrinne in einen Ringraum, der die innere Welle umgibt. Die Schmiervorrichtung weist weiter einen Ringspalt auf, der zwischen den Ringspalt der ineinander gesteckten Wellen gebildet ist. Über diesen Ringspalt kann Schmieröl zu Lagerstellen der Wellen und Planetenräder sowie zum Zahnkontakt im Planetengetriebe gefördert werden. The lubrication device has an oil gutter in which spray oil of a chain is caught. The trapped lubricating oil drains from the oil gutter into an annulus surrounding the inner shaft. The lubricating device further has an annular gap which is formed between the annular gap of the nested waves. About this annular gap can lubricating oil to bearings of the Shafts and planetary gears as well as tooth contact in the planetary gear be promoted.
Das Schmieröl wird in der gattungsgemäßen Getriebevorrichtung mittels eines Fördergliedes durch den Ringspalt gefördert. Das Förderglied ist eine Hülse, die einen zylindrischen Abschnitt mit schraubenlinienförmiger Profilierung aufweist und relativ zum Gehäuse der Getriebevorrichtung fest ist. Diese Profilierung ist innen an dem Abschnitt der Hülse ausgebildet, der in dem Ringspalt angeordnet ist. Sie besteht aus rippenartigen Erhebungen und liegt der inneren Welle an einem Spalt gegenüber. Die Profilierung wirkt bei Rotation der inneren Welle im Zusammenwirken mit der Oberfläche der inneren Welle wie eine Förderschnecke, die das an der rotierenden inneren Welle anhaftende Schmieröl in dem Ringspalt in axiale Richtung fördert. Bei hohen Drehzahlen der inneren Welle wird relativ hoher Schmieröldruck in dem Schmierkanal auf- gebaut, so dass über diesen die Schmierstellen im Planetengetriebe ausreichend versorgt werden können. The lubricating oil is conveyed in the generic transmission device by means of a conveyor member through the annular gap. The conveying member is a sleeve having a cylindrical portion with helical profiling and fixed relative to the housing of the transmission device. This profiling is formed on the inside of the portion of the sleeve, which is arranged in the annular gap. It consists of rib-like elevations and lies opposite the inner shaft at a gap. The profiling acts upon rotation of the inner shaft in cooperation with the surface of the inner shaft like a screw conveyor, which promotes the adhering to the rotating inner shaft lubricating oil in the annular gap in the axial direction. At high speeds of rotation of the inner shaft, relatively high lubricating oil pressure is built up in the lubricating channel, so that the lubrication points in the planetary gear can be adequately supplied via this.
Steckwellenanordnungen gewinnen zunehmend in modernen Getriebevorrichtungen an Bedeutung, so wie die in Getriebevorrichtungen für Add - On - Hyb- ridantrieben oder wie die in Doppelkupplungsgetrieben. In Add - On - Hybridantrieben wird ein mechanisches Getriebe, beispielsweise ein Differenzial oder ein Verteilergetriebe außer von dem Verbrennungsmotor oder vom Fahrzeuggetriebe auch noch im sogenannten„Add - On - Betrieb" wahlweise elektromotorisch angetrieben. Der für den Antrieb erforderliche Elektromotor kann aus Bauraumgründen in koaxialer Bauweise zur Eingangswelle bzw. Ausgangswelle der Getriebevorrichtung angeordnet sein. Die Rotorwelle des Elektromotors ist in diesen Anordnungen eine wahlweise antreibende Hohlwelle, in die die Eingangswelle bzw. Ausgangswelle gesteckt ist. In Doppelkupplungsgetrieben stecken beispielsweise zwei voneinander unabhängig antreibbare Eingangs- wellen eines Getriebes ineinander. Throttle shaft arrangements are becoming increasingly important in modern transmission devices, such as those in transmission devices for add-on hybrid drives or in dual-clutch transmissions. In add - on hybrid drives, a mechanical transmission, for example a differential or a transfer case, is also driven by an electric motor in addition to the internal combustion engine or the vehicle transmission in the so - called "add - on mode." The electric motor required for the drive can be made coaxial for reasons of space In these arrangements, the rotor shaft of the electric motor is an optionally driving hollow shaft in which the input shaft or output shaft is plugged in. In dual-clutch transmissions, for example, two input shafts of a transmission which can be driven independently of one another are inserted into one another.
In beiden zuvor beschriebenen Anordnungen können die koaxial ineinander steckenden Wellen an Lagerstellen aneinander abgestützt sein. Oft ist die Schmierölversorgung dieser Lagerstellen über die Steckwellenanordnung zu anderen Lagerstellen schwierig, insbesondere dann, wenn die Lagerstellen Wälzlager sind. Aufgrund der niedrigen radialen Bauweise werden an diesen Lagerstellen vorzugsweise Nadellager eingesetzt. Nadellager zeichnen sich durch niedrige Bauweise aus, da der Durchmesser der als Nadeln bezeichneten Rollen relativ zu ihrer Länge gering ist. Von Vorteil wäre es, wenn die Nadellager an den Lagerstellen auf Dauer mit Schmierfett befüllt werden könnten. Das geht jedoch nur in Anordnungen, in denen die Nadellager geringen Betriebsdrehzahlen ausgesetzt werden und abgedichtet sind. Bei hohen Drehzah- len kann durch die Linienberührung der Nadeln im Wälzkontakt eine ausreichende Fettlebensdauer nicht in jedem Fall abgesichert werden. Die Nadellager müssen deshalb mit Schmieröl versorgt werden. Der relativ geringe Durchlassquerschnitt der Wälzlager und deren Sitz tief in dem Ringspalt macht es schwierig, diese ausreichend mit Schmieröl zu versorgen. Außerdem können die Ringspalte zwischen den ineinander steckenden Wellen als Schmierkanäle vorgesehen sein, über die es aufgrund deren Länge und geringem Querschnitt schwierig ist, Schmieröl zu anderen Schmierstellen zu transportieren. Oftmals kann deshalb auf eine Druckölversorgung mittels Pumpe nicht verzichtet werden. In both arrangements described above, the coaxial nested shafts may be supported at bearings. Often that is Lubricating oil supply of these bearings on the stub shaft assembly to other bearings difficult, especially if the bearings are rolling bearings. Due to the low radial design needle bearings are preferably used at these bearings. Needle bearings are characterized by low construction, since the diameter of the rollers called needles is low relative to their length. It would be advantageous if the needle bearings could be filled at the bearings permanently with grease. However, this is only possible in arrangements in which the needle roller bearings are exposed to low operating speeds and sealed. At high speeds, the line contact of the needles in the rolling contact does not always ensure sufficient grease life. The needle bearings must therefore be supplied with lubricating oil. The relatively small passage cross-section of the rolling bearings and their seat deep in the annular gap makes it difficult to provide them sufficiently with lubricating oil. In addition, the annular gaps between the nested shafts can be provided as lubrication channels, over which it is difficult due to their length and small cross-section to transport lubricating oil to other lubrication points. Often therefore can not be dispensed with a pressure oil supply by pump.
Aufgabe der Erfindung Object of the invention
Die Aufgabe der Erfindung ist es daher, eine Getriebevorrichtung mit einer effektiven Schmiereinrichtung zu schaffen, mit der die Versorgung schwer zu- gänglicher Schmierstellen über Ringspalte von Steckwellenanordnungen ausreichend versorgt werden können und die sich kostengünstig herstellen lässt. The object of the invention is therefore to provide a transmission device with an effective lubrication device, with which the supply of hard-to-reach lubrication points can be adequately supplied via annular gaps of plug-shaft assemblies and which can be produced inexpensively.
Zusammenfassung der Erfindung Die Aufgabe ist nach den Merkmalen des Anspruchs 1 gelöst. Summary of the Invention The object is solved according to the features of claim 1.
Die Erfindung betrifft alle Getriebevorrichtung mit mindestens zwei Wellen, die zu einer gemeinsamen Rotationsachse koaxial ineinander gesteckt sind, von denen eine erste Welle als Hohlwelle ausgeführt ist und von denen eine zweite Welle in der ersten Welle steckt. Das betrifft beispielsweise Anordnungen in Doppelkupplungsgetrieben, Verteilergetrieben, Differenzialen und in Getrieben mit mehren Antrieben. The invention relates to all transmission device with at least two shafts, which are inserted coaxially into one another to a common axis of rotation of where a first shaft is designed as a hollow shaft and of which a second shaft is inserted in the first shaft. This applies, for example, arrangements in dual-clutch transmissions, transfer cases, and differentials in transmissions with multiple drives.
Die teilweise oder vorwiegend über die gesamte Länge ineinander gesteckten Wellen sind beide antreibende Wellen oder eine ist antreibende Welle und eine ist eine angetriebenen Welle bzw. beide sind angetriebenen Wellen zwischen denen einen von Schmieröl durchflossenen Ringspalt zur Versorgung wenigstens einer Schmierstelle ausgebildet ist. The partially or predominantly nested over the entire length shafts are both driving shafts or a driving shaft and one is a driven shaft or both are driven shafts between which an oil-flowing through an annular gap for supplying at least one lubrication point is formed.
In dem Ringspalt ist wenigstens eine schraubenlinienförmige Profilierung mit einer Schmieröl fördernden Wirkung angeordnet. Erfindungsgemäß ist die schraubenförmige Profilierung in dem Ringspalt um die gemeinsame Rotati- onsachse der Wellen separat zu wenigstens einer der Wellen rotierbar. Mit anderen Worten, das Förderglied, das die schraubenlinienförmige Profilierung aufweist, ist selbst um die Rotationsachse und zu wenigstens einer der Wellen rotierbar in der Getriebevorrichtung aufgenommen. Die schraubenlinienförmigen Profilierung sind nach der Art von Schneckenförderern, Exzenter-Schneckenförderern oder Schraubenspindelförderern als schraubenlinien-(=gewinde-) oder schneckenförmig an einem Zylinder oder an Konus um die Rotationsachse windende Rippen oder Nuten, alternativ auch als Kombinationen dieser zu verstehen. Diese Rippen oder Nuten korrespondieren mit einer zylindrischen Oberfläche oder mit korrespondierenden schnecken- bzw. schraubenlinienförmig gestalteten Oberflächen einer der Wellen, eines Gehäuses oder einer anderen beliebigen zylindrischen Fläche. Sie korrespondieren so, dass diese miteinander zusammenwirkend geeignet sind, bei Rotation die axiale Förderung von Schmieröl in dem Spalt zu bewirken. Es ist von Vorteil, dass derartige Profilierungen so ausgelegt werden können, dass diese auch fördern, wenn sich deren Drehrichtung um die Rotationsachse umkehrt. Der Vorteil derartiger Anordnungen besteht insbesondere darin, dass der mit dieser Profilierung geförderte Volumenstrom nicht nur von der Drehzahl einer der Wellen alleine abhängig ist, sondern über das selbst rotierende Förderglied beeinflusst, zum Beispiel verstärkt, werden kann. At least one helical profiling with a lubricating oil promoting action is arranged in the annular gap. According to the invention, the helical profiling in the annular gap is rotatable about the common axis of rotation of the shafts separately from at least one of the shafts. In other words, the conveyor member having the helical profiling is itself rotatably received in the transmission device about the axis of rotation and to at least one of the shafts. The helical profiling is to be understood by the nature of screw conveyors, eccentric screw conveyors or screw-spindle conveyors as helical (= thread) or helical on a cylinder or cone around the axis of rotation spiraling ribs or grooves, alternatively as combinations thereof. These ribs or grooves correspond with a cylindrical surface or with corresponding helical surfaces of one of the shafts, a housing or any other cylindrical surface. They correspond so that they cooperate with each other to effect upon rotation, the axial promotion of lubricating oil in the gap. It is advantageous that such profilings can be designed so that they also promote when reversing the direction of rotation about the axis of rotation. The advantage of such arrangements is, in particular, that the volume flow delivered with this profiling is not only dependent on the rotational speed of one of the shafts but is influenced, for example amplified, by the self-rotating conveyor member.
Außerdem kann mit dieser Anordnung auch Schmieröl gefördert werden, wenn die Welle steht. In diesem Zusammenhang sieht eine Ausgestaltung der Erfindung vor, dass die schraubenförmige Profilierung bzw. das Förderglied um die Rotationsachse rotierend antreibbar ist. So ist es denkbar, dass das Förder- glied mit der Profilierung mit einen separaten Antrieb angetrieben ist. Dadurch ist der Antrieb der Fördereinrichtung unabhängig vom Stillstand oder der Drehzahl einer der Wellen. In addition, with this arrangement, lubricating oil can be promoted when the shaft is stationary. In this context, an embodiment of the invention that the helical profiling or the conveying member is driven to rotate about the axis of rotation. So it is conceivable that the conveyor member is driven with the profiling with a separate drive. As a result, the drive of the conveyor is independent of standstill or the speed of one of the waves.
Eine weitere Ausgestaltung der Erfindung sieht vor, dass die schraubenförmige Profilierung bzw. das Förderglied mittels wenigstens eines Zahnrades antreibbar ist, wobei das Zahnrad drehbar an einer der Wellen gelagert ist. Ein derartiger Antrieb ist insbesondere dann von Vorteil, wenn das Zahnrad drehfest mit der ersten Welle verbunden ist. Da in diesem Fall die erste Welle eine angetriebene oder antreibende Welle ist, ist auch bei Stillstand der zweiten inneren Welle die Versorgung mit Schmieröl abgesichert. A further embodiment of the invention provides that the helical profiling or the conveying member is drivable by means of at least one gear, wherein the gear is rotatably mounted on one of the shafts. Such a drive is particularly advantageous if the gear is rotatably connected to the first shaft. Since, in this case, the first shaft is a driven or driving shaft, the supply of lubricating oil is ensured even when the second inner shaft is at a standstill.
Es ist auch von Vorteil, wenn das Zahnrad in einem Leistungsstrang der Getriebevorrichtung angeordnet ist. In diesem Fall ist kein gesonderter Antrieb des Förderglieds nötig, da der Antrieb durch der Getriebevorrichtung zugeführ- te Leistung abgesichert ist. Eine weitere Ausgestaltung der Erfindung sieht vor, dass das Zahnrad ein Sonnenrad eines Planetentriebs der Getriebevorrichtung ist. Diese Anordnung ist insbesondere dann von Vorteil, wenn das Sonnenrad fest mit der ersten Welle verbunden ist, und die erste Welle die Rotorwelle des Elektromotors ist. In diesem Fall wird je nach Leistungsfluss das Förderglied entweder durch den Elektromotor oder durch Leistung aus dem Planetengetriebe angetrieben. Letzteres trifft zum Beispiel zu, wenn der Rotor mitgeschleppt und der Elektromotor als Bremse oder Generator genutzt wird. Alternativ wird bei Stillstand des Sonnenrades die Förderwirkung durch Drehzahl der anderen Welle aufrecht erhalten. Letzteres trifft zu, wenn die Profilierung zur inneren Welle gerichtet ist und mit deren Oberfläche Schmieröl fördernd korrespondiert. Beschreibung der Zeichnungen It is also advantageous if the gear is arranged in a power train of the transmission device. In this case, no separate drive of the conveyor link is necessary because the drive is protected by the power supplied by the gear device. A further embodiment of the invention provides that the gear is a sun gear of a planetary gear of the transmission device. This arrangement is particularly advantageous when the sun gear is fixedly connected to the first shaft, and the first shaft is the rotor shaft of the electric motor. In this case, depending on the power flow, the conveying member is driven either by the electric motor or by power from the planetary gear. The latter applies, for example, when the rotor is dragged along and the electric motor is used as brake or generator. Alternatively, at standstill of the sun gear, the conveying effect by speed the other wave maintained. The latter is true when the profiling is directed to the inner shaft and lubricating oil corresponds with the surface thereof. Description of the drawings
Die Erfindung wird nachfolgend anhand von Ausführungsbeispielen näher beschrieben. Figur 1 zeigt einen Teilschnitt eines vereinfacht dargestellten Getriebevorrichtung 1 mit einem Planetengetriebe eines Differenzials mit einem Elektromotor 2. Das Planetengetriebe ist zeichnerisch teilweise mit dem Sonnenrad 3 und mit Planetenrädern 4 abgebildet. Ein Rotor 5 des Elektromotors 2 sitzt auf einer ersten Welle 6. Die erste Welle 6 ist mittels Schrägkugellagern 7 und 8 in dem Gehäuse 9 der Getriebevorrichtung 1 drehbar gelagert. The invention will be described in more detail below with reference to exemplary embodiments. Figure 1 shows a partial section of a transmission device 1 shown in simplified form with a planetary gear of a differential with an electric motor 2. The planetary gear is shown partially with the sun gear 3 and planetary gears 4. A rotor 5 of the electric motor 2 is seated on a first shaft 6. The first shaft 6 is rotatably supported in the housing 9 of the transmission device 1 by means of angular contact ball bearings 7 and 8.
Die erste Welle 6 ist innen hohl und weist ein Durchgangsloch 17 auf. In dem Durchgangsloch 17 ist das Sonnenrad 3 drehfest befestigt. Das Sonnenrad 3 steht mit einem Zahnrad 15 mit den Planetenrädern 4 im Zahneingriff, die in dem Leistungsstrang des Differenzials integriert sind und weist einen Schaft 16 auf. Der Schaft 16 und das Zahnrad 15 sind innen hohl. The first shaft 6 is hollow inside and has a through hole 17. In the through hole 17, the sun gear 3 is rotatably attached. The sun gear 3 is meshed with a gear 15 with the planetary gears 4, which are integrated in the power train of the differential and has a shaft 16. The shaft 16 and the gear 15 are hollow inside.
Eine zweite Welle 12 steckt in dem Durchgangsloch 17 der ersten Welle 6 und einem Durchgangsloch 18 des Sonnenrades 3 und ist an zwei Lagerstellen 10 und 1 1 in der ersten Welle 6 drehbar gelagert,. Die Lagerstellen 10 und 1 1 weisen jeweils ein als Nadellager 13 und 14 ausgebildetes Wälzlager auf. Die Nadellager 13 und 14 sind jeweils aus einer Hülse 19 und aus Wälzkörpern 20 in Form von Nadeln gebildet. Zwischen der ersten Welle 6 und der zweiten Welle 12 ist ein Ringspalt 21 ausgebildet. Ein weiterer Ringspalt 22 zwischen dem Sonnenrad 3 und der zweiten Welle 12 ausgebildet. Der Querschnitt des Ringspalts 22 ist kleiner als der Querschnitt des Ringspalts 21 . Der rotationssymmetrische Schaft 16 des Sonnenrades 3 ist ein Förderglied 23, das zwecks Förderung von Schmieröl innen in dem Durchgangsloch 18 mit einer schraubenförmigen Profilierung 24 versehen ist, die der zweiten Welle 12 zugewandt ist und um diese umläuft. Die Strömungsrichtung des Schmieröls ist mittels der Richtungspfeile angegeben. A second shaft 12 is inserted in the through hole 17 of the first shaft 6 and a through hole 18 of the sun gear 3 and is rotatably supported at two bearings 10 and 1 1 in the first shaft 6,. The bearings 10 and 1 1 each have a designed as a needle bearing 13 and 14 bearings. The needle bearings 13 and 14 are each formed of a sleeve 19 and 20 of rolling elements in the form of needles. Between the first shaft 6 and the second shaft 12, an annular gap 21 is formed. Another annular gap 22 between the sun gear 3 and the second shaft 12 is formed. The cross section of the annular gap 22 is smaller than the cross section of the annular gap 21. The rotationally symmetrical shaft 16 of Sun gear 3 is a conveying member 23 which is provided for conveying lubricating oil inside in the through hole 18 with a helical profiling 24 which faces the second shaft 12 and rotates about this. The flow direction of the lubricating oil is indicated by means of the directional arrows.
Das Sonnenrad 3 ist mit den Figuren 2 und 3 als Einzelteil in unterschiedlichen Ansichten dargestellt. Figur 4 zeigt einen Schnitt durch das Sonnenrad 3 längs entlang der Rotationsachse. Die schraubenförmige Profilierung an der Innenseite des Schafts 16 ist eine spiralförmig verlaufende Nut 30, die bei Drehung der zweiten Welle 12 bei Vorwärtsfahrt in eine Drehrichtung mit beispielsweise hohen Drehzahlen, auch durch Relativdrehzahlen der beiden Wellen zueinander, axial in Richtung der Schmierstellen 27 und 28 fördert. The sun gear 3 is shown with the figures 2 and 3 as a single part in different views. FIG. 4 shows a section through the sun gear 3 along the axis of rotation. The helical profiling on the inside of the shaft 16 is a spirally extending groove 30, which promotes axially in the direction of the lubrication points 27 and 28 upon rotation of the second shaft 12 in forward rotation in a direction of rotation with, for example, high speeds, even by relative speeds of the two shafts ,
Das Förderglied 23 ist mit der schraubenförmigen Profilierung 24 in dem Ring- spalt 21 um die gemeinsame Rotationsachse 25 der Wellen 6 und 12 rotierbar angeordnet und wird bei Betrieb des Elektromotors 2 mittels der als Rotorwelle ausgebildeten ersten Welle 6 angetrieben. Alternativ ist das Förderglied 23, das einteilig mit dem Zahnrad 15 ausgebildet ist und seitlich von diesem abgeht, durch das Planetengetriebe und damit durch das Zahnrad 15 angetrie- ben. Schmieröl gelangt über das Wellenende 26 in den Ringspalt 22 und wird von dort durch die Förderwirkung der schraubenförmigen Profilierung 24 in den Ringspalt 21 und zu den Schmierstellen 27 und 28 gefördert, die die Lagerstellen 10 und 1 1 sind und deren Querschnitt enger ist als der Querschnitt des Ringspalts 22. Das Schmieröl wird über die Querbohrungen 29 in den Schmier- kanal 35 und von dort in das Planetengetriebe zurück gefördert. The conveying member 23 is rotatably arranged with the helical profiling 24 in the annular gap 21 about the common axis of rotation 25 of the shafts 6 and 12 and is driven during operation of the electric motor 2 by means of the first shaft 6 designed as a rotor shaft. Alternatively, the conveying member 23, which is formed integrally with the gear 15 and extends laterally therefrom, driven by the planetary gear and thus by the gear 15 ben. Lubricating oil passes through the shaft end 26 into the annular gap 22 and is conveyed from there by the conveying action of the helical profiling 24 in the annular gap 21 and the lubrication points 27 and 28, which are the bearings 10 and 1 1 and whose cross section is narrower than the cross section of the annular gap 22. The lubricating oil is conveyed via the transverse bores 29 into the lubricating channel 35 and from there into the planetary gearbox.
Figur 5 zeigt eine alternative Ausbildung eines Sonnenrades 31 , bei dem die schraubenförmige Profilierung 24 und damit die Nut 30 nicht unmittelbar an einem Schaft, sondern an einer gesonderten Hülse 33 ausgebildet ist. Die Hül- se 33 ist in das Durchgangsloch 32 eingepresst. Ein derartig ausgebildetes Sonnenrad 31 lässt sich unter Umständen leichter herstellen, da die Nut 30 nicht unmittelbar beispielsweise spanabhebend in den Schaft 34 eingebracht werden muss, sondern beispielsweise an einer durch Rollieren von Blech hergestellten Hülse 33 ausgebildet ist. Figure 5 shows an alternative embodiment of a sun gear 31, wherein the helical profiling 24 and thus the groove 30 is not formed directly on a shaft, but on a separate sleeve 33. The sleeve 33 is pressed into the through hole 32. Under certain circumstances, a sun gear 31 designed in this way can be produced more easily, since the groove 30 is not introduced into the shaft 34, for example, by machining, for example must be, but is formed, for example, on a sleeve 33 produced by rolling sheet metal.
Bezugszeichenliste LIST OF REFERENCE NUMBERS
Getriebevorrichtung 21 RingspaltGear device 21 Annular gap
Elektromotor 22 RingspaltElectric motor 22 Annular gap
Sonnenrad 23 FördergliedSun gear 23 conveyor link
Planetenrad 24 ProfilierungPlanetary wheel 24 profiling
Rotor 25 Rotationsachse erste Welle 26 WellenendeRotor 25 Rotation axis First shaft 26 Shaft end
Schrägkugellager 27 SchmierstelleAngular contact ball bearings 27 Lubrication point
Schrägkugellager 28 SchmierstelleAngular contact ball bearing 28 Lubrication point
Gehäuse 29 QuerbohrungHousing 29 Cross hole
Lagerstelle 30 Nut Bearing point 30 groove
Lagerstelle 31 Sonnenrad zweite Welle 32 Durchgangsloch Bearing 31 Sun gear second shaft 32 through hole
Nadellager 33 Hülse Needle roller bearing 33 sleeve
Nadellager 34 Schaft  Needle bearing 34 shank
Zahnrad 35 Schmierkanal Gear 35 lubrication channel
Schaft shaft
Durchgangsloch  Through Hole
Durchgangsloch  Through Hole
Hülse  shell
Wälzkörper  rolling elements

Claims

Patentansprüche claims
Getriebevorrichtung (1 ) mit mindestens zwei Wellen (6, 12), die zu einer gemeinsamen Rotationsachse (25) koaxial sind, von denen eine erste Welle (6) als Hohlwelle ausgeführt ist und von denen eine zweite Welle (12) in der ersten Welle (6) angeordnet ist, wobei die Getriebevorrichtung (1 ) wenigstens eine Schmierstelle (27, 28) und mindestens einen von Schmieröl durchflossenen Ringspalt (21 , 22) zwischen den Wellen (6, 12) zur Versorgung der Schmierstelle (27, 28) aufweist und wobei in dem Ringspalt (21 , 22) wenigstens ein Förderglied (23) mit einer schrau- benlinienförmige Profilierung (24) für eine Schmieröl fördernden Wirkung angeordnet ist, dadurch gekennzeichnet, dass das Förderglied (23) mit der schraubenlinienförmige Profilierung (24) in dem Ringspalt (21 , 22) um die gemeinsame Rotationsachse (25) der Wellen (6, 12) separat zu wenigstens einer der Wellen (12) rotierbar ist. Transmission device (1) with at least two shafts (6, 12), which are coaxial to a common axis of rotation (25), of which a first shaft (6) is designed as a hollow shaft and of which a second shaft (12) in the first shaft (6), wherein the transmission device (1) has at least one lubrication point (27, 28) and at least one annular gap (21, 22) through which lubricating oil flows between the shafts (6, 12) for supplying the lubrication point (27, 28) and wherein in the annular gap (21, 22) at least one conveying member (23) is arranged with a screw-line profiling (24) for a lubricating oil-promoting effect, characterized in that the conveying member (23) with the helical profiling (24) in the annular gap (21, 22) is rotatable about the common axis of rotation (25) of the shafts (6, 12) separately from at least one of the shafts (12).
Getriebevorrichtung nach Anspruch 1 , dadurch gekennzeichnet, dass das Förderglied (23) mit schraubenlinienförmiger Profilierung (24) um die Rotationsachse (25) rotierend antreibbar ist. Transmission device according to claim 1, characterized in that the conveying member (23) with helical profiling (24) about the rotation axis (25) is driven to rotate.
Getriebevorrichtung nach Anspruch 2, dadurch gekennzeichnet, dass das Förderglied (23) mittels wenigstens eines Zahnrades (15) antreibbar ist, wobei das Zahnrad (15) drehbar an einer der Wellen (6, 12) gelagert ist. Transmission device according to claim 2, characterized in that the conveying member (23) by means of at least one gear (15) is drivable, wherein the gear (15) is rotatably mounted on one of the shafts (6, 12).
Getriebevorrichtung nach Anspruch 3, dadurch gekennzeichnet, dass das Zahnrad (15) drehfest mit der ersten Welle (6) verbunden ist. Transmission device according to claim 3, characterized in that the gear (15) is non-rotatably connected to the first shaft (6).
Getriebevorrichtung nach Anspruch 3, dadurch gekennzeichnet, dass das Zahnrad (15) in einem Leistungsstrang der Getriebevorrichtung (1 ) angeordnet ist. Transmission device according to claim 3, characterized in that the gear (15) in a power train of the transmission device (1) is arranged.
Getriebevorrichtung nach Anspruch 5, dadurch gekennzeichnet, dass das Zahnrad (15) ein Sonnenrad (3) eines Planetentriebs der Getriebevorrichtung (1 ) ist. Transmission device according to claim 5, characterized in that the gear (15) is a sun gear (3) of a planetary drive of the transmission device (1).
7. Getriebevorrichtung nach Anspruch 5, dadurch gekennzeichnet, dass das Zahnrad (15) elektromotorisch antreibbar ist. 7. Transmission device according to claim 5, characterized in that the gear (15) is driven by an electric motor.
8. Getriebevorrichtung nach Anspruch 5, dadurch gekennzeichnet, dass das Zahnrad (15) elektromotorisch antreibbar ist, wobei das Zahnrad (15) mit der ersten Welle (6) drehfest verbunden ist. 8. Transmission device according to claim 5, characterized in that the gear (15) is driven by an electric motor, wherein the gear (15) with the first shaft (6) is rotatably connected.
9. Getriebevorrichtung nach Anspruch 8, dadurch gekennzeichnet, dass die erste Welle (6) eine Rotorwelle eines Elektromotors(2) ist. 9. Transmission device according to claim 8, characterized in that the first shaft (6) is a rotor shaft of an electric motor (2).
10. Getriebevorrichtung nach Anspruch 3, dadurch gekennzeichnet, dass die schraubenlinienförmige Profilierung (24) innen an einem rotationssymmetrischen Abschnitt des Fördergliedes (23) ausgebildet ist, der seitlich von dem Zahnrad (15) abgeht und zumindest teilweise in dem Ringspalt (21 ) zwischen der ersten Welle (6) und der zweiten Welle (12) die zweite Welle (12) umgreift. 10. Transmission device according to claim 3, characterized in that the helical profiling (24) is formed on the inside at a rotationally symmetrical portion of the conveying member (23), the side of the gear (15) goes off and at least partially in the annular gap (21) between the first shaft (6) and the second shaft (12) engages around the second shaft (12).
1 1 . Getriebevorrichtung nach Anspruch 10, dadurch gekennzeichnet, dass die schraubenlinienförmige Profilierung (24) innen an dem Abschnitt und dabei der zweiten Welle (12) zugewandt ausgebildet ist. 1 1. Transmission device according to claim 10, characterized in that the helical profiling (24) is formed on the inside of the section and thereby the second shaft (12) facing.
12. Getriebevorrichtung nach Anspruch 10, dadurch gekennzeichnet, dass die schraubenlinienförmige Profilierung (24) eine um die zweite Welle (12) verlaufende spiralförmige Nut (30) in dem Abschnitt ist. 12. Transmission device according to claim 10, characterized in that the helical profiling (24) around the second shaft (12) extending helical groove (30) in the section.
13. Getriebevorrichtung nach Anspruch 1 , dadurch gekennzeichnet, dass die Schmierstelle (27,28) wenigstens ein Wälzlager aufweist, mit dem die Wellen (6, 12) aneinander gelagert sind, wobei das Wälzlager in dem Schmierspalt (21 ) angeordnet ist. 13. Transmission device according to claim 1, characterized in that the lubrication point (27,28) comprises at least one rolling bearing, with which the shafts (6, 12) are mounted to each other, wherein the rolling bearing in the lubrication gap (21) is arranged.
14. Getriebevorrichtung nach Anspruch 13, dadurch gekennzeichnet, dass der Durchlassquerschnitt des Wälzlagers für das Schmieröl kleiner ist als es der Förderquerschnitt der schraubenlinienförmigen Profilierung (24) für das Schmieröl ist. 14. Transmission device according to claim 13, characterized in that the passage cross section of the rolling bearing for the lubricating oil is smaller than the conveying cross section of the helical profiling (24) for the lubricating oil.
PCT/EP2010/063831 2009-10-28 2010-09-21 Transmission device WO2011051055A1 (en)

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