DE102021132892A1 - planetary gear arrangement - Google Patents

Abstract

It is an object of the present invention to propose a planetary gear arrangement with a simplified oil supply. A planetary gear arrangement 1 with a sun gear unit 2, the sun gear unit having a sun gear 3 and a sun shaft 4, is proposed with a planet carrier 6, the planet carrier 6 having a first carrier cheek 7 and a second carrier cheek 70, and with at least one planet wheel 8 and a planet bolt 9, the planet wheel 8 being rotatably arranged on the planet bolt 9 via a bearing 10 and meshing with the sun wheel 3, with a main supply path 19 for an oil supply of the bearing 10, the main supply path 19 being divided into a first and a second partial supply path 20,21, the first partial supply path 20 starting from the oil supply via a first axial sun side area 22 of the sun wheel 3 and the second partial supply path 21 starting from the oil supply via a second axial sun side area 25 of sun gear 3, with first partial supply path 20 leading to bearing 10 via a first lubricating gap 23 located between first carrier cheek 7 and planet gear 8 and/or that second partial supply path 21 via a second lubricating gap 230 located between the second carrier cheek 70 and the planet gear 8 to the storage 10 leads.

Description

The invention relates to a planetary gear arrangement having the features of the preamble of claim 1

Planetary gears usually have a planetary carrier with planetary gears arranged thereon eccentrically and offset relative to one another in the direction of rotation. The planet gears are often mounted on bolts, with the mounting being implemented either with a plain bearing or a rolling element bearing. The bearings are lubricated with gear oil, especially in vehicle transmissions. To ensure that there is sufficient lubrication at all times, the bearings form lubricated components in the oil circuits of the vehicle transmission. Since the planetary carrier with the planetary gears arranged on it rotates about a central axis of the planetary carrier, the lubrication of the bearings rotating with it is correspondingly demanding. One possible design provides that the bolts are designed as hollow bolts and the transmission oil is routed to the bearings via the hollow bolts.

The pamphlet US2016146332A1 , which probably forms the closest prior art, discloses a planetary gear with a planetary carrier and planetary gears arranged thereon. The planet carrier sits on a shaft which is designed as a hollow shaft. This hollow shaft has at least one radial passage, which distributes the transmission oil from the hollow shaft in the radial direction. The transmission oil flows around a sun gear, which meshes with the planet gears of the planet carrier. On both sides of the planetary carrier, oil-collecting shells are arranged, which catch the gear oil moved by centrifugal force and lead axially on the face side to the bolts of the planetary gears, which are designed as hollow bolts. The transmission oil is fed into the hollow bolts via the oil drip trays and from there via cross bores to the bearings for lubrication.

It is an object of the present invention to propose a planetary gear arrangement with a simplified oil supply. This object is achieved by a planetary gear arrangement having the features of claim 1. Preferred or advantageous embodiments of the invention result from the dependent claims, the following description and the attached figures.

The subject matter of the invention is a planetary gear arrangement which is particularly suitable and/or designed for a vehicle. The planetary gear arrangement can form part of a vehicle transmission, in particular a manual transmission, an automatic transmission, a reduction gear, a step-up gear, a summation gear or a differential gear. In particular, the planetary gear arrangement is designed to transmit a traction torque of the vehicle. For example, the planetary gear arrangement is designed as part of a drive train of an electric drive, in particular an electric axle, or of a hybrid drive train.

The planetary gear arrangement has a sun gear unit. The sun wheel unit defines a main axis of rotation with its axis of rotation. The sun gear unit has a sun gear and a sun shaft, the sun gear being arranged on the sun shaft. The sun wheel and the sun shaft can be designed in one piece, in particular from a common material section. As an alternative to this, the sun wheel can be placed on the sun shaft. The sun gear carries face gearing, which can be designed, for example, as straight gearing or as helical gearing

The planetary gear arrangement has a planet carrier, the planet carrier comprising a first carrier cheek and a second carrier cheek.

In particular, a housing is formed by the planet carrier. The carrier cheeks can each be implemented continuously or only in sections. The carrier cheeks can each be designed in one piece or in multiple pieces. Furthermore, the planetary carrier has at least one planetary gear, preferably several planetary gears, for example three or four planetary gears, and a corresponding number of planetary bolts which connect the carrier cheeks. For example, the planetary bolts are fixed in or on the first carrier cheek and in or on the second carrier cheek. The planet wheel is rotatably arranged on the planet pin via a bearing. The bearing can be designed, for example, as a sliding bearing or as a rolling element bearing. The bearing is preferably implemented as a needle bearing device. The planetary gears with the planetary pin are preferably regularly distributed in the direction of rotation in a pitch circle diameter around the main axis of rotation. One set of planet gears, alternatively several sets, in particular two sets, of planet gears can be provided. The planet gears mesh with the sun gear. In particular, the planetary gears have spur gearing, which can be implemented as spur gearing or helical gearing to match the sun gear, for example.

The planetary gear arrangement has a main supply path for supplying oil to the bearing, in particular to the majority, in particular all of the bearings of the planet gears. A large part, in particular at least 70%, preferably at least 80% and in particular at least 90%, of the transmission oil, which lubricates the bearing or bearings, is preferably transported via the main supply route.

The main supply path is supplied with the transmission oil via an oil feed, the oil feed being provided radially on the inside of the sun gear unit. The sun shaft can be designed as a hollow shaft, for example, with the oil being supplied via the interior or partial areas of the interior of the hollow shaft.

It is provided that the main supply path is preferably divided exclusively into a first and a second partial supply path. Starting from the oil supply, the first partial supply path runs via a first axial sun side area of the sun gear, ie in particular in an area axially next to the sun gear on a first axial side of the sun gear. Starting from the oil feed, the second partial supply path runs via a second axial sun side area of the sun gear, ie via an axial area which is arranged on a second axial side of the sun gear.

In the context of the invention, it is proposed that the first partial supply path leads via at least one first lubricating gap, the at least first lubricating gap being arranged between the first carrier cheek and the planet gear and the at least first lubricating gap being fluidically connected to the bearing. Alternatively or in addition, it is proposed that the second partial supply path leads via at least one second lubricating gap, the at least second lubricating gap being arranged between the second carrier cheek and the planet gear and the second lubricating gap being fluidically connected to the bearing. It is thus proposed in particular that the first and the second partial supply path in particular run as intended between the carrier cheek and the planet wheel and, starting from the lubricating gap, lead directly to the bearing. The lubricating gap extends in particular in a radial plane to the main axis of rotation.

The oil flow within the planetary gear arrangement, in particular the wheel set, is adjusted so that the oil is no longer directed past the planet carrier into an oil drip tray or an oil collector, but instead the amount of oil fed centrally into the planetary gear arrangement is used to cool and lubricate the bearings, in particular the Planetary bearing, leads. For this purpose, the oil is fed into the planetary carrier on both sides of the sun gearing and is preferably guided to the thrust washers of the planetary gears by centrifugal force. The planet wheel is thus flushed with oil from the outside on both sides. Heat is thus dissipated by the oil flowing past the planet wheel. The flow of oil within the planetary gear bearing is inverted, i.e. it no longer flows from the inside to the thrust washers, but is guided proportionally from the thrust washers to the bearing, in particular to the radial needle bearing. There is no need for an oil collector and a solid pin without oil holes can be used to mount the planet wheel. To control the oil flow, the components that are already present in the wheel set (e.g. sun gear, axial bearing of the sun/planet carrier, thrust washers, planet gears) are preferably adapted in such a way that no additional elements are required.

In a preferred development of the invention, the planetary pin is fluidically closed and/or fluidically passive and/or designed as a solid material pin. Closed off in terms of flow and/or passive in terms of flow means in particular that there is no passage from the oil to the bearing through the interior of the planet bolt. This development is intended to emphasize that the oil is supplied axially to the bearing and/or not in the radial direction. In particular, it is provided that the bearing is supplied with the oil axially and/or is sealed off in an oil-tight manner in the radial direction from the inside by the outer surface of the planet bolt.

In a preferred embodiment of the invention, the planetary gear arrangement has at least one thrust washer. The thrust washer is arranged between the carrier cheek and the planet wheel. In particular, the thrust washer serves as an axial slide bearing for the planet gear during operation. An inner, carrier-side oil supply structure for supplying the oil from the lubricating gap to the bearing is arranged on the side of the thrust washer facing the carrier cheek. The oil supply structure is designed in particular as a vertical structure. In particular, the thrust washer does not lie flat and/or flat on the carrier cheek, but rather the inner, carrier-side oil supply structure forms open channels through which the oil can flow to the bearing. Alternatively or additionally, an outer oil supply structure for supplying the oil from the lubricating gap to the bearing is arranged on the side of the carrier cheek facing the thrust washer. The outer oil supply structure has the function that the thrust washer does not lie flat and/or over a large area gene, but that open channels for supplying the oil from the lubricating gap to the storage are available. It can also be provided that the planetary gear arrangement has the inner oil supply structure and the outer oil supply structure. For example, the oil supply structure is designed as a number of channels. The lubricating gap is arranged in particular between the thrust washer and a contact surface, in particular the carrier cheek.

In a preferred development of the invention, the planetary gear arrangement has an inner carrier-side oil drainage structure on the side of the thrust washer facing the carrier cheek for removing the oil from the bearing and/or from the oil supply structure. Alternatively or additionally, an outer oil drainage structure for draining the oil from the bearing and/or from the oil supply structure is formed on the side of the carrier cheek that faces the thrust washer. It can also be provided that the planetary gear arrangement has the inner, carrier-side oil drainage structure and the outer oil drainage structure. For example, the oil discharge structure is designed as a channel or multiple channels. Thus, the oil-guiding structures form the conversion for the lubrication of the bearing and the cooling of the planet wheel.

In a preferred embodiment of the invention, the planetary gear arrangement has at least one or the thrust washer. The thrust washer is arranged between the carrier cheek and the planet wheel. In particular, the thrust washer is used to start the planet wheel during operation. On the side of the thrust washer facing the planet wheel, there is an inner, wheel-side oil supply structure for supplying the oil from the lubricating gap to the bearing. The oil supply structure is designed in particular as a vertical structure. In particular, the thrust washer does not lie flat and/or flat on the planet gear, but rather the inner, wheel-side oil supply structure forms open channels through which the oil can flow to the bearing. For example, the oil supply structure is designed as a number of channels. The lubricating gap is arranged in particular between the thrust washer and the planet wheel.

In a preferred development of the invention, the planetary gear arrangement has an inner, wheel-side oil drainage structure on the side of the thrust washer facing the planetary gear for draining the oil from the bearing and/or from the oil supply structure. For example, the oil discharge structure is designed as a channel or multiple channels. Thus, the oil-guiding structures form the conversion for the lubrication of the bearing and the cooling of the planet wheel.

In particular, a first carrier-side lubricating gap can be formed between the first thrust washer and the first carrier cheek and a first wheel-side lubricating gap between the first thrust washer and the planet wheel. Alternatively or additionally, a second carrier-side lubricating gap can be formed between the second thrust washer and the second carrier cheek, and a second wheel-side lubricating gap can be formed between the first thrust washer and the planet wheel.

The function of the thrust washer is therefore in particular to keep the lubricating gap open in order to ensure a permanent flow of oil to the bearing or drain from the bearing and, optionally, to redirect the oil flow into the area of the bearing.

In a preferred constructional implementation of the invention, the thrust washer is freely rotatable on the planetary pin. In particular, the thrust washer is not fixed at an angle of rotation. In this implementation, it is particularly preferred that the inner oil supply structure(s) and the inner oil drainage structure(s) are depicted in a common inner oil drainage structure, with the oil supply structures forming the inner oil supply structure or the outer oil drainage structure in any angular position of the thrust washer. For example, the inner oil drainage structure on the thrust washer is divided into at least or exactly three segments in the direction of rotation, so that it is ensured that at any angular position at least one segment or at least a partial segment forms the inner oil drainage structure and a segment or at least a partial segment forms the inner oil drainage structure. For example, the inner oil guide structure can have multiple channels.

Alternatively or additionally, the lubricating gap is formed or opened up by oil guide contours on the thrust washer.

In a preferred embodiment of the invention, the thrust washer has a receiving opening for the planet bolt. In the direction of rotation, the receiving opening corresponds in sections to the outer diameter of the planet bolt, so that the thrust washer is positively secured in the radial direction by the planet bolt. The receiving opening preferably has at least one inlet enlargement arranged radially on the inside for passing on the oil from the lubricating gap, in particular from the oil supply structure to the bearing. The input enlargement can, for example, be an enlargement of the receiving opening be trained. Via the lubricating gap, in particular the oil supply structure, the oil is passed on to the inlet enlargement and from there into the bearing in an axial direction. In particular, the inlet extension forms a flow inlet into the bearing. Alternatively or additionally, the receiving opening has an outlet enlargement arranged radially on the outside for draining the oil from the bearing to the lubricating gap, in particular to the oil drainage structure. Oil escaping from the bearing is thus passed on via the outlet expansion to the lubricating gap, in particular to the oil drainage structure.

For the implementation in which the thrust washer is designed to rotate freely, the thrust washer has extensions that represent the input extension and/or the output extension. For example, the thrust washer has several, in particular three, extensions, with the extensions assuming the function of the input extension and the output extension depending on the angular position.

In a preferred embodiment of the invention, the sun gear unit has at least one, preferably at least or exactly two, first radial opening(s), in particular a radial bore for the fluidic connection of the oil feed to the first axial sun-side area. Alternatively or additionally, the sun wheel unit has at least one, preferably at least or exactly two, second radial opening(s), in particular radial bore(s), for the fluidic connection of the oil feed to the second axial sun side area. The oil can flow via the respective radial opening, starting from the oil supply, in particular starting from the interior of the hollow shaft, to the respective sunny side areas.

In a preferred implementation of the invention, the planetary gear arrangement has at least one axial bearing device for the axial bearing of the sun wheel unit. It is preferred that the first partial supply path or the second partial supply path runs through the axial bearing device. The axial bearing device is designed in particular as a rolling element bearing device, with the second partial supply path running between the rolling elements.

In a preferred constructional implementation, the sun gear unit has at least one first radial opening for the fluidic connection of the oil feed to the first axial sun-side area and the axial bearing device. The first partial supply path runs via the at least one first radial opening, the second partial supply path runs via the axial bearing device.

In a preferred development, the planetary gear arrangement has a shaft which is accommodated coaxially in the sun wheel unit, in particular in the sun shaft. The shaft has a coaxial oil feed and is implemented in particular as a further hollow shaft or blind hole shaft with a coaxial bore, designed as a blind hole. An annular gap is formed between the shaft and the sun gear unit, with the annular gap in particular forming a section of the interior of the hollow shaft of the sun gear unit. At least or precisely one transverse channel is provided in the shaft, which fluidically connects the coaxial oil supply to the annular gap. In this way a first section of the main supply path is formed. In particular, the oil is fed from the coaxial oil feed of the shaft, via the annular gap, via the sun-side areas to the lubricating gaps between the carrier cheek and the planet wheel and then into the bearing.

In a preferred implementation of the invention, the transverse channel, depending on the flow resistance and/or the oil loss of the first or second partial supply path, in particular in the area of the sun gear unit, is arranged closer in the axial direction to the partial supply path that has the higher flow resistance and/or a higher oil loss .

The flow resistance is specified in particular structurally by different throttle cross sections of the partial supply paths. The flow resistance is determined by the number and diameter of the radial cross bores in T1 and/or the number of rolling elements and cages of the axial bearing in T2.

If, for example, the first partial supply path has first radial bores and, for example, the second partial supply path is routed via the axial bearing device, namely via an opening on the end face of the sun gear unit and thus without radial openings, then the second partial supply path has a lower flow resistance, so that the at least one transverse channel is closer to the first radial openings than is arranged on the axial bearing device. Furthermore, it must be taken into account that the partial supply paths may have different oil losses, so that the transverse channel is arranged closer to the partial supply path with the higher oil loss. Considering the distance between the radial opening for the first partial supply path and a front opening of the sun gear unit for the second partial supply path with the axial bearing device, the transverse channel is arranged in such a way that the distance between the first radial opening and the transverse channel is less than 30%, preferably less than 20% of the distance. Alternatively, the transverse channel can be located at an axial position outside the distance between the first radial opening and the front opening, namely on the side of the first radial opening. Alternatively or additionally, it can be provided that a ratio of the oil flow quantity in the annular gap of the first partial supply path T1 to the second partial supply path T2 is as follows: T1/T2<1/9. In particular, in this way the transverse channel can be shifted to the side of the sun wheel unit that is closer to an input opening of the shaft. Thus, the blind hole does not have to be made as deep.

The position ensures in particular that a similar or the same amount of oil is fed to the two sides of the respective bearing via the two partial supply paths.

It is particularly preferred that the shaft is designed as a planet carrier shaft. In particular, the second partial supply path exits axially from the sun gear unit and leads via the axial bearing device, which is arranged between the sun gear unit and in particular the sun gear and a shoulder of the planet carrier shaft.

• Die Beölung erfolgt zentral über die mit Relativdrehzahl zum Planetenträger drehende Sonnenradeinheit, was eine umfänglich gleichmäßige Ölverteilung ergibt. Die Beölung erfolgt beidseitig der Sonnenverzahnung über die Axiallagereinrichtung zwischen Sonnenradeinheit und Planetenträger sowie über bevorzugt mindestens zwei Radialöffnungen in der Sonnenradeinheit, direkt neben der Laufzahnung des Sonnenrads. Das Mengenverhältnis zwischen dem ersten Teilversorgungsweg und dem zweiten Teilversorgungsweg ist in einem Verhältnis von 1:9 bis 9:1 einstellbar und kann zum einen über die Anzahl und Durchmesser der Bohrungen sowie das Käfig- und Axialscheibendesign der Axiallagereinrichtung, insbesondere des Axialnadellagers beeinflusst werden. Ölführungsstrukturen im Planetenträger (keine gebohrten Kanäle im Vollmaterial, Ölfluss innerhalb des Trägers) zur Bündelung des Öls im Bereich der Planetenräder bzw. Vorgabe eines fliehkraftindizierten Vorzugsweges durch den Schmierspalt. Die Anlaufscheiben an den Planetenrädern sind mit Ölführungsstrukturen/-konturen versehen, die das Öl in die radiale Planetenradlagerung fördern. Die Planetenbolzen sind „Vollbolzen“, ohne weitere Ölbohrungen.

Possible advantages are:

• The oiling takes place centrally via the sun gear unit rotating at relative speed to the planet carrier, which results in an even distribution of oil over the entire area. The oiling takes place on both sides of the sun gear via the axial bearing device between the sun gear unit and the planet carrier and via preferably at least two radial openings in the sun gear unit, directly next to the running gear of the sun gear. The quantity ratio between the first partial supply path and the second partial supply path can be adjusted in a ratio of 1:9 to 9:1 and can be influenced on the one hand by the number and diameter of the bores and the cage and axial disk design of the axial bearing device, in particular the axial needle bearing. Oil routing structures in the planetary carrier (no drilled channels in the solid material, oil flow within the carrier) for bundling the oil in the area of the planetary gears or specifying a preferred centrifugal path through the lubricating gap. The thrust washers on the planetary gears are provided with oil-guiding structures/contours that feed the oil into the radial planetary gear bearing. The planetary bolts are "solid bolts" without additional oil bores.

• 1 eine schematische Längsschnittdarstellung eines Ausführungsbeispiels einer erfindungsgemäßen Getriebeanordnung als ein Ausführungsbeispiel der Erfindung;
• 2 eine schematische Draufsicht auf eine Anlaufscheibe der Planetengetriebeanordnung der 1.

Further features, advantages and effects of the invention result from the following description of a preferred exemplary embodiment of the invention and the attached figures. These show:

• 1 a schematic longitudinal sectional view of an embodiment of a transmission arrangement according to the invention as an embodiment of the invention;
• 2 a schematic plan view of a thrust washer of the planetary gear assembly 1 .

The 1 shows a planetary gear arrangement 1 in a schematic longitudinal section along a main axis of rotation 100, as can be used, for example, in a vehicle transmission.

The planetary gear arrangement 1 has a sun gear unit 2 , the sun gear unit 2 including a sun gear 3 and a sun shaft 4 . The sun wheel 3 is non-rotatably connected to the sun shaft 4 . In this exemplary embodiment, the sun gear unit 2 is formed in one piece with the sun gear 3 and with the sun shaft 4 . The sun wheel unit 2 and in particular the sun shaft 4 is designed as a hollow shaft, which has a sun toothing 5 at a free end, which is designed as a plug-in toothing. The sun wheel unit 2 and in particular the sun shaft 4 has a coaxial, continuous opening. The sun toothing 5 is arranged at a first end of the sun wheel unit 2 or the sun shaft 4 .

The planetary gear arrangement 1 has a planet carrier 6, the planet carrier 6 comprising a first carrier cheek 7 and a second carrier cheek 70, which are arranged parallel to one another. In this embodiment, the carrier cheeks 7, 70 are designed as flat components. The planetary carrier 6 has a plurality of planetary gears 8 which are rotatably mounted on planetary bolts 9 via a bearing 10 which is implemented as a needle bearing device. The planet bolts 9 are designed as solid material. The carrier cheeks 7, 70 are connected via the planetary bolts 9 and optionally not shown webs. The axes of rotation 101 of the planet gears 8 are offset parallel to the main axis of rotation 100 . The planetary gears 8 and/or the planetary bolts 9 are arranged at regular intervals around the main axis of rotation 100 in the direction of rotation. The planet gears 8 have helical gearing just like the sun gear 3 , the planet gears 8 meshing with the sun gear 3 . More specifically, between the planet gear 8 and the first carrier cheek 7 is a first thrust washer 24 a and between A second thrust washer 240 is arranged between the planet wheel 8 and the second carrier cheek 70 . A first carrier-side lubricating gap 23 is arranged between the first carrier cheek 7 and the first thrust washer 24 , and a second carrier-side lubricating gap 230 is arranged between the second carrier cheek 70 and the second thrust washer 240 .

The planetary carrier 6 is placed on a planetary carrier shaft 11 and is connected to it in a torque-proof manner. The planet carrier shaft 11 has a blind opening which is aligned coaxially to the main axis of rotation 100 and which is open on a first side. In particular, the blind opening can end immediately after the transverse channel 16 . Thus, the planet carrier shaft 11 is designed in sections as a hollow shaft. On the same side, the planet carrier shaft 11 carries a further carrier toothing 12, the further toothing being designed as a spline.

The planetary gear arrangement 1 has an axial bearing device 13 , the sun gear unit 2 and in this exemplary embodiment the sun gear 3 being supported on the axial bearing device 13 in the axial direction. The planet carrier shaft 11 has a shaft shoulder 14, with the axial bearing device 13 being supported in the axial direction on a shaft shoulder 15 of the shaft shoulder 14, so that the sun gear unit 2, in particular the sun gear 3, has a first bearing partner and the planet carrier shaft 11, in particular the shaft section 14 and in special the shaft shoulder 15 form a second bearing partner. The axial bearing device 13 is designed as a roller bearing device, in particular a needle bearing device.

The planet carrier shaft 11 has at least one transverse channel 16, the transverse channel 16 fluidically connecting an interior of the planet carrier shaft 11 to the interior of the sun gear unit 2, in particular the sun shaft 4 and/or the sun gear 3. An annular gap 17 is formed between the planetary carrier shaft 11 and the sun gear unit 2 , the annular gap 17 being fluidically connected to the interior of the planetary carrier shaft 11 via the transverse channel 16 .

The sun gear unit 2 and in particular the sun shaft 4 has at least one radial opening 18, the radial opening 18 being designed as a radial bore.

The planetary gear arrangement 1 has a main supply path 19 for supplying oil to the bearing 10 . The main supply path 19 forms an oil supply for the bearing 10. The main supply path 19 begins in the interior of the planetary carrier shaft 11, which is supplied with oil via an end opening. For example, the oil is actively pumped into the interior.

The main supply path 19 runs via the transverse channel 16 into the annular gap 17 and thus into the interior of the sun shaft 4. In the annular gap 17, the main supply path 19 divides into a first partial supply path 20 and a second partial supply path 21.

The first partial supply path 19 runs via the radial opening 18 into a first axial sun side area 22 which is arranged axially next to the sun wheel 3 . The first partial supply path 20 then runs into the first lubricating gap 23. The first carrier-side lubricating gap 23 is delimited on the one hand by the first thrust washer 240 and on the other hand by the first carrier cheek 7 . The first partial supply path 20 runs into the first lubricating gap 23 on the carrier side and then continues in the axial direction towards or into the bearing 10.

The second partial supply path 21 runs, starting from the annular gap 17, exiting axially from the sun gear unit 2 to the axial bearing device 13. In particular, the second partial supply path 21 emerges from an opening at the end of the sun gear unit 2 and/or the sun gear 3, so that only a small flow resistance arises here . Starting from the axial bearing device 13 , the second partial supply path 21 runs into a second axial area 25 on the sun side, which is arranged between the sun wheel 3 and the shaft shoulder 14 . The second partial supply path 21 then runs into the second carrier-side lubricating gap 230. The second carrier-side lubricating gap 230 is delimited on the one hand by the second thrust washer 24b and on the other hand by the second carrier cheek 70. The second partial supply path 21 enters the bearing 10 in the axial direction through the second thrust washer 24b.

For a discharge of the oil from the bearing 10, it again passes through the first or second thrust washer 24a, b and is transported away radially outwards via the first or second carrier-side lubricating gap 23, 230 by centrifugal force.

The 2 FIG. 12 shows the thrust washer 24a, b in a schematic axial top view, wherein it can be seen that this has a receiving opening 26 for the planet bolt 9. Sections of the receiving opening 26 correspond to the outer diameter of the planetary pin 7a, b, as shown by a dashed circle with the reference number 9.

The side of the thrust washer 24a, b shown faces away from the respective carrier cheek 7, 70. An inner oil supply structure 27 is introduced on the underside, so that the respective carrier-side lubricating gap 23, 230 between the thrust washer 24 a, b and the carrier cheek 7, 70 has an oil channel or oil flow area which connects the outer circumference of the thrust washer 24 a, b with the inner circumference , In particular the receiving opening 26 fluidically connect. In addition or as an alternative, it can be provided that the respective carrier cheek 7, 70 has external oil supply structures. As shown, the oil supply structure 27 can be formed by a channel, but this can also be realized as individual elevations, nubs or the like.

Two internal oil drainage structures 28 are introduced on the upper side, which open the carrier-side lubricating gap 23, 230 radially outside of the respective planet bolts 7, 70 in order to ensure that the oil is drained from the bearing 10. The oil discharge structures 28 are designed as channels identical to the oil supply structures 27 .

In the lower area of the receiving opening 26 there is an inlet enlargement 29 for enlarging the receiving opening 26 so that the oil can be guided from the carrier-side lubricating gap 23, 230 into the bearing 10 in the axial direction. In an axial top view, the inlet enlargement 29 is arranged congruently with the bearing 10, so that the oil can flow in the axial direction from the carrier-side lubricating gap 23, 230 directly into the bearing 10.

In an upper area there are exit extensions 30 for discharging the oil from the bearing 10 to the carrier-side lubricating gaps 23, 230 and to the oil discharge structure 28. The exit extensions 30 are arranged congruently with the bearing 10 in an axial plan view. In one possible configuration, the thrust washer 24, 240 is inserted in a rotationally fixed manner. As an alternative to this, the thrust washer 24, 240 is arranged to rotate freely, with inner oil-guiding structures 31, formed from the inner oil-supply structure 27 and that of the inner oil-draining structure 28, and the extensions 32, formed from the input extension 29 and the output extensions 30 by changing the angular position of the thrust washer 24 , 240 swap their position and function. In particular, the inner oil-guiding structures 31 and the extensions 32 ensure that the first and second carrier-side lubricating gaps 23, 230 are formed and are fluidically connected to the bearing 10.

Optionally or alternatively, a first, wheel-side lubricating gap (not shown) can be provided between the planetary gear 8 and the first thrust washer 24 and/or a second, wheel-side lubricating gap (not shown) can be provided between the planetary gear 8 and the second thrust washer 240 . The wheel-side lubricating gap is formed analogously to the carrier-side lubricating gap by oil-guiding structures on thrust washer 24, 240, which can be configured identically to the oil-guiding structures on the side of thrust washer 24, 240 facing carrier cheek 7, 70. The first and the second partial supply path 20, 21 flows around the thrust washer 24, 240 on both sides, so that cooling or lubrication between the carrier cheek 7, 70 and the thrust washer 24, 240 and between the thrust washer 24, 240 and the planet wheel 8 is achieved. In exemplary embodiments, only the carrier-side lubricating gaps 23, 230 or the wheel-side lubricating gaps or any mixture of carrier-side lubricating gaps 23, 230 and the wheel-side lubricating gaps can be used.

Reference List

1

planetary gear arrangement

2

sun gear unit

3

sun gear

4

sun wave

5

sun teeth

6

planet carrier

7, 70

first and second beam cheek

8th

planet gears

9

planet bolt

10

storage

11

planet carrier shaft

12

further interlocking

13

thrust bearing device

14

wave heel

15

shaft shoulder

16

cross channel

17

annular gap

18

radial opening

19

main supply route

20

first partial supply route

21

second partial supply path

22

first axial sunny side area

23, 230

first and second lubricating gap

24, 240

first and second thrust washer

25

second axial sunny side area

26

intake opening

27

internal oil supply structure

28

internal oil drainage structure

29

input extension

30

output extension

31

internal oil routing structures

32

extensions

100

main axis of rotation

101

axis of rotation

QUOTES INCLUDED IN DESCRIPTION

This list of documents cited by the applicant was generated automatically and is included solely for the better information of the reader. The list is not part of the German patent or utility model application. The DPMA assumes no liability for any errors or omissions.

Patent Literature Cited

• US2016146332A1 [0003]

Claims (10)

Planetary gear arrangement (1) with a sun wheel unit (2), the sun wheel unit having a sun wheel (3) and a sun shaft (4), the sun wheel (3) being arranged on the sun shaft (4), with a planet carrier (6), wherein the planet carrier (6) has a first carrier cheek (7) and a second carrier cheek (70), and with at least one planet wheel (8) and a planet pin (9), the planet pin (9) connecting the carrier cheeks (7, 70) and the planet wheel (8) is rotatably arranged on the planet pin (9) via a bearing (10) and meshes with the sun wheel (3), with a main supply path (19) for supplying oil to the bearing (10), the main supply path (19) can be supplied via an oil feed radially on the inside of the sun gear unit (2), the main supply path (19) being divided into a first and a second partial supply path (20, 21), the first partial supply path (20) starting from the oil feed via a first axial The sun side area (22) of the sun gear (3) and the second partial supply path (21), starting from the oil supply, via a second axial sun side area (25) of the sun gear (3), characterized in that the first partial supply path (20) has at least one first lubricating gap (23) arranged between the first carrier cheek (7) and the planet wheel (8) leading to the bearing (10) and/or that the second partial supply path (21) via at least one second lubricating gap (230) arranged between the second carrier cheek (70) and the planet gear (8) leading to the bearing (10). Planetary gear arrangement (1) after claim 1 , characterized in that the planetary pin (9) is fluidically closed and/or fluidically passive and/or is designed as a solid material bolt. Planetary gear arrangement (1) according to any one of the preceding Claims 1 or 2 , characterized in that the planetary gear arrangement (1) has at least one thrust washer (24, 240), the thrust washer (24, 240) being arranged between the carrier cheek (7,70) and the planet wheel (8) and being on the carrier cheek (24, 240) side facing an inner, carrier-side oil supply structure (27) for supplying the oil from the lubricating gap (23,230) to the bearing (10) and/or on the side facing the thrust washer (24, 240) of the carrier cheek (7 ,70) an outer oil supply structure for supplying the oil from the lubricating gap (23,230) to the bearing (10) is arranged. Planetary gear arrangement (1) after claim 3 , characterized in that on the side of the thrust washer (24, 240) facing the carrier cheek (7, 70) there is an inner, carrier-side oil discharge structure (28) for discharging the oil from the bearing (10) and/or that on the thrust washer ( 24, 240) facing side of the carrier cheek (7,70) an outer oil discharge structure for discharging the oil from the bearing (10) is arranged. Planetary gear arrangement (1) after claim 3 or 4 , characterized in that one or the thrust washer (24, 240) is designed to rotate freely and has an inner oil guide structure (28), wherein the inner oil guide structure (28) in any angular position, the inner oil feed structure (27) and / or the outer oil discharge structure ( 28) forms. Planetary gear arrangement (1) according to one of claims 3 until 5 , characterized in that the thrust washer (24, 240) has a receiving opening (26) for the planetary bolt (9), the receiving opening (26) partially corresponding to the outer diameter of the planetary bolt (9) and at least one input enlargement (29) for passing on the Oil from the oil supply structure (27) and/or from the lubricating gap (23, 230) to the bearing (27) and/or at least one outlet extension (30) for draining the oil from the bearing (10) to the oil discharge structure (28) and/or to the Has lubricating gap (23.230). Planetary gear arrangement (1) according to one of the preceding claims, characterized in that the sun gear unit (2) has at least one first radial opening (18) for fluidically connecting the oil supply to the first axial sun side area (22) and/or that the sun gear unit (2) has second radial openings (18) for fluidic connection of the oil supply with the second axial sun side area (25). Planetary gear arrangement (1) according to one of the preceding claims, characterized in that it has at least one axial bearing device (13) for the axial bearing of the sun wheel unit (2), the first partial supply path (20) or the second partial supply path (21) being guided by the axial bearing device (13 ) runs. Planetary gear arrangement (1) according to one of the preceding claims, characterized in that the planetary gear arrangement (1) has a shaft (11), the shaft (11) being accommodated coaxially in the sun wheel unit (2). is, wherein the shaft (2) has a coaxial oil supply, wherein an annular gap (17) is formed between the shaft (11) and the sun wheel unit (2) and wherein a transverse channel (16) in the shaft, the coaxial oil supply with the annular gap ( 17) fluidly connects to form a first portion of the main supply path (19). Planetary gear arrangement (1) after claim 9 , characterized in that the transverse channel (16) depending on the flow resistance and / or the oil loss of the first and the second partial supply path (20, 21) closer to the partial supply path (20, 21) with the higher flow resistance and / or with the higher oil loss is arranged.

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