DE102022111075B4 - Lubrication device for a planetary wheel bearing of a planetary gear and planetary gear - Google Patents

Abstract

Lubrication device for a planetary gear bearing of a planetary gear (1) with a planetary carrier (2), at least one bearing pin arranged thereon, a rolling bearing (5) arranged on the bearing pin (4), a planetary gear (6) mounted via the rolling bearing (5) and two thrust washers ( 7; 100; 200; 300) which are arranged on both sides of the planet gear (6) between the planet gear (6) and the planet carrier (2) and each have contact surfaces (8; 10; 107; 108; 207; 208; 309; 310) for the planet gear (6) and the rolling bearing (5), with between the planet carrier (2) and at least one adjacent thrust washer (7; 100; 200; 300) and/or between at least one thrust washer (7; 100; 200; 300) and the adjacent planetary gear (6) is provided with a lubricant gap that is open radially outwards, via which lubricant supplied from radially outside the thrust washer (7; 100; 200; 300) can be guided onto the rolling bearing (5) which axially projects beyond the planetary gear (6).

Description

The invention relates to a lubricating device for a planetary wheel bearing of a planetary gear with a planetary carrier, at least one bearing pin arranged thereon, a roller bearing arranged on the bearing pin, a planetary gear mounted above the roller bearing and two thrust washers which are arranged on both sides of the planetary gear between the planetary gear and the planetary carrier and each Have contact surfaces for the planetary gear and the rolling bearing.

Planetary gears are used in a wide variety of areas, for example in a motor vehicle and there, for example, in a transmission or a drive train of an electric drive, in particular an electric axle, or a hybrid drive train. Such a planetary gear usually has a planetary carrier with at least one, usually several, off-center and circumferentially offset relative to one another planet gears, which are mounted on bearing pins provided on the carrier side via respective roller bearings. Between the planet gear or the rolling bearing and the planet carrier, which is formed, for example, by means of two parallel cheeks, an annular thrust washer with a central receiving hole through which the bearing pin engages is arranged, so seen axially it is located between the planet gear or the rolling bearing and the planet carrier, so that the planet gear, which is slightly axially displaceable on the bearing pin, can run against the thrust washer and is axially supported on the planet carrier via this. The same applies to the rolling bearing, which consists of a cage in which several rolling elements, usually cylindrical needles, are accommodated or guided, the cage axially closing off the rolling bearing and running axially against the corresponding thrust washer when starting.

Since the planetary gear rotates during operation, the bearing area must be lubricated with a lubricant. For this purpose, it is known to supply the lubricant, usually oil, via the bearing pin, which is designed as a hollow pin and has an axial bore and at least one radial bore, so that the lubricant is supplied axially to the bolt and can exit radially into the bearing area. In order to direct the lubricant into the hollow bearing pin, a lubricant collecting tray must regularly be provided, with which the lubricant is captured and guided past the planet carrier to the side outside. The lubricant collecting tray is connected to the bearing pins so that the lubricant can be fed directly to the bearing pins via the collecting tray. This means that in order to realize an appropriate supply of lubricant to the storage area, considerable effort has to be made, since on the one hand special, drilled bolts have to be used, and on the other hand a corresponding supply structure comprising a lubricant collecting tray has to be arranged and appropriate precautions have to be taken for fastening the same and the like.

The US 2016/ 0 195 136 A1 and the US 3,316,035 A each show planetary gears with thrust washers, which form a lubricant gap.

The DE 36 22 671 C1 shows a thrust washer arrangement, in particular for planetary gears in a planetary gear carrier, which consists of two thrust washers arranged on both sides of planetary gears which are rotatably mounted on planetary gear bolts fixed in the planetary gear carrier via a needle bearing arrangement and which are provided with recesses for supplying lubricating oil to the bearing arrangement. The external thrust washer has on its outer circumference diametrically opposed, sector-shaped cutouts of approximately 110° angular extent, the vertices of which lead lubricating oil to the bearing arrangement, and the internal thrust washer is non-uniform on the circumference with a plurality of non-uniform circumferences arranged on a circle outside the thrust circle of the needles of the needle bearing arrangement distributed holes, such that in each relative position of the outer and inner thrust washers only one connection between one of the two vertices on the outer thrust washer and a hole in the inner thrust washer is ensured.

The invention is based on the object of specifying an improved lubricating device for a planetary gear bearing of a planetary gear.

To solve this problem, in a lubricating device of the type mentioned at the outset, it is provided according to the invention that between the planet carrier and at least one adjacent thrust washer and / or between at least one thrust washer and the adjacent planet gear there is a lubricant gap that is open radially outwards, via which from radially outside the Thrust washer supplied lubricant can be guided onto the roller bearings axially projecting beyond the planet gear.

In the lubricating device according to the invention, the lubricant is supplied directly from the sun gear side, which means that the lubricant is supplied to the planet gears from radially within the planetary gear set. Around the lubricant supplied from the radial inside to the bearing area To be able to supply, the invention provides for the formation of a defined lubrication gap between the planet gear and the thrust washer and / or the thrust washer and the planet carrier or its cheek, this lubrication gap being open radially outwards. Such a lubrication gap is understood to be a one-part or multi-part channel structure, which on the one hand is open radially outwards, so that an inflow of lubricant is possible from radially outside the thrust washer area, and which is open radially inwards to the bearing pin or the bearing area. The lubricant supplied radially from the sun gear side, i.e. from the radially inside, is received via this lubrication gap or channel structure and directed radially in the direction of the bearing area. According to the invention, it is provided that the rolling bearing axially projects beyond the planetary gear, which means that, viewed axially, the rolling bearing is wider than the planetary gear. The rolling bearing consequently protrudes axially beyond the end face of the planetary gear. As described, the rolling bearing consists of the cage and the needle-shaped rolling elements. Since the cage with corresponding ring rims forms the axial end of the rolling bearing, at least the cage therefore projects axially beyond the planet wheel end face at least in sections, with the rolling bearing running with the respective ring rim against the contact surface of the thrust washer. Since, as described above, the corresponding lubricating gap, i.e. the channel structure, is formed between the thrust washer and the planet gear or the planet carrier, which is also open radially inwards, it is therefore possible that the lubricant supplied to the channel structure directly onto the axially projecting cage or ring edge, from where it is then guided directly into the rolling area. This means that a direct supply of lubricant to the cage and thus to the rolling bearing is possible through the radial lubricant supply on the sun gear side and the corresponding intake and forwarding via the lubrication gap or the channel structure. At the same time, this also supplies lubricant to the actual contact or friction areas between the planet gear or cage and the thrust washer, and, if the thrust washer is rotatably mounted on the bearing pin, also between the thrust washer and the cheek of the planet carrier.

According to the invention, an integrated lubricating device is therefore provided which enables a simplified lubricant supply without the use of specific bearing bolts or other supply components. This is because there is no need for hollow-drilled bearing bolts, a lubricant catch tray or any other precautions. All that is required is, for example through an appropriate design of the thrust washer, a corresponding lubrication gap or channel structure, as well as a corresponding radial lubricant supply into the planetary gear set on the sun gear side via a simple channel geometry. Via the lubricant or channel structure realized with the help of inevitably provided components, namely the thrust washer in connection with the planet gear and/or the planet carrier, as well as the axial projection of the roller bearing or cage over the planet gear provided according to the invention, a direct supply of lubricant is ultimately possible without additional components Radial flow of lubricant onto the axially projecting cage area, where the channel structure opens radially, is possible.

According to the invention, the thrust washer is provided with a lubricant guide structure which extends the radial lubricant flow from radially outside to radially inward and defines the lubrication gap, the thrust washer having a profiling, via which, on the one hand, there is a radially outer first contact surface for the planetary gear and a radially inside second contact surface for the rolling bearing is formed, the second contact surface being set back axially with respect to the first contact surface and the rolling bearing being axially wider than the planet gear, and via which profiling on the other hand the lubricant guiding structure is formed. The thrust washer is therefore provided with a specific profiling, i.e. geometrically shaped in such a way that two defined contact surfaces are formed on it, which are offset from one another when viewed axially. A first, radially outer contact surface is formed, against which the planetary gear runs with its end face. A second, internal contact surface is also formed, against which the roller bearing or cage runs axially. This second contact surface is axially set back with respect to the first, which takes into account the fact that the rolling bearing, as described, is axially wider than the planet gear, i.e. it protrudes axially. With its two axially offset contact surfaces or contact planes, the thrust washer therefore offers optimal support for the components of different widths, namely the planetary gear and the rolling bearing.

According to the invention, the profiling forming the lubricant guiding structure has a plurality of recesses, provided at least in an outer disc section, offset in the circumferential direction and introduced from a first disc side, as well as flat elevations corresponding to these and protruding on the opposite second disc side, the elevations forming the first contact surface form. The thrust washer is therefore characterized by a specific disk profile, which, on the one hand, creates two separate, axially offset thrust surfaces located on different radial planes, as well as lubrication gaps that are open radially towards the outer circumference or channels, i.e. the channel or lubricant guide structure, via which lubricant can be supplied from the radial outside. The thrust washer, and of course the same applies to the second thrust washer, provided this is also correspondingly profiled, is correspondingly profiled by mechanical forming, in particular embossing, of a metal sheet. It has a plurality of axial recesses offset around the circumference, which are provided in an outer disk section and preferably extend to the outer circumference. On the opposite side of the disk, corresponding elevations arise due to the forming process, which alternate with axially set back, non-formed disk areas. Seen radially, these non-formed disc areas, i.e. the areas between two adjacent elevations, each form a channel that is open towards the outer circumference and through which lubricant can be supplied radially from the outside. Since the elevations are locally formed, they form a segmented first contact surface, that is, the sum of the individual, flat elevations forms the total area of this first contact surface. Since the elevations, viewed radially, do not extend to the inner circumference, a non-deformed, annular disk section remains in the inner disk area, which is the second contact surface on which the roller bearing or the cage is supported, this second contact surface, as described, is set back axially with respect to the segmented first contact surface. By designing the thrust washer or the disk profile in this way, the channel structure can be formed in a simple manner, as can the two contact surfaces located in different axial planes.

In a further development of the invention, the depressions and elevations can extend to the outer edge of the thrust washer. After the thrust washer rests against the planet carrier with the side from which the recesses are made, the latter then covers the recesses so that the recesses form pockets that are open radially outwards and can serve as a lubricant reservoir.

It is conceivable in one embodiment of the invention that corresponding openings are provided at the foot of the recesses, through which the lubricant contained in the pockets can reach the other side of the disk, i.e. directly to the axially projecting cage, so that the supplied lubricant volume can be increased .

However, it is also conceivable that the depressions and elevations extend over the entire width of the thrust washer, in which case tabs or the like that project radially inwards between the elevations are expediently provided on the inner circumference in the area of the undeformed disk areas and define the inner bore diameter. This means that radially open channels also form on the side facing the planet carrier. The inflowing lubricant can flow into the bearing area through the recesses on the inner circumference, so that ultimately the entire circumference of the thrust washer is provided as an open channel structure. In this way, the thrust washer can be provided with one or more axial openings or recesses that allow an axial flow of lubricant, although instead of such tabs that each define a recess between them, axial, closed openings or the like can also be provided.

In addition to the lubricating device, the invention also relates to a planetary gear with a planetary carrier, at least one bearing pin arranged thereon, a rolling bearing arranged on the bearing pin, a planetary gear mounted above the rolling bearing and two thrust washers which are arranged on both sides of the planetary gear between the planetary gear and the planetary carrier and each contact surfaces for the planet gear and the rolling bearing. Such a planetary gear is characterized in that at least one thrust washer is provided with a lubricant guiding structure which allows a radial flow of lubricant from radially outside to radially inward, and in that the thrust washer has a profiling, via which, on the one hand, there is a radially outer first contact surface for the planetary gear and a radially internal second contact surface is formed for the rolling bearing, the second contact surface being set back axially with respect to the first contact surface and the rolling bearing being axially wider than the planet gear, the lubricant guiding structure being formed via the profiling.

The planetary gear is preferably part of a drive train of an electric drive, such as an electric axle, or a hybrid drive train. In addition to a sun gear unit, it has a planet carrier with bearing pins, as well as a planet gear mounted on the bearing pin via a roller bearing. According to the invention, as already described above for the lubricating device, the thrust washer is correspondingly provided with a profile, i.e. shaped, on the one hand to form two contact surfaces lying on different radial planes via the profile or the geometry, and on the other hand the lubricant guide structure via which the radial lubricant supply to the rolling area takes place .

The profiling can be provided several times, at least in an outer pane section Hene, circumferentially offset depressions introduced from a first disk side and flat elevations corresponding to these and projecting on the opposite second disk side, the elevations forming the first contact surface, the depressions and the elevations preferably extending up to the outer edge of the thrust washer. As already described for the lubricating device, such a profiling of the thrust washer can be realized by a corresponding depression or elevation profile, which can be achieved by appropriate deformation of the metal strip from which the thrust washer is made.

Such a thrust washer with a lubricant guiding structure is expediently provided on both sides of the planet gear. This means that there is a quasi symmetrical structure. The rolling bearing, which is wider than the planetary gear as described, therefore projects axially beyond the planetary gear with its cage on both sides. The fact that a thrust washer with such a profile is provided on both sides of the planetary gear means that a corresponding, offset contact surface profile is provided on both sides, which takes into account the different widths of the planetary gear and rolling bearing. A corresponding lubricant supply in the sense of the invention is therefore possible on both sides, and ultimately a corresponding lubricating device is provided on both sides.

It is conceivable here to only provide a lubricant supply from the radial inside on one side, which means that the lubricant is only supplied to one side of the planetary gear and from there is distributed in the bearing area and flows out of it again, which of course also via the corresponding one Lubricant guiding structure can be done in the area of the respective thrust washer.

Of course, simultaneous lubricant supply on both sides is also conceivable.

In principle, it would also be conceivable to only provide a profiled thrust washer on one side and a flat thrust washer on the other side. The rolling bearing would therefore only protrude axially on one side, while on the other side there would be a common contact plane for the planetary gear and cage.

According to an expedient development of the invention, a lubricant trapping or guiding profile can be provided on a cage of the rolling bearing, which axially projects beyond the planet gear, at least on one side with which it is arranged adjacent to the profiled thrust washer. As described, the lubrication concept is based on the fact that the lubricant is supplied directly radially to the axially projecting cage or to its axially projecting ring edge via the lubricant guide structure of the thrust washer or in the thrust washer area. The invention now provides that this ring edge, i.e. the axially projecting edge of the cage, has a corresponding profiling which enables the inflowing lubricant to be captured or forwarded into the rolling element area. The cage therefore does not end with a flat end face or an unprofiled edge, but rather has a specific profile there.

Such a lubricant trapping or guiding profile can be designed in the form of a cage edge that widens conically in diameter towards a free end. The cage edge consequently widens conically towards the outside, so that a conical, annular outer surface of the ring rim is created, i.e. running at an angle to the longitudinal axis of the cage. The lubricant flows onto this, is captured there and is deflected axially into the rolling element area due to the inclined arrangement.

• 1 eine Prinzipdarstellung eines erfindungsgemäßen Planetengetriebes in einer geschnittenen Teilansicht mit einer erfindungsgemäßen Schmiervorrichtung,
• 2 eine Perspektivansicht eines erfindungsgemäßen Käfigs,
• 3 eine Seitenansicht des Käfigs aus 2,
• 4 eine Schnittansicht durch den Käfig aus 3,
• 5 eine Perspektivansicht eines Wälzlagers umfassend einen Käfig gemäß 1,
• 6 eine Perspektivansicht einer Anlaufscheibe einer ersten Ausführungsform,
• 7 eine Aufsicht auf die Anlaufscheibe aus 6,
• 8 eine Schnittansicht entlang der Linie VIII - VIII aus 7,
• 9 eine vergrößerte Teilansicht des Bereichs IX aus 8,
• 10 eine Perspektivansicht einer Anlaufscheine einer zweiten Ausführungsform,
• 11 eine Aufsicht auf die Anlaufscheibe aus 10,
• 12 eine Schnittansicht durch die Anlaufscheibe aus 11 entlang der Linie XII -XII,
• 13 eine vergrößerte Teilansicht des Bereichs XIII aus 12,
• 14 eine Perspektivansicht einer dritten Anlaufscheibe,
• 15 eine Aufsicht auf die Anlaufscheibe,
• 16 eine Schnittansicht durch die Anlaufscheibe entlang der Linie XVI - XVI in 15,
• 17 eine Aufsicht auf eine nicht erfindungsgemäße vierte Anlaufscheibe,
• 18 eine Schnittansicht entlang der Linie XVIII-XVIII in 17, und
• 19 eine Schnittansicht entlang der Linie XVIIII-XVIIII in 18.

The invention is explained below using exemplary embodiments with reference to the drawings. The drawings are schematic representations and show:

• 1 a schematic representation of a planetary gear according to the invention in a sectional partial view with a lubricating device according to the invention,
• 2 a perspective view of a cage according to the invention,
• 3 a side view of the cage 2 ,
• 4 a sectional view through the cage 3 ,
• 5 a perspective view of a rolling bearing comprising a cage according to 1 ,
• 6 a perspective view of a thrust washer of a first embodiment,
• 7 a top view of the thrust washer 6 ,
• 8th a sectional view along the line VIII - VIII 7 ,
• 9 an enlarged partial view of area IX 8th ,
• 10 a perspective view of a start-up note of a second embodiment,
• 11 a top view of the thrust washer 10 ,
• 12 a sectional view through the thrust washer 11 along the line XII -XII,
• 13 an enlarged partial view of area XIII 12 ,
• 14 a perspective view of a third thrust washer,
• 15 a view of the thrust washer,
• 16 a sectional view through the thrust washer along the line XVI - XVI in 15 ,
• 17 a top view of a fourth thrust washer not according to the invention,
• 18 a sectional view along line XVIII-XVIII in 17 , and
• 19 a sectional view along the line XVIIII-XVIIII in 18 .

1 shows a detail of a planetary gear 1 according to the invention. Such a planetary gear 1 has a sun gear unit, not shown here, whose axis of rotation defines the main axis of rotation of the gear. The sun gear unit has a sun gear and a sun shaft, wherein the sun gear is arranged on the sun shaft and is either a separate, attached component or in one piece with the sun shaft. A plurality of planet gears rotatably mounted on a planet carrier usually mesh with the sun gear, the sun gear being arranged concentrically within the planet gear arrangement. The planet gears would also come with a ring gear surrounding them. The basic structure of such a planetary gear is known.

The in 1 Shown detail of a planetary gear 1 shows the planet carrier 2, here consisting of two cheeks 3, on which corresponding bearing pins 4, of which in 1 only one is shown, are attached. Such a bearing bolt is a simple, solid bolt. The bearing pin 4 extends from one cheek 3 to the other.

A planetary gear 6 is rotatably mounted via a rolling bearing 5 comprising a cage 50 and the rolling elements 56 held or guided therein. The planet gear 6 has external teeth with which it meshes with the sun gear, not shown, on the one hand, and with the ring gear, also not shown, on the other hand.

A thrust washer 7 is arranged between the planetary gear 6 and the rolling bearing 5 and each of the cheeks 3, against which the planetary gear 6 with its respective axial end face as well as the cage 50 with its annular edges 51, which, like 1 shows, protrude axially over the planet gear 6, can start, and is therefore axially supported there. Each of the thrust washers 7 is supported axially on the respective cheek 3 on the other side. Each thrust washer has a first contact surface 8, formed by local elevations projecting axially on the respective disk body 9, the planet gear 6 running against this first contact surface 8 with its respective end face. The first contact area results from the sum of the areas of the flat elevations, so it is segmented, with the elevations being distributed equidistantly around the circumference. Each thrust washer 7 also has a second, annular contact surface 10, which is located radially further inward and is ultimately formed by the disk body 9. The respective axially projecting ring rim 51 runs with its end face against this second contact surface 10, which is set back axially relative to the first contact surface 8.

How 1 shows, this axial offset of the respective contact surfaces 8, 10 and consequently the axially different bearing levels results in a radially open lubricant guide structure 11, in the example shown on each of the two planet gear sides. The profiling of the thrust washer 7 or the thrust surface 8 over the elevations results in radially open channel or gap structures between the planetary gear 6 and the thrust washer 7, through which, as shown by the arrow P1, from the radially inside, i.e. from the sun gear side , supplied or inflowing lubricant or oil can flow in the direction of the rolling bearing 5. The oil, see arrow P2, flows directly onto the conical outer surface 59 of the funnel-shaped ring rim 51 (see 3 ) after it protrudes axially beyond the planet gear 6 as described and is directly accessible via the lubricant guide structure 11 in an exposed manner. The lubricant flows onto the inclined outer surface 59, over which it is axially deflected, as shown by the arrow P2, and reaches the area of the rolling elements 56. The lubricant is distributed there. This deflection gives it a directional component that directs the lubricant to the diagonally opposite side of the bearing. There, the lubricant can, as shown by the arrow P3, be driven radially outwards due to centrifugal force, and flow radially outwards via the lubricant guide structure 11, which is of course also open there, as finally shown by the arrow P4.

Of course, there is also a certain direct radial flow of lubricant, which means that the lubricant flowing in on the right side also flows out to a certain extent on the right side of the bearing. However, this is not shown in more detail here, since the main flow direction is defined via the oblique outer surface 59 and runs obliquely through the bearing.

In the event that also on the left side of the bearing, i.e. via the lubricant guide shown on the left Structure 11 a lubricant inflow takes place, which would also be possible in a targeted and controlled manner from the sun gear side, that is to say that a targeted supply would then take place on both sides, so a corresponding lubricant inflow would also result on this side via the sloping outer surface 59 there, whereby this Lubricant would then ultimately flow obliquely through the rolling bearing 5 to the right exit side.

Depending on where the respective lubricant supply takes place from the sun gear side, a corresponding lubricant distribution or a lubricant flow through the rolling bearing 5 can be controlled.

The rolling bearing 5 or the cage 50, which is in the 2-4 is shown in more detail, enables targeted capture and directing or steering of the inflowing lubricant after the respective oblique ring rim 51 protrudes axially beyond the planet gear 6 and is open or freely accessible radially from the lubricant supply side, resulting from the lubricant guiding structure 11 provided on the thrust washer 7, formed via the corresponding profiling of the respective thrust washer 7 via the corresponding elevations.

Of course, this lubricant supply also supplies lubricant to the respective contact surfaces 8, 10, where there is frictional contact between the cage 50 or the end face of the planet gear 6 and the respective contact disk 7.

If, on the side facing the respective cheek 3, the depressions introduced there, which form the elevations on the other side, are open radially outwards, corresponding lubricant catch pockets can form there, since the depressions are closed over the respective cheek 3 when viewed axially are. This can be used to form a lubricant reservoir and, in addition, the lubricant supply for any frictional contact between the thrust washer 7, which may be rotatably mounted on the bearing pin 4, and the cheek 3. In the event that the pockets have openings on the foot side, there would also be a passage of lubricant from the pockets the rolling bearing area possible.

2 shows the cage 50. The cage 50, which is preferably made of sheet metal, has two terminal ring rims 51, between which several webs 52 extend, which directly connect to the ring rims 51 at their ends. The webs 52 are, as in particular 3 shows, W-shaped, so have a web center 53 that is raised radially outwards, to which web ends 54 that are bent radially inwards are connected on both sides. The ring edges 51 adjoin these web ends 54. A pocket 55 is formed between two webs 52, in each of which there is a cylindrical, needle-shaped rolling body 56, see 5 , which shows the rolling bearing 4, is recorded and guided.

In the cage 50 according to the invention, the two edge edges 51 are funnel-shaped, that is, they expand in diameter towards their free end, as in particular 4 clearly shows. The diameter expansion is conical, which means that the funnel-shaped inner surface 58 as well as the corresponding outer surface 59 run in a straight line and at an angle to the longitudinal axis 60 of the cage 50. The angle that the respective ring edge 51 or the inner and outer surfaces 58, 59 has to the longitudinal axis 60 is, for example, 45°. It should generally be in the interval between 15° - 75°, especially between 30° - 60°.

The outer diameter of the free end edge of the respective ring rim 51 corresponds at most to the outer diameter in the area of the web center 53, so that the respective funnel-shaped annular rim 51 does not protrude radially beyond the web center 53.

The inclined, conical outer surface 59 of each ring rim 51 forms a lubricant guiding structure 61, via which, as will be discussed below, lubricant flowing in from the radial outside, regularly oil, is captured and forwarded.

5 As described, shows the rolling bearing 4 with the cage 50 and the needle-shaped rolling elements 56 inserted in its pockets 55, as in the planetary gear 1 is provided.

The 6 - 9 show a first exemplary embodiment of a thrust washer 100, which is used as a thrust washer 7 in the planetary gear 1 1 can be integrated. The thrust washer 100 is circular and profiled in a special way. It has depressions 102 introduced from one side of the pane 101, which, as passages, lead to corresponding flat elevations 103 on the opposite side of the pane 104. In the example shown, four such depressions 102 or elevations 103 are provided, which are distributed equidistantly around the circumference of the thrust washer 100. The depressions 102 extend by a certain angular increment in the circumferential direction and merge back into the undeformed area of the disk via a gentle bend. Seen radially, the depressions 102 only extend a little way to an inner disk section 105, which remains undeformed. In the transition of the respective recess 102 to the disk section 105 there is a relatively sharp, cranked transition zone 106, in which, see the enlarged detailed view according to 9 , the wall thickness is greatly reduced, which makes it possible to form a sharp step, as in 9 clearly shown.

Through this stepped design, two axially offset first and second contact surfaces can be realized, on which, on the one hand, the planetary gear 6 is supported with its end face, and on the other hand, the cage 50.

The first contact surface 107 is formed over the surfaces of the elevations 103. This means that the first contact surface 107 is segmented; it is composed of the four surface segments of the elevations 103. Compared to the inner disk section 102, this first contact surface 107, on which the planet gear 6 contacts, is axially offset, like that 8th and 9 show clearly.

A second contact surface 108 in the shape of a circular ring is formed over the undeformed inner disk section 105, the two contact surfaces 107, 108 being provided on the same side of the disk. It is clearly set back axially relative to the first contact surface 107. The cage 50 is guided on it or runs on it, whichever way 1 already described, the cage 50 axially projects beyond the planet gear 6.

In the assembly position, the axial washer 100 is in the same position as the axial washer 7 in 1 shown, with the disk surface 101 on the cheek 3. The first and second contact surfaces 107, 108 are arranged adjacent to the end face of the planet gear 6 and to the rolling bearing 5 and the cage 50, respectively. In this arrangement, corresponding channels 109 are formed between the elevations 103, resulting from the undeformed sections of the thrust washer 100 located between them. These channels 109 are radially open and run in a quasi V-shape to the central axis of the thrust washer 100. They can be used in the assembly position according to arrow P1 in 1 supplied lubricant flows radially into the area of the first and second contact surfaces 107, 108 and into the area of the rolling bearing 5, so a channel structure that is open towards the rolling bearing 5 is formed. The oil consequently wets the contact or friction areas between the individual friction partners, just as it also supplies the rolling bearing 5. The oil migrates through the bearing and friction area and can also escape radially outwards via this channel structure.

The depressions 102, which are covered axially by the cheek 3, are also open radially outwards. The depressions 102 define corresponding pockets that serve as reservoirs and into which the lubricant can also flow from the radially inside via the arrow P1. This virtually ensures a rear lubricant supply, since the lubricant can wet the contact area between the disk side 101 and the cheek 3, where friction can also occur when the axial disk 100 is rotatably mounted on the bearing pin 4.

As a result of the profiling of the thrust washer 100 according to the invention, on the one hand, a corresponding support of the planetary gear 6 and the cage 50 is ensured, the support being provided here in two separate axial planes due to the axial offset of the contact surfaces 107, 108. On the other hand, the structure with the depressions 102 or elevations 103 offers the possibility of the best possible lubricant supply, since a corresponding guide channel structure is formed here, in conjunction with any lubricant reservoirs via the depressions 102, so that on the one hand the actual rolling bearing area is very well supplied with lubricant is, but on the other hand also the corresponding friction or contact areas on the thrust washer 100. This makes it possible to dispense with a lubricant supply to the rolling area via the bearing pin 4 and to supply the lubricant solely via the sun gear side from radially inside via the thrust washer arrangement.

A second embodiment of a thrust washer 200 according to the invention, which is used as a thrust washer 7 in the planetary gear 1 according to 1 can be used is in the 10 - 13 shown. The thrust washer 200 also has several depressions 202 introduced from the disk side 201, in the example shown also four depressions, as well as corresponding flat elevations 203 projecting on the disk side 204. The depressions 202, of which four are also provided here, for example, are again offset equidistantly around the circumference and merge into the neighboring, undeformed pane area via gentle bends. However, similar to the previous exemplary embodiment, they only extend radially to an inner disk section 205, which remains undeformed. This results in a corresponding stepped structure, with a first contact surface 207, which is segmented and is formed over the surfaces of the individual elevations 203, like a second contact surface 208, which is provided via the undeformed disk section 205.

Unlike the design according to the 6 - 9 There is no offset transition zone 206 here. Rather, the transition zone 206 is provided with an opening 209, which is like an elongated hole and extends essentially over the length of the Depression 202 extends. The two disk sides 201 and 204 communicate with each other via these openings.

In the assembly position, the thrust washer 200 lies with its disk side 201 against the cheek 3, while the disk side 204 with the two contact surfaces 207, 208 is adjacent to the planet gear 6 and the rolling bearing 5, respectively. Again, the planet gear 6 runs on the first segmented contact surface 207, while the cage 50 runs on the annular contact surface 208.

The profiling also results in a corresponding formation of guide channels 210 between two adjacent elevations 203, as already described for the above embodiment. Here too, the guide channels 210 are quasi V-shaped and open directly onto the cage 50, which is supported radially on the inside on the contact surface 208. This means that via these guide channels 210 or the guide channel structure in the same way as in the embodiment according to 6 to 9 The lubricant supplied via the arrow P1 is supplied on the one hand to the two contact surfaces 207, 208, but on the other hand also directly to the rolling bearing 5.

As described, the recesses 202 of the cheek 3 are arranged opposite each other here, and are thus virtually overlapped by the cheek 3, so that corresponding pockets are also formed here. However, these are radially open here through the openings 209, so that the lubricant flowing into the recesses 202 can also reach directly into the rolling bearing area through the openings 209. Here, the rolling bearing supply takes place not only via the guide channels 210, but also via the depressions 202 and the openings 209.

Another thrust washer 300, which acts as a thrust washer 7 in the planetary gear 1 can be used is in the 14 - 16 shown. 14 shows a perspective view of this thrust washer 300, which has a first disk side 301, from which several, in the example shown, four recesses are made, so that recessed disk sections 302 are formed on this side, while correspondingly raised disk sections 304 are formed on the opposite disk side 303 . Inevitably, corresponding raised disc sections 305 remain on the disc side 301 between two recessed disc sections 302 because they have not been formed, while on the opposite disc side 303 between the raised disc sections 304 there, respective recessed disc sections 306 are formed. This results in a disk section structure consisting of raised and recessed disk sections alternating in the circumferential direction on both disk sides 301, 303.

On the disk side 303, which faces the planet gear 6 in the assembly position, the raised flat sections 304 form a first segmented contact surface for the planet gear. These raised disc sections 304 extend over the entire disc width, inevitably also the recessed disc sections 302 provided on the other side.

The recessed disc sections 306, seen from the disc side 303, are provided with radially inwardly projecting projections 307, i.e. extended radially inwards, these projections defining the inner bore diameter through which the thrust washer 300 rests on the bearing pin 4. A corresponding recess 308 is therefore formed between two adjacent projections 307, which means that the thrust washer 300 is axially open here.

If the thrust washer 300 is now mounted, the disk side 301 rests against the cheek 3 of the planet carrier 2 as described, and is therefore partially or segmentally supported there. The opposite disk side 303 faces the planet gear 6. This is also axially on the first contact surface 309, see 16 , formed via the flat, raised disk sections 304, axially supported.

The projections 307, on the other hand, form a second axial contact surface 310 on the disk side 303, see 16 , on which the cage 50 is axially supported. This second support surface 310 is also segmented, formed over the four surfaces of the projections 307 on the disk side 303.

In the assembly position, as stated, the disk side 301 rests on the cheek 3 of the planet carrier 2, the disk side 303 faces the planet gear 6. Due to the corresponding profiling with the recessed and raised disk sections, both between the thrust washer 300 and the cheek 3 are formed the thrust washer 300 and the planet gear, which are open radially towards the outer circumference and towards the inner circumference, through which the lubricant flows from the radial outside from the sun gear side, as indicated by the arrow P1 in 1 shown, supplied and can pass radially through the thrust washer 300. Each disk section 302 or 306 recessed on the disk side 301 and 303 defines such a channel in conjunction with the cheek 3 or the planet gear 6 that overlaps it. The lubricant flows through this channel.

If the channel is formed via the recessed disk sections 306, the lubricant reaches, on the one hand, the area of the first contact surface 309, which is located radially further out, and into the area of the second contact surface 310, which is located radially further inside, on the projections 307. Because the lubricant flows directly along the corresponding recessed disk section 306 to the cage and from there to the rolling bearing. If the fluid flows via the channels formed via the recessed sections 302, i.e. from the other side of the disk, the lubricant also reaches the area of the rolling bearing via the corresponding recesses 308, since it can pass axially through the disk through the recesses 308. In addition, the friction or contact area between the thrust washer 300 and the cheek 3 can also be very well supplied with lubricant via the lubricant inflow on this side.

The 17 to 19 show an embodiment not according to the invention of a thrust washer 400, which is used as a thrust washer 7 in the planetary gear 1 1 can be integrated. The thrust washer 400 is circular and profiled in a special way. It has first recesses 402 made in an outer pane section from one pane side 401, which lead as passages to corresponding elevations 403 on the opposite pane side 404. In the example shown, four such depressions 402 or elevations 403 are provided, which are distributed equidistantly around the circumference of the thrust washer 400. As the figures show, the depressions 402 are open towards the outer circumference, but are closed in the circumferential direction and in particular towards the inner circumference. In the example shown, they extend over slightly more than half the width of the annular disk body.

Second depressions 405 are also provided, which are made on an inner pane section and lead to corresponding elevations 406 on the opposite pane side 404. These second recesses 405, which are open towards the inner circumference, are also closed in the circumferential direction and towards the outer circumference; they only extend over approximately 1/3 of the width of the disk body, like 17 shows. Here too, four depressions 405 distributed equidistantly around the circumference and of course corresponding elevations 406 are provided.

The elevations 403 and 406 are flat elevations, so they have flat side surfaces. These flat elevations 403 form a first segmented contact surface 407, against which the planetary gear 6 abuts on the front side in the assembly position. In contrast, the second flat elevations 406 form a second contact surface 408 located radially further inwards, against which the cage 50 abuts. This second contact surface 408 is also segmented. Due to the segmentation of the two contact surfaces 407, 408, there is only a smaller contact area between the contact disk 400 and the planet gear 6 or the cage 50, so that the friction can be reduced.

In the example shown, the two contact surfaces 407, 408 are arranged in a common axial plane, which means that the corresponding elevations 403, 406 protrude axially at the same distance from the undeformed disk body. This means that the cage 50 of the rolling bearing 5 cannot axially project beyond the planetary gear 6, and therefore can have a maximum of the axial length of the planetary gear 6.

To use this type of thrust washer in the planetary gear 1 To be able to use the axially projecting rolling bearing 5, it is possible to arrange the first and second contact surfaces 407, 408 axially offset from one another, i.e. to form the second contact surface 408 axially set back with respect to the first contact surface 407. The respective elevations would therefore be of different heights, with the outer elevations forming the contact surface 407 protruding further from the disk body than the inner elevations which form the second contact surface 408. The second contact surface 408 then protrudes less far from the undeformed disk body. This makes it possible to use a cage 50 that projects axially beyond the planet gear 6 and, associated with it, possibly somewhat longer rolling elements in the form of needles.

How 17 shows, the depressions 402, 405 and the resulting elevations 403, 406 are arranged offset from one another in the circumferential direction and positioned in a gap. This results in a channel structure 409 that is open radially to both the outer circumference and the inner circumference, which means that corresponding channels are formed between the elevations in the assembly position, through which the lubricant can flow from radially outside to radially inside. In the assembly position, the disk side 404 points towards the planet gear 6, which means that the recessed disk areas lying between two elevations 403 are overlapped by the planet gear. Likewise, the cage extends over the undeformed disk areas lying between the elevations 406. This results in corresponding guide channels that are open radially outwards and radially inwards, so that the radial flow is possible via this lubricant guide or channel structure 409. Via this flow, the lubricant is, on the one hand, conveyed into the area of the first and second contact surfaces 407, 408 and can lubricate them, on the other On the other hand, the lubricant also flows into the rolling bearing area and supplies it. The overlap results in a corresponding branched channel structure 409, whereby the geometry and size of the channel structure 409 can of course be influenced and adjusted via the corresponding positioning or spacing of the individual elevations 403 and 406 as well as their specific size, so that the lubricant inflow is ultimately controlled here can be.

As described, the thrust washer 400 lies with the disk side 404 and thus with the elevations 403, 406 adjacent to the planet gear 6 and the cage 50. As a result, the disk side 401 lies adjacent to the cheek 3 of the planet carrier 2, against which it rests when starting. This results in the cheek 3 axially covering the depressions 402 and 405, so that corresponding, then closed pockets are formed over the depressions 402, 405, which serve as lubricant reservoirs. The radially outwardly open pockets, formed via the depressions 402, are filled by the lubricant flowing on the sun gear side and provide a lubricant reservoir in particular for the frictional contact between the thrust washer 400 and the cheek 3. The pockets formed via the depressions 405 are filled either by a flow of lubricant between the thrust washer 400 and the cheek 3, which means that a minimal lubricating gap remains, or from the inside, so to speak, from the side of the bearing pin 4 on which the thrust washer 400 sits. This creates a lubricant reservoir close to the bolt.

Reference symbol list

1

Planetary gear

2

Planet carrier

3

cheek

4

bearing pin

5

roller bearing

6

Planetary gear

7

thrust washer

8th

contact surface

9

disc body

10

contact surface

11

Lubricant guiding structure

50

Cage

51

Ring border

52

web

53

middle of the bridge

54

End of the jetty

55

Bag

56

rolling elements

57

roller bearing

58

Inner surface

59

external surface

60

Longitudinal axis

61

Lubricant guiding structure

100

thrust washer

101

disc side

102

deepening

103

survey

104

disc side

105

Disc section

106

Transition zone

107

contact surface

108

contact surface

109

channel

200

thrust washer

201

disc side

202

deepening

203

survey

204

disc side

205

Disc section

206

Transition zone

207

contact surface

208

contact surface

209

Breakthrough

210

Guide channel

301

disc side

302

Disc section

303

disc side

304

Disc section

305

Disc section

306

Disc section

307

head Start

308

recess

309

contact surface

310

contact surface

400

thrust washer

401

disc side

402

deepening

403

survey

404

disc side

405

deepening

406

survey

407

contact surface

408

contact surface

409

Channel structure

Claims (8)

Lubrication device for a planetary gear bearing of a planetary gear (1) with a planetary carrier (2), at least one bearing pin (4) arranged thereon, a rolling bearing (5) arranged on the bearing pin (4), a planetary gear (6) mounted via the rolling bearing (5) and two thrust washers (7; 100; 200; 300), which are arranged on both sides of the planet gear (6) between the planet gear (6) and the planet carrier (2) and each have contact surfaces (8; 10; 107; 108; 207; 208; 309 ; 310) for the planet gear (6) and the rolling bearing (5), with between the planet carrier (2) and at least one adjacent thrust washer (7; 100; 200; 300) and/or between at least one thrust washer (7; 100; 200; 300) and the adjacent planet gear (6) there is a lubricant gap that is open radially outwards, via which lubricant supplied from radially outside the thrust washer (7; 100; 200; 300) is fed to the roller bearing (5) which axially projects beyond the planet gear (6). ) can be guided, characterized in that the one-piece thrust washer (7; 100; 200; 300) has a lubricant guide structure (11; 109; 210) which allows the radial flow of lubricant from radially outside to radially inside and defines the lubrication gap, and that the thrust washer (7; 100; 200; 300) has a profiling over which, on the one hand, a radially outer first contact surface (8; 107; 207; 309) for the planet gear (6) and a radially inner second contact surface (10; 108; 208; 310) for the rolling bearing (5) is formed, the second contact surface (10; 108 ; 208; 310) is set back axially with respect to the first contact surface (8; 107; 207; 309) and the rolling bearing (5), viewed axially, is wider than the planet gear (6), and via which, on the other hand, the lubricant guide structure (11; 109; 210 ) is formed, the profiling being a plurality of depressions (102; 202; 302), provided at least in an outer pane section, offset in the circumferential direction and introduced from a first side of the pane, as well as flat elevations corresponding to these and projecting on the opposite second side of the pane (103; 203; 304), the elevations (103; 203; 304) forming the first contact surface (8; 107; 207; 309). Lubrication device after Claim 1 , characterized in that the depressions (102; 202; 302) and the elevations (103; 203; 304) extend to the outer edge of the thrust washer (7; 100; 200; 300). Lubrication device after Claim 1 or 2 , characterized in that the thrust washer (200; 300) has one or more axial openings (209) or recesses (308) which allow an axial flow of lubricant. Planetary gear with a planet carrier (2), at least one bearing pin (4) arranged thereon, a rolling bearing (5) arranged on the bearing pin (4), a planet gear (6) mounted above the rolling bearing and two thrust washers (7; 100; 200; 300) , which are arranged on both sides of the planet gear (6) between the planet gear (6) and the planet carrier (2) and each have contact surfaces (8, 10; 107; 108; 207; 208; 309; 310) for the planet gear (6) and the Have rolling bearings (5), characterized in that at least one one-piece thrust washer (7; 100; 200; 300) is provided with a lubricant guiding structure (11; 109; 210) which allows a radial flow of lubricant from radially outside to radially inward, and that the thrust washer (7; 100; 200; 300) has a profiling, on the one hand a radially outer first contact surface (8; 107; 207; 309) for the planet gear (6) and a radially inner second contact surface (10; 108; 208; 310) is formed for the rolling bearing (5), the second contact surface (10; 108; 208; 310) is set back axially with respect to the first contact surface (8; 107; 207; 309) and the rolling bearing (5), viewed axially, is wider than the planet gear (6), and via which, on the other hand, the lubricant guide structure (11; 109; 210) is formed , wherein the profiling comprises a plurality of depressions (102; 202; 302), which are provided at least in an outer pane section and are offset in the circumferential direction and introduced from a first pane side, as well as flat elevations (103; 203; 103; 203; 304), the elevations (103; 203; 304) forming the first contact surface (107; 207; 309). Planetary gear Claim 4 , characterized in that the depressions (102; 202; 302) and the elevations (103; 203; 304) extend to the outer edge of the thrust washer (100; 200; 300). Planetary gear Claim 4 or 5 , characterized in that such a thrust washer is on both sides of the planet gear (6). (7; 100; 200; 300) is provided with a lubricant guiding structure (11; 109; 210). Planetary gear according to one of the Claims 4 until 6 , characterized in that on a cage (50) of the rolling bearing (5), which axially projects beyond the planet gear (6), at least on the side with which it is arranged adjacent to the profiled thrust washer (7; 100; 200; 300). , a lubricant catch or guide profile (61) is provided. Planetary gear Claim 7 , characterized in that the lubricant trapping or guiding profile (61) is designed in the form of a cage edge (51) which widens conically in the diameter towards a free end.

Images