Lubrication device for planetary gear bearings of a planetary transmission, and planetary transmission

Abstract

A lubrication device for planetary gear bearings of a planetary transmission (1), the planetary transmission (1) comprising a planet carrier (2) with two carrier webs (3), at least one bearing pin (4) arranged on the carrier webs (3), a rolling bearing (5) arranged on the bearing pin (4), a planetary gear (8) mounted via the rolling bearing (5), and two thrust plates (9) arranged on both sides of the planetary gear (6) between the planetary gear (6) and the carrier webs (2). at least one channel-like recess (12, 14) is formed on at least one carrier web (3) on its surface facing the planetary gear (8), via which lubricant fed from the radial outside of the thrust plate can be fed to a bearing area in the area between the thrust plate and the carrier web (3) or lubricant flowing out from the bearing area can be discharged radially to the outside in the area between the thrust plate and the carrier web (3).

Description

Technical Field

[0001] The present invention relates to a lubrication device for a planetary gear bearing of a planetary transmission, wherein the planetary transmission has a planetary carrier with two carrier webs, at least one bearing pin arranged on the carrier web, a rolling bearing arranged on the bearing pin, a planetary gear attached via the rolling bearing, and two thrust plates arranged on both sides of the planetary gear between the planetary gear and the carrier web.

Background Art

[0002] Planetary transmissions are used in a wide variety of fields, for example in motor vehicles, where they are used, for example, in the drive train of a transmission or an electric drive unit, specifically in an electric axle or a hybrid drive train. Such planetary transmissions usually have a planetary carrier with at least one, but usually a plurality of planetary gears, which are arranged eccentrically and offset from each other in the circumferential direction and are attached to bearing pins provided on the carrier side via respective rolling bearings. An annular thrust plate is arranged between the planetary gear or the rolling bearing and the planetary carrier, and the thrust plate is formed, for example, by two parallel webs and enables at least the axial contact of the axially slightly displaceable planetary gear. A rolling bearing consisting of a cage in which a plurality of rolling elements, usually cylindrical needles, are received or guided can also optionally contact such a thrust plate and extend axially.

[0003] As the planetary gears rotate during operation, lubrication of the bearing area with a lubricant is necessary. For this purpose, it is known that a lubricant, usually oil, is supplied via a bearing pin configured as a hollow pin and having an axial bore and at least one radial bore (see, for example, the planetary transmission known from German Patent Application Publication No. 19736686(A1)), thereby allowing the lubricant to be supplied axially to the pin and radially to the bearing area. To guide the lubricant into the hollow bearing pin, a lubricant collection tray must generally be provided to capture the lubricant and guide it laterally outward from the planetary carrier. The lubricant collection tray is connected to the bearing pin so that the lubricant can be guided directly into the bearing pin through the collection tray. This means that a considerable amount of effort must be made to realize the corresponding lubricant supply to the bearing area, as this requires the use of a special perforated pin on the one hand, and the placement of a corresponding supply structure with a lubricant collection tray on the other hand, and corresponding precautions to secure it. [Overview of the Initiative] [Problems that the invention aims to solve]

[0004] The present invention aims to provide an improved lubrication device for planetary gear bearings of a planetary transmission. [Means for solving the problem]

[0005] To achieve this objective, in the lubrication device of the type described first, according to the present invention, at least one channel-shaped recess is introduced on the surface of at least one carrier web facing the planetary gear, through which lubricant supplied from the radially outside of the thrust plate can be supplied to the bearing region within the region between the thrust plate and the carrier web, or lubricant flowing from the bearing region can be discharged radially to the outside within the region between the thrust plate and the carrier web.

[0006] In the lubrication device according to the present invention, the lubricant is supplied directly from the sun gear side, i.e., the lubricant is supplied to the planetary gears from the radially inward side of the planetary gear set. To enable the supply of lubricant from the radially inward side to the bearing area, the present invention provides the formation of a lubrication channel defined in the region between the thrust plate and the carrier web of the planetary carrier, the channel opening radially outward. For this purpose, the surface of at least one carrier web facing the planetary gear is provided with a channel-shaped recess opening at least radially outward, thereby allowing entry from the sun gear side when the lubricant is supplied radially. Through this lubrication channel, the lubricant is then transported to the bearing or rolling area, where it is distributed accordingly. Viewed axially, the thrust plate is provided adjacent to the carrier web and abuts against the carrier web when in contact. Since the lubrication channel in the carrier web is introduced through a recess in the surface, the lubrication channel is always open so that the lubricant can always be supplied through it. Of course, in order to further increase the radially open cross-section, it is also conceivable to form a corresponding guide structure on the thrust plate, thereby creating a correspondingly larger radially open lubrication gap, in which part of the lubrication gap may be a channel-shaped recess, or this recess may communicate with the lubrication gap so that the total amount of lubricant that can be supplied can increase accordingly.

[0007] However, it is also conceivable to form such channel-like depressions in the carrier web for the purpose of releasing lubricant from the rolling region. These depressions allow the lubricant to be released radially outward after flowing through the bearing. In this case as well, a thrust plate is provided adjacent to the depression, and a corresponding lubricant guide structure is also provided if necessary. However, in either case, a corresponding supply of flowing lubricant to the channel-like depression is possible, and the channel-like depression may also be part of a larger volume lubricant guide structure that opens radially outward.

[0008] Overall, the design of the lubrication device according to the present invention allows for improved lubrication supply to the rolling region, as one or both carrier webs can be integrated into the radial lubrication supply and radial lubrication discharge sections via their channel-like recesses that support centrifugal-driven lubrication supply.

[0009] Preferably, if only one recess is provided in the carrier web, this recess is positioned to allow improved lubricant delivery to the rolling area and thus enable radial lubrication from the sun gear side. Such an integrated lubrication device makes it possible to achieve simplified lubricant delivery without requiring specific bearing pins or other supply components. This is because neither hollow drill bearing pins, lubricant collection trays, nor other precautions are required. In the simplest design, only a corresponding channel-shaped recess in the carrier web needs to be provided, through which a corresponding supply channel is formed, enabling radial lubrication flow together with, or supported by, a lubricant guide structure on an adjacent thrust plate, as needed. The components provided as needed, namely the lubricant or channel structure realized using the carrier web and possibly together with the thrust plate, thus enable direct lubricant delivery or direct radial lubricant flow to the bearing area without requiring additional components.

[0010] In a particularly advantageous further development, at least one channel-shaped recess is provided on both carrier webs, offset from each other with respect to the axis of the bearing pin, with one recess positioned further inward radially relative to the rotation axis of the planetary transmission than the other recess. Preferably, the channel-shaped recess, and thus the channel structure, is provided on both carrier webs and preferably embossed. However, the two recesses are offset from each other circumferentially with respect to the bearing axis of the planetary pin. One recess is positioned further inward radially relative to the rotation axis of the planetary transmission, and the other recess, in contrast, is positioned further outward radially. This allows for the definition of an inlet side and an outlet side. On the inlet side, the channel-shaped recess is positioned further inward, i.e., closer to the central planetary transmission axis, so that the fluid flowing in from the sun gear side has a shorter path and can therefore flow directly into the channel structure which is radially open toward the sun side. The channel-shaped recess formed on the other carrier web is preferably offset by 180° from it, thereby further separating it from the sun gear side. This defines the outlet side, but allows for easier lubricant flow after the lubricant has been driven radially outward. Preferably, as described above, the two recesses are positioned offset from each other by 180° around the circumference of the pin.

[0011] The recesses are, conveniently, elongated, and their longitudinal axes extend perpendicular to the rotation axis of the planetary transmission. They extend radially with respect to the central axis, but are offset from each other by 180°.

[0012] Each carrier web has a through-hole into which a bearing pin is inserted. The two channel-like recesses conveniently open directly at the through-holes, i.e., at the bearing pin, so that fluid flowing in radially from the interior at the inlet side, i.e., from the sun gear side, can flow directly to the bearing pin and then be distributed axially from the bearing pin if the fluid has not yet been axially guided into the bearing area beforehand. At the outlet side, lubricant can also be discharged by flowing directly from the bearing pin into the lubrication channels on the web side.

[0013] According to a particularly advantageous development of the present invention, as already described, there is a radially outward-opening lubricant gap between the carrier web and the thrust plate having adjacent recesses, through which lubricant can be supplied or released. As described above, the lubricant guide structure is preferably formed by the corresponding design of the thrust plate adjacent to the recess and is configured as a radially open gap or channel structure, i.e., when such recesses are provided on both sides, corresponding gaps are formed on both the inlet and outlet sides, and the gaps define a correspondingly large opening cross section. This is particularly advantageous on the inlet side, as a sufficiently large amount of lubricant can be supplied from the sun gear side and then distributed to the rolling region through this lubricant guide structure, which is also part of the recess in the carrier web. Such a structure is also useful on the outlet side to allow for the release of an appropriate amount of lubricant.

[0014] To form such a lubricant-guiding structure, the thrust plate may have a plate body, on a first plate side of the plate body, a plurality of pocket-like first recesses that open outward and close inward, optionally provided, a plurality of pocket-like second recesses that open inward and close outward, on the opposite second plate side, flat first and second protrusions corresponding to the first and second recesses, the surface sections of the plate body disposed between the first recesses form a segmented first thrust plate, optionally, the surface sections of the plate body disposed between the second recesses form a segmented second contact surface, and the first and second protrusions are spaced apart from each other to create a channel structure that opens from the outer to the inner circumference. Thus, the thrust plate is contoured by the corresponding recesses and protrusions, which define a radially open channel structure on the one hand, and also define the corresponding contact surface on the other hand. When such a separate thrust plate is used, the thrust plate abuts the carrier web at a raised portion that extends from the plate body. On the other hand, the opposite side of the plate body forms corresponding contact surfaces, namely a radially outer contact surface for the planetary gear and a radially inner contact surface for the rolling bearing cage, which, depending on the design of the axial plate, are fully positioned within the planetary gear bore, i.e., as flush as possible with the planetary gear bore, or may protrude slightly axially from the planetary gear. The raised portion forms a pocket closed radially inward, and also a pocket closed radially outward, if provided, forming a channel structure that is radially outward and inward open as a whole, allowing radial inflow and radial outflow. This channel structure or gap structure also communicates with a web-side recess.Lubricant received within closed pockets is retained there and can act as a lubricant reservoir, and after these pockets open to the planetary gears or cage, the gears and cages are lubricated accordingly in the event of contact; that is, lubricant is also supplied to this contact zone. Note that the second radially inward recess is not essential, and an undeformed plate body may be provided in the inner circumferential region to create an annular plate surface as a second contact surface supporting the cage. However, forming a recess on the other side, thereby creating a raised portion, is useful for supporting the thrust plate on the web.

[0015] If a first and a second recess exist, they preferably overlap each other when viewed circumferentially, so as to create a corresponding channel structure that is preferably arranged in a staggered pattern, preferably extending from the radially outer to the radially inward, and not interrupted at any point, but at most slightly angled due to possible overlaps.

[0016] If the thrust plate is produced by molding, the axial depth of the recess and therefore the height of the protrusion must also be selected depending on whether the cage is as flush as possible with the end face of the planetary gear, i.e., whether the width of the cage corresponds to the maximum width of the planetary gear when viewed in the axial direction, or whether the cage is slightly wider and therefore slightly protrudes axially on one or both sides of the planetary gear. It is conceivable that the first and second contact surfaces lie in a common plane, which is useful when the axial width of the cage corresponds to the axial width of the planetary gear. However, if the cage is somewhat long, the second contact surface is advantageously set back axially from the first contact surface, i.e., the cage that slightly protrudes from the planetary gear is guided into the second contact surface which is axially offset in proportion to the first contact surface.

[0017] The first recess may be deeper than the second recess in the radial direction. As described above, the first recess is located on the outer circumference or further offset outward and opens radially outward. Between these recesses, the undeformed plate body forms the first contact surface of the planetary gear and extends in contact with the first contact surface and integrally with its end face. On the one hand, due to the radially deeper pocket, the entire contact surface may be reduced accordingly to reduce the frictional contact provided by the segmented first contact surface of the planetary gear end face. On the other hand, this inevitably results in a correspondingly larger pocket volume, and therefore the reservoir volume is correspondingly larger.

[0018] The recess, specifically the outer first recess, is conveniently configured to be slightly trapezoidal in shape, so as to generate a correspondingly large radial catch opening cross-section.

[0019] To further improve not only lubricant supply but also discharge, it is conceivable to provide a lubricant guidance structure on at least one axial side, and if necessary, both sides, to guide the incoming or outgoing lubricant on the cage. This lubricant guidance structure can be realized by corresponding contours in the axial end regions of the cage, and thus may have a positive effect on lubricant supply or discharge.

[0020] Lubricant guide structures may be realized by contours formed on the axial end face of the annular rim of the cage, and / or contours formed on the inner and / or outer circumference of the annular rim, and / or by cage edges that widen conically in diameter toward the free end, and / or by grooves provided on the outer side of the rib and extending along the rib. For example, the axial end face of the annular rim may have contours of alternating depressions and protrusions, for example, in the form of a corrugated contour. As a result, channel structures or pocket structures may be realized in this region, through which lubricant flowing radially from the sun side can be received. Alternatively or additionally, corresponding contours may be provided on the outer and / or inner circumference of the radial rim in the form of alternating protrusions and depressions, which serve to axially transport the lubricant to the rolling element region. Cage edges may also widen in diameter in a quasi-conical manner to define an obliquely extending annular trapping surface, through which radially flowing lubricant can be received and axially deflected toward the bearing region. Such a cage protrudes axially beyond the planetary gear so that radially supplied lubricant directly impacts the catch cone. Alternatively or additionally, each rib may be provided with a longitudinal groove-like recess on its outer side, which, while receiving and guiding the lubricant axially, also acts as a lubricant reservoir, supplying lubricant to the friction region of the cage guided outward within the planetary gear bore. Therefore, different designs are possible for the possible lubricant guidance structures on the cage side.

[0021] In addition to the lubrication device itself, the present invention further relates to a planetary transmission comprising a planetary carrier having two carrier webs, at least one bearing pin disposed on the carrier webs, a rolling bearing disposed on the bearing pin, a planetary gear mounted via the rolling bearing, and two thrust plates disposed on both sides of the planetary gear between the planetary gear and the planetary carrier, each having a contact surface for the planetary gear and the rolling bearing, and further comprising the lubrication device of the type described above.

[0022] The planetary transmission is preferably part of the drivetrain of an electric drive unit such as an electric axle or hybrid drivetrain. In addition to the sun gear unit, it has planetary carriers having bearing pins and planetary gears mounted on the bearing pins via rolling bearings. According to the present invention, as already described above with respect to the lubrication device, one or preferably both carrier webs are provided with corresponding channel-shaped recesses, and optionally, the thrust plates or both thrust plates are also provided with corresponding contours, i.e., corresponding contours are formed.

[0023] Such lubricant guide structures are conveniently provided on both sides of the planetary gear, thereby creating a defined inlet side on the one hand, from which the lubricant is primarily supplied to one side of the gear, and a defined outlet side from which the majority of the lubricant flowing axially through the rolling bearings is discharged axially. This means that the lubricant is introduced on only one side of the planetary gear, from there distributed to the bearing area, and then flows out again, which happens on the other side of the planetary gear. To some extent, especially if well-contoured thrust plates are provided on both sides, at least corresponding lubricant outflow is provided on both sides of the gear, but the lubricant on the inlet side is given an axial flow direction that transports the lubricant into the bearing area quasi-axially, so the majority of the lubricant flows out to the opposite outlet side.

[0024] As described above, the cage can have a width corresponding to the width of the planetary gear. Alternatively, it can protrude axially beyond the planetary gear, which means that the lubricant supplied radially from the sun gear side can flow directly onto the annular rim of the cage or onto the lubricant guide structure provided thereon, which specifically improves the supply to the rolling region if the corresponding lubricant guide structure is provided on the annular rim via a contour.

[0025] The present invention is described below based on exemplary embodiments with reference to the drawings, which are schematic diagrams. [Brief explanation of the drawing]

[0026] [Figure 1] The schematic diagram of the planetary transmission according to the present invention is shown as a partial cross-sectional view having the lubrication device according to the present invention. [Figure 2] An enlarged partial view of region II of FIG. 1 is shown as a perspective view. [Figure 3] An enlarged partial view of region III of FIG. 1 is shown as a perspective view. [Figure 4] The top view of the thrust plate of the planetary transmission of FIG. 1 is shown. [Figure 5] The cross-sectional view of the thrust plate along line V-V of FIG. 4 is shown. [Figure 6] The cross-sectional view along line VI-VI of FIG. 4 is shown. [Figure 7] The perspective view of the cage of the first embodiment that can be used in the planetary transmission according to FIG. 1 is shown. [Figure 8] The side view of the cage of FIG. 7 is shown. [Figure 9] The cross-sectional view of the cage of FIG. 8 is shown. [Figure 10] It is a perspective view of a rolling bearing provided with such a cage. [Figure 11] It is a perspective view of a rolling bearing of a further embodiment having a cage of the second embodiment. [Figure 12] The longitudinal cross-sectional view of the rolling bearing of FIG. 11 is shown. [Figure 13] It is a perspective view of a further usable rolling bearing having another embodiment of the cage. [Figure 14] The longitudinal cross-sectional view of the rolling bearing of FIG. 12 is shown. [Figure 15] The perspective view of a rolling bearing of a further embodiment having a cage of another design is shown. [Figure 16] The top view of the rolling bearing of FIG. 15 is shown. [Figure 17] It is the longitudinal cross-sectional view of the rolling bearing of FIG. 15. [Figure 18] The perspective view of a further usable rolling bearing having a thrust plate with the cage integrally formed is shown. [Figure 19]Figure 18 shows an enlarged view of a rolling bearing having an integrally formed thrust plate. [Figure 20] This shows a cross-sectional view of an annular rim, where an integrally formed thrust plate is located in the rib region. [Figure 21] This is a cross-sectional view of an annular rim, where an integrally formed thrust plate is located in the pocket area. [Modes for carrying out the invention]

[0027] Figure 1 shows a cross-section of a planetary transmission 1 according to the present invention. Such a planetary transmission 1 comprises a sun gear unit having a rotating shaft that defines the main rotation axis of the transmission. The sun gear unit comprises a sun gear and a sun shaft, the sun gear being positioned on the sun shaft and being a separate mounted component or being integrated with the sun shaft. Typically, a plurality of planetary gears rotatably mounted on a planetary carrier mesh with the sun gear, the sun gear being arranged concentrically within the planetary gear configuration. The planetary gears also mesh with a ring gear surrounding them. The basic structure of such a planetary transmission is known.

[0028] The details of the planetary transmission shown in Figure 1 are shown here, with a planetary carrier 2 consisting of two webs 3, to which corresponding bearing pins 4 are attached, only one of which is shown in Figure 1. Such bearing pins 4 are simple solid material pins. The bearing pins 4 extend from one carrier web to the other carrier web 3.

[0029] The planetary gear 8 is rotatably mounted by a rolling bearing 5 comprising a cage 6 and rolling elements 7 held or guided within it. The planetary gear 8 has an external gear system that meshes with a sun gear on one side and with a ring gear (not shown) on the other.

[0030] Thrust plates 9 are positioned between the planetary gear 8, the rolling bearing 5, and each carrier web 3. By contacting these thrust plates 9, the planetary gear 8 can extend integrally with its axial end face, and similarly, the cage 6 can extend integrally with its annular rim, thereby supporting the planetary gear 8 axially. Each of the thrust plates 9 is axially supported on one side of the carrier web 3. Each thrust plate 9 has a first contact surface 10 into which the planetary gear 8 extends. Furthermore, each thrust plate 9 has a second contact surface 11, which is positioned further inward in the radial direction, and by contacting the second contact surface 11, the cage 6 extends integrally with the axial end face of its annular rim.

[0031] To supply lubricant to the bearing area, the two carrier webs 3 have corresponding contours, as shown in Figures 2 and 3. Figure 2 shows a perspective view of the carrier web 3 shown on the right side of Figure 1, and Figure 3 shows the carrier web 3 shown on the left side of Figure 1.

[0032] As shown in Figure 2, the carrier web 3 is preferably provided with an embossed channel-shaped recess 12, which is introduced into the surface of the carrier web 3 and opens radially inward on one side and into a corresponding through hole 13 in which a bearing pin 4 is received on the other side. This elongated channel-shaped recess 12 extends radially, i.e., perpendicular to the rotational axis of the planetary transmission. Because the channel-shaped recess 12 opens radially inward, lubricant can be supplied radially inward, i.e., from the sun gear side, as indicated by arrow P1. This lubricant enters radially into the recess 12 and can reach the area of ​​the bearing pin 4 on one side, but can also reach axially inward into the actual rolling area on the other side. For this purpose, the adjacent thrust plate 9 preferably has a corresponding notch on its inner circumference, which opens the thrust plate 9 axially so that lubricant flowing in through the recess 12 can enter the bearing area axially.

[0033] A corresponding channel-shaped recess 14 is also provided on the opposite side of the second carrier web 3, but the channel-shaped recess 14 is positioned 180° offset from the first recess 12 with respect to the longitudinal axis of the bearing pin. The channel-shaped recess 14 is also elongated and on one side opens into the through hole 15 into which the bearing pin 4 is received, and radially opens onto the outer side of the carrier web 3. This allows fluid flowing in from inside the bearing to be discharged again radially, as indicated by arrow P2.

[0034] This makes it possible to supply lubricant from the radial interior, i.e., from the sun gear side. The sun gear unit is shown here in its basic form. A radial supply passage is provided through which lubricant is supplied from the radial interior to the region of the planetary gear pair. The local supply section may be positioned to originate mainly from the right side of the gear as shown in Figure 1, thereby the lubricant mainly enters there according to arrow P1. The lubricant is always driven by centrifugal force and passes radially outward through the radial guide channel formed by the recess 12, then deflected axially and flows axially into the rolling region through the notch on the thrust plate 9 already described. There the lubricant flows further, thereby wetting all the regions to be lubricated, and then, driven again by centrifugal force, reaches the outlet region due to its axial flow component, where it enters the outlet channel formed by the recess 14, and the lubricant is then again driven by centrifugal force and discharged radially outward. In this way, as clearly shown in Figure 1, defined lubricant supply at the designated inlet side into which the primary lubricant volume flows, and defined lubricant discharge at the discharge side can be achieved.

[0035] Figures 4–6 show exemplary embodiments of a thrust plate 400 that can be integrated as a thrust plate 9 in the planetary transmission 1 of Figure 1. The thrust plate 400 is annular and has a special contour. It has a first recess 402 introduced from one plate side 401 into the outer plate section, which, as a recess, connects to a corresponding protrusion 403 on the opposite plate side 404. In the illustrated embodiment, four such recesses 402 or protrusions 403 are provided, which are distributed at equal intervals around the thrust plate 400. As shown in the figure, the recesses 402 are open toward the outer circumference but closed toward the circumferential direction, specifically toward the inner circumference. In the illustrated embodiment, they extend slightly beyond half the width of the annular plate body.

[0036] Furthermore, a second recess 405 is provided, which is formed on the inner plate section and connects to a corresponding raised portion 406 on the opposite plate side portion 404. These second recesses 405 open inward and close circumferentially and outward, and extend only over about one-third of the width of the plate body, as shown in Figure 4. Here again, four recesses 405 distributed equidistantly around the circumference and, of course, corresponding raised portions 406 are provided.

[0037] The raised portions 403 and 406 are flat raised portions, i.e., have flat side surfaces. In the assembled position, these flat raised portions 403 and 406 each abut against the carrier web 3. Opposite surfaces of the plate body form a first segmented contact surface 407, and the end face of the planetary gear 8 extends in contact with it in the assembled position. In contrast, the surface of the plate body opposite the second flat raised portion 406 forms a second contact surface 408, which is further positioned radially inward, and the cage 6 extends in contact with it. This second contact surface 408 is also segmented. The segmentation of the two contact surfaces 407 and 408 provides only a smaller contact area between the thrust plate 400 and the planetary gear 8 or cage 6, so that friction can be reduced. In the illustrated embodiment, the two contact surfaces 407 and 408 are positioned in a common axial plane, meaning that the corresponding protrusions 403 and 406 project axially by the same distance from the undeformed plate body. This means that the cage 6 of the rolling bearing 7 cannot project axially beyond the planetary gear 8 and can therefore have a maximum axial length equal to the maximum axial length of the planetary gear 8. However, it is also conceivable to position the first contact surface 407 and the second contact surface 408 axially offset from each other, i.e., the second contact surface 408 is formed axially offset from the first contact surface 407. The second contact surface 408 then projects less from the undeformed plate body. This makes it possible to use a cage 6 that projects axially beyond the planetary gear 8, and in connection with this, it may be possible to use somewhat longer rolling elements in the form of needles.

[0038] As shown in Figure 4, the depressions 402, 405 and the resulting protrusions 403, 406 are offset from each other in the circumferential direction and positioned in a staggered manner. This results in a channel structure 409 that is radially open both outward and inward, i.e., a corresponding channel is formed between the protrusions / depressions in the assembly position, through which lubricant can flow from the radially outside to the radially inside. In the assembly position, the plate side 404 faces the planetary gear 8, meaning that the recessed plate region overlaps with the planetary gear. Similarly, the cage extends across the recessed plate region. This results in a corresponding guide channel that is radially outward and radially inward, thereby enabling radial flow through this lubricant guide structure or channel structure 409 provided on both plate sides. At the same time, the channel-shaped depressions 12, 14 communicate with the lubricant guide structure or channel structure 409. Through this flow, the lubricant is, on the one hand, delivered into the areas of the first contact surface 407 and the second contact surface 408, and lubricated thereafter, and on the other hand, the lubricant also flows into the rolling bearing area, supplying it. The overlap results in a corresponding branched channel structure 409, the geometric shape and size of the channel structure 409 can, of course, be influenced and adjusted by the corresponding positioning or spacing of the individual recesses / ridges and their particular size, so that the lubricant inflow can ultimately be controlled.

[0039] As described above, the thrust plate 400 is positioned such that its plate side portion 404, and therefore its recesses 402 and 405, are adjacent to the planetary gear 8 and cage 6. As a result, the plate side portion 401 is adjacent to the web 3 of the planetary carrier 2 and abuts against the web 3 when in contact. This causes the planetary gear 8 to axially cover the recesses 402 and 405, thereby forming corresponding closed pockets, which serve as lubricant reservoirs. The radially outward-opening pocket formed by recess 402 is filled with lubricant flowing in from the sun gear side, specifically providing a lubricant reservoir for frictional contact between the thrust plate 400 and the planetary gear 8 and cage 6. The pocket formed by the recess 405 is filled by a lubricant flow between the thrust plate 400 and the planetary gear 8, that is, either leaving a minimal lubrication gap, or filling substantially from the inside out, i.e., from the side of the bearing pin 4 on which the thrust plate 400 sits. This creates a lubricant reservoir near the pin. A larger volume receptacle is also formed on the side facing the carrier web 3 via the structure 409, where it lubricates the friction area.

[0040] Figure 7 shows a cage 50 according to the present invention for a rolling bearing, which can be integrated as a rolling bearing 5 within a planetary transmission according to Figure 1. The cage 50 is made of a metal sheet or plastic and has two end annular rims 51, between which a number of ribs 52 extend, the ribs 52 being directly connected to the annular rims 51 at their ends. Specifically, the ribs 52 are W-shaped, as shown in Figure 9, i.e., the ribs 52 have a rib center portion 53 that rises radially outward, and rib ends 54 that are bent radially inward are connected to the rib center portion 53 on both sides. The annular rims 51 are connected to these rib ends 54. A pocket 55 is formed between each of the two ribs 52, in which cylindrical needle-shaped rolling elements 56 are received and guided (see Figure 10 showing a rolling bearing 57 according to the present invention).

[0041] In the cage 50 according to the present invention, the two annular rims 51 are funnel-shaped, that is, specifically, their diameter widens towards their free ends, as clearly shown in Figure 9. The diameter widening portion is conical, meaning that the funnel-shaped inner surface 58 and the corresponding outer surface 59 extend straight and at an angle with respect to the longitudinal axis 60 of the cage 50. The angle that the annular rims 51 or the inner surface 58 and outer surface 59 have with respect to the longitudinal axis 60 is, for example, 45°. This should generally be in the range of 15° to 75°, specifically 30° to 60°.

[0042] The outer diameter of the free edge of the annular rim 51 corresponds to the outer diameter of the central rib portion 53 at most, and as a result, the funnel-shaped annular rim 51 does not protrude radially beyond the central rib portion 53.

[0043] The inclined conical outer surface 59 of each annular rim 51 forms a lubricant guide structure 61 through which a lubricant, usually oil, flowing radially from the outside is captured and delivered, as will be discussed below.

[0044] As described above, Figure 10 shows a rolling bearing 57 according to the present invention, which has a cage 50 according to the present invention and needle-shaped rolling elements 56 inserted into its pockets 55. Specifically, this rolling bearing 57 according to the present invention plays the role of supporting the planetary gears of a planetary transmission on bearing pins.

[0045] The rolling bearing 57 has an axial length somewhat longer than the planetary gear; that is, its cage with a funnel-shaped annular rim protrudes slightly beyond the end faces of the planetary gear 8 on both sides when viewed axially. As a result, the end faces of the planetary gear 8 and the edges of the funnel-shaped annular rim are positioned on an axially offset plane. This results in a thrust plate having two contact surfaces on the offset plane, which may be formed by recesses of different depths, in the case of the thrust plate 400 in Figures 4-6.

[0046] In the assembled position, the funnel-shaped annular rim 51 has an outer surface 59 that is freely accessible radially via a lubricant guide or channel structure 409. Therefore, the lubricant flowing into the inlet side according to arrow P1 directly impacts the outer surface 59, where it is received and deflected axially into the rolling region. Accordingly, the fluid flow on the outlet side is reversed. Thus, the cage 50, which is longer in the axial direction, is used to directly receive and deliver the lubricant.

[0047] Figure 11 shows a further embodiment of the cage 100 as part of a rolling bearing 101 that may be used in the planetary transmission 1 according to Figure 1. The cage 100 is preferably made of plastic, and optionally of metal, and has two axial end annular rims 102 and a number of ribs 103 extending between them and connecting them, see also the cross-sectional view in Figure 12 for this. In a circumferential view, a pocket is formed in either case between two adjacent ribs 103, and a cylindrical rolling element 104 is inserted into each pocket, as shown in the figure. The rolling element 104 is a cylindrical needle. The annular rims 102 extend radially or have a corresponding radial width, and therefore they each have a larger annular plate-like axial end face.

[0048] In the cage 100 according to the present invention, the axial annular plate-shaped end faces 105 of the two annular rims 102 are contoured via alternating ridges 106 and depressions 107, the ridges 106 and depressions 107 arranged in a symmetrical order. Each ridge 106 has a flat end face. The ridges 106 and depressions 107 ultimately form a segmented support surface into which the cage 100 extends in contact with axially adjacent thrust plates.

[0049] The recesses 107 are configured in a channel-like manner and extend from the outer to the inner circumference of the annular rim 102 to create a lubricant guide structure or channel structure that opens radially outward and inward. The width of each recess 107 remains constant along its radial length when viewed circumferentially, which means that the flow cross-section does not change. This is useful in allowing as much lubricant as possible to be directed into the bearing area through the lubricant guide structure.

[0050] As shown in Figures 11 and 12, the raised portion 106 and the depression 107 are fused together almost continuously so that a wave-shaped contour is formed.

[0051] Specifically, as shown in Figure 11, groove-like depressions 108 extending along the entire length of the rib are provided on the outer side of each rib 103. These groove-like depressions 108 form lubricant grooves in which lubricant accumulates, allowing the lubricant to flow axially along the cage 100 or the rolling bearing 101. On the other hand, the groove-like depressions 108 also form lubricant pockets or lubricant reservoirs through which the externally guided cage 100 is lubricated within the planetary gear bore housing the rolling bearing 101.

[0052] Each rib has an outer rib section 109, through which it is flush with the annular rim 102. These rib sections 109 are somewhat wider in the circumferential direction and form a snap section 110 through which the rolling elements 104 are held in pockets. The recessed sections 108 within the rib sections 109 are found to be wider and deeper than those within the central rib section 125, which is recessed relative to the rib sections 109. The recessed sections provided in the rib sections 109 form correspondingly larger lubricant pockets, which allow for the corresponding volume to be received.

[0053] In the planetary transmission 1, a thrust plate 9 is positioned between the planetary gear 8, the rolling bearing 101, and each web 3. By contacting the thrust plate, the planetary gear 8 can extend integrally with its axial end face, and similarly, the cage 100 can extend integrally with its annular rim 102, thereby supporting the planetary gear 8 axially. Neither the rolling bearing 101 nor the cage 100 extends axially beyond the planetary gear 115, i.e., they do not protrude axially, meaning that the annular rim 102 is as flush as possible with the end face of the planetary gear 115. However, in principle, with a correspondingly different design of the thrust plate 9, it is conceivable that the cage 100 may protrude slightly beyond the planetary gear axially.

[0054] Each of the thrust plates 9 in Figure 1 has a first contact surface formed by the plate body. For example, the plate body of the thrust plate 9 in the form of thrust plate 400 further forms a second contact surface radially inward, the second contact surface being, for example, on the same plane as the first contact surface and, like the first contact surface, may be segmented, but may also exist as an undeformed annular plate. The cage 100 extends in contact with the thrust plate 9, either integrally with its annular rim 102 or integrally with the corrugated contour formed thereon. The radial width of each annular rim 102 may be slightly larger than the radial width of the second contact surface, so that the corrugated contour of the radial rim 102, i.e., specifically the radially open recess 107, overlaps with the recess provided on this plate side. As a result, the lubricant guide structure formed by the structuring of the thrust plate 9 and defined by the recess formed on the side of the planetary gear communicates with the lubricant guide structure formed on the annular rim 102, specifically the recess 107 thereon.

[0055] The lubricant is captured on one side of the planetary gear and supplied to a lubricant guide structure formed between the planetary gear 8 or carrier web 3 and the thrust plate 9, particularly through the recess 12. See arrow P1 in Figure 1. The lubricant flows radially outward through these, reaching the region of the recess 107 on the cage 100, where the lubricant is first received and distributed to the thrust plate 9 in the friction region, but then also supplied radially and delivered to the rolling region. At the same time, the lubricant also flows into the groove-like recess 108. Overall, a sufficiently large amount of lubricant is guided radially from the outside to the radially inward into the actual rolling region, where it is distributed axially as indicated by arrow P1.

[0056] The lubricant is guided to some extent axially through the rolling bearing 101. On this bearing side, shown on the left side of Figure 1, the lubricant is released outwards again, on the one hand by flowing out of the groove-shaped recess 108, and on the other hand by being driven by centrifugal force to flow radially outward through the recess 107 on the annular rim 102 and the recess on the thrust plate 9 there, where it is shaken off. This flow path is indicated by arrow P2.

[0057] As described above, the cage 100 can also protrude axially beyond the planetary gear 8 on both sides. In this case, the thrust plate 9 must be contoured somewhat differently, as already described above for the embodiments of the cage shown in Figures 7 to 9. This is because an axial offset must exist between the first contact surface 10 and the second contact surface 11.

[0058] Figure 13 shows a further embodiment of a cage 150, which is part of a rolling bearing 151 according to the present invention, and which can be used as a rolling bearing 5 in a planetary transmission 1 according to Figure 1. The cage 150 is preferably made of plastic, but may be made of metal. The cage 150 has a first axial end annular rim 152 and a second axial end annular rim 153, with a rib 154 extending between them. The annular rims extend radially or have a corresponding radial width, and thus each annular rim has a larger annular plate-like axial end face. Between two adjacent ribs, in either case, one pocket 155 is formed, and a cylindrical needle-like rolling element 156 is inserted into each pocket. The first annular rim 152 is provided with a first lubricant guide structure 157, while the second annular rim 153 is provided with a second lubricant guide structure 158. These components serve to guide or direct the lubricant supplied radially from the outside as intended, which will be discussed below in relation to Figure 3.

[0059] The first lubricant guide structure is formed only on the inner circumference of the annular rim 152 in the form of a first contour on the inner circumference, and the outer circumference is not contoured. This contour is realized by a plurality of first recesses 159 that are offset in the circumferential direction, each recess 159 located on the extension of the pocket 155. All recesses 159 open to both the axial end face 160 of the annular rim 152 and each pocket 155. In the illustrated embodiment, the floor surface 161 of each recess 159 extends parallel to the longitudinal axis of the cage 150.

[0060] Through this first lubricant guide structure 157, i.e., individual recesses 159, the lubricant supplied from the radially outside of the cage can be supplied directly axially to the area of ​​the individual rolling elements 156. The lubricant enters the recesses 159 axially and from there directly into the rolling elements 156, i.e., into the pockets 155. Due to the axial deflection through the recesses 159, the lubricant, which is normally oil, passes through axial flow components so that the lubricant flows axially through the rolling bearing 151, as will be considered below.

[0061] The second lubricant guide structure 158 on the second annular rim 153 is also formed by a contour, but it is located on the outer circumference of the annular rim 153, where the inner circumference is not contoured. This contour is also realized by a plurality of recesses 162 that are distributed circumferentially, and these recesses open axially toward the end face 163 of the second annular rim and axially toward the adjacent pockets 155. This means that they are also directly open toward the rolling elements 156.

[0062] The lubricant flowing axially through the rolling bearing 151 then enters the area of ​​the second recess 162 from the actual rolling element or bearing area, is then guided axially from the rolling element 151 through the second recess 162, and is then discharged therefrom. The floor surface 164 of the recess 162 specifically extends obliquely in a sloping manner, inclined from the end face 163 to the pocket 155, as shown in Figure 14.

[0063] Specifically, as shown in the diagram in Figure 13, each rib is further provided with a groove-like recess 165 extending along the entire length of the rib. Each rib has two first rib sections 166, through which it is adjacent to the annular rims 152, 153 so as to be flush with the outer sides of the annular rims 152, 153. The first rib sections 166 are slightly wider than the central rib section 167, so that corresponding snap projections 168 protrude into the pocket, thereby holding the rolling elements 156, are provided on the first rib sections.

[0064] As shown in Figure 13, the recess 165 section provided in the rib section 166 is wider and deeper than that of the central rib section 167. In this way, lubricant reservoirs of corresponding volumes can be formed in the regions of the annular rims 152 and 153, where a volume of lubricant can be held, thereby lubricating the frictional contact between the external guide cage 150 and the planetary gear bore. In the central rib section 157, the recess is narrower and flatter, and this region is primarily used for axial transport of the lubricant.

[0065] When the rolling bearing 151 is integrated into the planetary transmission 1 in Figure 1, the lubricant is supplied to the planetary gear ring via the sun gear, i.e., from radially inward. The lubricant is captured on one side of the planetary gear and supplied to a lubricant guide structure formed via a recess / ridge, for example, in the form of a thrust plate 400, configured between the planetary gear 8 and the thrust plate 9. See arrow P1 in Figure 1. The lubricant flows radially outward through the recess / ridge, reaches the region of the recess 159 provided on the inner circumference of the cage 150, where it is received, supplied axially, and carried into the region of the rolling elements. At the same time, the lubricant also flows into the groove-like recess 165. Overall, a sufficiently large amount of lubricant is guided radially inward from the radially outside into the actual rolling region, where it is distributed axially as indicated by arrow P1.

[0066] The lubricant is guided to some extent axially through the rolling bearing 151, after passing through axial flow components to the other side of the bearing via the thrust plate 9 and cage 150 to which the lubricant is supplied. On this bearing side, shown on the left side of Figure 1, the lubricant is again discharged outwards, on the one hand by flowing out of a groove-like recess 165, and on the other hand by being driven by centrifugal force to flow radially outward through a recess 162 on the annular rim 153 and a recess on the thrust plate 9 therein, where it is shaken off. This flow path is indicated by arrow P2.

[0067] As described above, the cage 150 does not have the same length as the planetary gear 8 and may protrude axially beyond the planetary gear 8 on both sides. In this case, the thrust plate 9 or 400 needs to be contoured slightly differently, as already described. This is because there needs to be an axial offset between the first contact surface and the second contact surface, which can be achieved by changing the depth of the recess.

[0068] Figures 15–17 show further embodiments of the cage 200 as part of a rolling bearing 201 which can be used as a rolling bearing 5 within the transmission 1 according to Figure 1. The cage 200 is preferably made of plastic, and optionally of metal, and has two axial end annular rims 202 and a number of ribs 203 extending between them and connecting them. See also Figures 16 and 17. In both cases, pockets 204 are formed between two adjacent ribs 203, and cylindrical rolling elements 205 are inserted into each pocket, as shown in the figures. The rolling elements 205 are cylindrical needles.

[0069] In the cage 200 according to the present invention, each annular rim 202 is provided with a spacer 206 on its inner side, i.e., the side to which the rib 203 is connected. The spacer 206 protrudes axially into the pocket 204. Each rolling element 205 is found to have an axial end face 207 that is axially adjacent to and at a short distance from the spacer 206. During operation, the rolling element 205 extends axially in contact with the spacer 206 together with its end face 207, thereby being supported on the spacer 206. The spacer itself can be completely cylindrical, but can also be partially cylindrical as shown in the figures, i.e., the outer side can have a rounded semicircular shape as shown in Figure 16, while the inner side is semi-flat, i.e., only slightly curved along the inner circumference, as shown in Figure 15.

[0070] As can be seen, the radially outward and radially inward openings 208 are formed at the ends of the pocket and extend to both sides of the spacer 206, which is centrally located on the annular rim, and the spacer 206 is then also positioned adjacent to the two adjacent ribs 203. This means that radially open lubricant guide structures can be formed on both cage rims 202.

[0071] Furthermore, each of the annular rims 202 is provided with a radial recess 209 on the outer circumference of the region between the two ribs 203, the radial recess 209 opening axially on both sides and thus opening toward both the axial end face of the annular rim 202 and the pocket 204. Specifically, as shown in the cross-sectional view in Figure 17, the bottom 210 of each recess is inclined downward toward the pocket in a slanted manner, i.e., an inclined surface is formed to further facilitate the inflow and outflow of lubricant.

[0072] Finally, specifically as shown in Figure 16, groove-like recesses 211 extending along the entire length of the ribs are provided on the outer side of each rib 203. These groove-like recesses 211 form lubricant grooves where lubricant accumulates, allowing the lubricant to flow axially along the cage 200 or rolling bearing 201 on one side, thereby reaching from one side of the rolling bearing 201 to the other. On the other hand, the groove-like recesses 211 also form lubricant pockets or lubricant reservoirs through which the cage 200, guided outward, is lubricated within the planetary gear bore housing the rolling bearing 201.

[0073] Each web has an outer rib section 212, which is flush with the annular rim 202. The rib section 212 is somewhat wider in the circumferential direction and forms a snap section 213 through which the rolling elements 205 are held in pockets 204. The recessed section 211 within the rib section 212 is found to be wider and deeper than the central rib section 214 which is recessed relative to the rib section 212. The recessed section provided in the rib section 212 forms a correspondingly larger lubricant pocket, which allows a corresponding volume to be received.

[0074] At the assembly position, the lubricant flows into a radially outward-opening channel-shaped lubricant guide structure between the planetary gear 8 or carrier web 3 and a thrust plate 9, for example, in the form of a thrust plate 400 (see arrow P1 in Figure 1). The lubricant passes from the radially outward to the outer circumference of the adjacent radial rim 202, where it enters a recess 209 having a slightly sloping, inclined floor surface, as described above. The lubricant is redirected through the recess 209 and then flows axially through the rolling bearing 201 (see arrow P1), also entering the corresponding opening 208, thereby supplying lubricant to the entire bearing or rolling region, both on the planetary pin 4 and on the inner circumference of the planetary gear 8.

[0075] This deflection causes the lubricant to flow axially through the rolling bearing 201, as indicated by arrow P2, via the axial flow components, and is ejected to the opposite side by centrifugal force. The lubricant then flows axially outward again from the opening 208, into the recess 209, and subsequently into the lubricant guide structure or thrust plate 9 formed therein, which is also driven radially outward through the channels or gaps formed therein. This ultimately means that there is a defined inlet side, and the lubricant is supplied from the sun gear side to only one side, with the majority of the lubricant flowing out again at the opposite outlet side. Of course, the lubricant guide structure on the cage also supplies lubricant to the friction and contact areas of the cage 200 and planetary gear 8 at the contact surface of the thrust plate 9, and this also applies to the area of ​​the thrust plate 9 on the opposite outlet side, so a certain proportion also flows radially out at the inlet side.

[0076] A certain proportion of the lubricant naturally flows into the depressions 211 formed on the outside of the rib 203 and accumulates there. This supplies lubricant to the frictional contact area of ​​the cage 200 with respect to the planetary gear bore, and also allows for a certain axial flow of lubricant through it.

[0077] In this case as well, the cage may be axially flush with the planetary gear, or it may protrude slightly axially beyond the planetary gear, which then results in a slightly different design of the thrust plate, as described.

[0078] Figures 18 to 21 show another embodiment of the cage or rolling bearing for the planetary transmission 1 according to Figure 1. Figure 18 shows the cage 300 as part of a rolling bearing 301. The cage has a first annular rim 302 on one axial side and a second annular rim 303 on the opposite side. A number of ribs 304 extend between the annular rims 302, 303 and connect them, and pockets 305 are formed in each case between two adjacent ribs 304, in which cylindrical, in this case needle-shaped, rolling elements 306 are received.

[0079] At the end of the first annular rim 302, an annular plate-shaped flange section 307 extending radially outward from the annular rim 302 is integrally mounted on a cage 300, which is made of plastic and optionally metal, and may also be called a crankpin cage. The flange section 307 is slightly offset axially from the annular rim 302, as shown in Figures 20 and 21. This means that the flange section 307 protrudes somewhat axially from the annular rim 302. This allows the flange section 307 to be positioned in the assembled position, axially, between the planetary gears and their planetary carriers or carrier webs of the planetary transmission, thereby providing the thrust plate of the planetary gears. This is because the outer diameter of the flange section 307 is larger than the inner diameter of the planetary gear bore, which houses the rolling bearing 301 and thus the cage 300, and therefore an overlap is created between the end face of the planetary gear and the flange section 307, axially. In the assembled position, the flange section 307 is positioned such that the first side 308 faces away from the rolling element 306 adjacent to the planetary carrier or web, so that the cage is supported in contact with and extends in contact with the web, integrally with the plate side 308. The second plate side 309 facing the rolling element 306 forms the contact surface of the planetary gear.

[0080] As shown in Figure 18, and more specifically in Figure 19, the flange section 307 is provided with a lubricant guide structure 310. For this purpose, a plurality of recesses 311 are provided on the first plate side 308, offset equidistant in the circumferential direction, and extending across the entire width of the flange section 307 or plate side 308, i.e., opening radially outward and inward. As clearly shown in Figure 18, the channel-shaped recesses 311 are located on the axial extension of the rib 304.

[0081] On the opposite side of the second plate side 309, a recess 312 is also provided, which is channel-shaped, i.e., elongated and opening radially outward, but radially inward relative to the annular rim 302. These recesses 312 are located within the axial extension of the pocket 305, i.e., within the axial extension of the rolling element 306, as clearly shown in Figure 19.

[0082] As a result, a meandering structure is formed by the flange section 307, as shown not only in the side view in Figure 19 but also in Figure 18, which is formed on both plate sides 308, 309 by recesses introduced therein and the resulting ridges. Since the recesses 311, 312 open radially outward as described, lubricant can be supplied radially from the outside, as will be considered below.

[0083] As already shown in Figure 19, and also as shown in Figure 21, the annular rim 302 is also contoured on its outer circumference. Furthermore, recesses 313 are formed in the axial extension of the pocket 305, and these recesses are inclined downward toward the pocket 305 in a slanted manner (see Figure 21). Each recess 313 opens first into the pocket 305 and second into the adjacent recess 312, ultimately creating an angled channel structure, each formed by one recess 312 and 313. As a result, fluid flowing radially from the outside enters the recess 312, through which it enters the recess 313, from which it enters the pocket 305 axially, where the lubricant is deflected axially, and reaches the rolling element 306.

[0084] The inner circumference of the radial flange 302 also has a contour formed by a recess 314 on the inner circumference opposite the recess 313, as Figure 21 clearly shows in comparison with Figure 20. This forms an opening cross section that allows lubricant to flow into the pocket and rolling element area, including lubricant flowing in radially from the outside through a recess 311 that opens radially outward of the flange section 307. This is because, as shown in Figure 21, an annular space is formed in the inner circumferential region of the flange section 307 and communicates with the inner circumferential recess 314, thereby allowing fluid flowing in from this side to also flow into the rolling element area.

[0085] As further shown in Figure 18, the ribs 304 are also contoured externally. Each rib has a longitudinal groove-like recess 315 on its outer side, which is used to transport lubricant axially but also forms a lubricant reservoir. Each rib 304 consists of a first rib section 316 that is flush with the respective annular rims 302, 303. Between them is a recessed central rib section 317. The groove-like recess 315 extends throughout all rib sections, but is wider and deeper in the terminal rib sections 316 than in the central rib section 317. Since the cage 300 is guided externally within the planetary gear bore, meaning that frictional contact occurs there, larger sections of the recess 315 form a correspondingly larger volume of lubricant reservoir that lubricates this frictional contact in the best possible way.

[0086] As described, a lubricant guide structure is formed in the flange section 307. In the assembled position, the flange section is positioned between the planetary gear end face and the web, and no additional thrust plates (such as thrust plate 9 shown on the right side of Figure 1) are provided there. As a result, a channel or gap section opening radially outward is formed by a recess 311 in the region between the plate side 308 and the web. As indicated by arrow P1 in Figure 1, lubricant supplied from the radially outward, usually oil, can flow radially through these toward the bearing pins, and from there through the recess 314, and of course through any other free space, into the individual pockets 305 and toward the rolling elements 306.

[0087] Simultaneously, a corresponding channel section or gap section is formed in the region between the planetary gear and the plate side portion 309. Here again, a corresponding channel section or gap section opening radially outward is formed via a recess 312 opening radially outward, and lubricant flows into this channel section or gap section from the radially outward direction according to arrow P1 due to centrifugal force. This lubricant then flows into a communicating recess 313 so as to reach the pocket 305 and the rolling elements 306 directly, and is deflected axially. Arrow P1 first represents radial inflow and second represents axial forward flow. Thus, the lubricant passes through axial flow components so that the lubricant can be distributed to the rolling region in axial flow. Due to centrifugal force, the lubricant exits the rolling bearing again, as shown by arrow P2 in Figure 1. To facilitate discharge on this side, the thrust plate is also provided with a lubricant guide structure formed by a recess introduced on the plate side facing the planetary gear, which connects to a corresponding ridge on the plate side facing the web. These recesses are formed only within the outer plate region, thereby leaving an annular plate-shaped, undeformed body section within the inner circumferential region of the thrust plate. Since the plate body is deformed only locally through the recesses, the corresponding body section remains within the outer circumferential region, through which a first contact surface is formed, into which the planetary gear contacts and extends. In the inner circumferential region, the undeformed annular plate-shaped body section forms a second contact surface into which the annular rim 303 of the cage 300 contacts and extends.

Claims

1. A lubrication device for planetary gear bearings of a planetary transmission (1), wherein the planetary transmission (1) comprises a planetary carrier (2) having two carrier webs (3), at least one bearing pin (4) positioned on the carrier webs (3), a rolling bearing (5) positioned on the bearing pin (4), a planetary gear (8) mounted via the rolling bearing (5), and two thrust plates (9) positioned on both sides of the planetary gear (8) between the planetary gear (8) and the carrier webs (3), wherein at least one channel-shaped recess (12, 14) is introduced on at least one carrier web (3) on the surface facing the planetary gear (8), and a lubricant supplied from radially outside the thrust plate is supplied to the bearing area in the region between the thrust plate and the carrier webs (3) via the recess. It is possible that the lubricant flowing out from the bearing region can be discharged radially to the outside within the region between the thrust plate and the carrier web (3), wherein only one channel-shaped recess (12, 14) is provided on the two carrier webs (3), and the recesses (12, 14) on one carrier web (3) and the other carrier web (3) are offset about the axis of the bearing pin (4), with one recess (12) being positioned further inward radially with respect to the rotation axis of the planetary transmission (1) than the other recess (14), thereby the lubricant flows into the rolling bearing (5) through the further inward recess (12), flows axially through the rolling bearing (5), flows into the further outward recess (14), and is discharged therefrom. At a minimum, there is a lubricant gap between the carrier web (3) having the recesses (12, 14) and the thrust plate (9) that is radially outward, and the lubricant can be supplied or released through the lubricant gap. A lubrication device characterized in that the thrust plate (9, 400) has a plate body, and a plurality of pocket-shaped first recesses (402) are provided on the first plate side portion (401) of the plate body, which are open toward the outer circumference and closed toward the inner circumference, and the surface sections of the plate body disposed between the first recesses form segmented first contact surfaces (407).

2. The lubrication device according to claim 1, characterized in that the two recesses (12, 14) are elongated and their longitudinal axes extend perpendicularly to the rotation axis of the planetary transmission (1).

3. The lubrication device according to claim 1 or 2, characterized in that each carrier web (3) has through holes (13, 15) into which the bearing pin (4) is inserted, and both recesses (12, 14) are open in the through holes (13, 15).

4. The lubrication device according to claim 1, wherein a plurality of pocket-shaped second recesses (405) are provided on the first plate side (401) of the plate body, opening toward the inner circumference and closing toward the outer circumference, and flat first and second protrusions (403) and (406) corresponding to the first and second recesses (405) are provided on the opposite second plate side (404), and the surface section of the plate body disposed between the second recesses of the plate body forms a segmented second contact surface (408), and the first and second protrusions (403) and (406) are spaced apart from each other to create a channel structure (409) opening from the outer circumference toward the inner circumference.

5. The lubrication device according to claim 4, characterized in that the first recess (402) is arranged in a staggered pattern with respect to the second recess (405) and overlaps with each other when viewed in the circumferential direction.

6. The lubrication device according to claim 1, characterized in that a lubricant guide structure (61, 157, 158, 310) for guiding the lubricant to flow in or out is provided on at least one axial side of the cage (50, 100, 150, 200, 300) of the rolling bearing (5, 57, 101, 151, 201, 301).

7. The lubrication device according to claim 6, characterized in that the lubricant guide structure (61, 157, 158, 310) is provided by a profile formed on the axial end face of the annular rim (102, 302) of the cage (100, 300), and / or by a profile formed on the inner circumference and / or outer circumference of the annular rim (202), and / or by a groove extending along the rib (203), and / or by a cage edge whose diameter widens conically toward the free end.

8. A planetary transmission comprising: a planetary carrier (2) having two carrier webs (3); at least one bearing pin (4) disposed on the carrier web; a rolling bearing (5) disposed on the bearing pin (4); a planetary gear (8) mounted via the rolling bearing; and two thrust plates (9) disposed on both sides of the planetary gear (8) between the planetary gear (8) and the planetary carrier (2), each having a contact surface for the planetary gear (8) and the rolling bearing (5), and comprising the lubrication device according to claim 1.

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