Planetary gear for a planetary gear and a planet carrier for such a planetary gear

Abstract

The invention relates to a planet wheel (10) for a planetary gear (14), having a planet wheel bore (28) which extends coaxially or parallel to a planet wheel axis of rotation (APR), which planet wheel bore at least partially passes through a planet wheel shaft (22). Furthermore, the invention also relates to a planet carrier (44) for such a planet wheel (10), comprising a carrier body (46) having a first disc-shaped body (48) and a second disc-shaped body (50), the first disc-shaped body having at least one first bearing recess (60) with at least one first locking protrusion (64) extending in the circumferential direction, the second disc-shaped body having at least one second bearing recess (62) with at least one second locking protrusion (66) extending in the circumferential direction.

Description

Technical Field

[0001] The present invention relates to a planetary gear for a planetary gear and a planet carrier for such a planetary gear. Background Technology

[0002] Planetary gears are particularly useful when high gear ratios or reduction ratios must be provided within a small space. For example, modern vehicles have numerous auxiliary drive systems, such as parking brake actuators, trunk lid actuators, sunroof actuators, or seat longitudinal adjustment devices. These almost exclusively use electric motors as torque sources, but these motors operate at relatively high speeds and low torque. In these cases, planetary gears provide the necessary gear ratios or reduction ratios within a small space. Furthermore, planetary gears are especially popular because they allow for mass production at low cost and because of their low noise levels; in this case, the planetary gears are made of plastic. Injection molding is used for production in this situation, where the boundary conditions that must be observed during injection molding cause the design of the planetary carrier, in particular, to deviate more or less from conventional designs. Planetary carriers and planetary gears made of plastic are known, for example, in EP 3 722 641 A1, DE 102005 023 542 A1, DE10 2015 119 803 A1, EP 3 527 846 A1, EP3 486 523 A1 and WO 2014 / 095966 A1.

[0003] Because these planetary gears are suitable for mass production, their quick and safe installation is an important additional aspect. Furthermore, planetary gears sometimes bear very high loads in the aforementioned applications, so the fatigue strength of the planetary gears, in particular, is another important aspect, which sometimes conflicts with injection-molding compatible production. Summary of the Invention

[0004] The purpose of embodiments of the present invention is to provide a planetary gear that can meet the above requirements and can be manufactured in a simple and low-cost manner for planetary gears and planet carriers. The planetary gear and planet carrier are designed so that the planetary gears are easy to manufacture and assemble, and have high fatigue strength or high maximum transferable misuse torque.

[0005] The stated objective is achieved by means of one aspect of the invention. Advantageous embodiments are those according to another aspect of the invention.

[0006] Embodiments of the present invention relate to a planetary gear for a planetary gear system, comprising:

[0007] - A wheel body having a first planetary gear end face and a second planetary gear end face.

[0008] - Planetary gear axle, the planetary gear axle:

[0009] The planetary gear defines the axis of rotation of the planetary gear and includes a first bearing portion and a second bearing portion, wherein the first bearing portion protrudes beyond the end face of the first planetary gear, and the second bearing portion protrudes beyond the end face of the second planetary gear.

[0010] - At least one planetary gear bore that extends coaxially or parallel to the planetary gear shaft passes through the planetary gear shaft at least partially.

[0011] The proposed planetary gear includes a first bearing portion and a second bearing portion, both arranged outside the gear body. The planetary gear can be inserted into a first or second bearing recess of the planet carrier via the first and second bearing portions. Since the planetary gear has a planetary gear bore extending coaxially with its axis of rotation, a pin of an assembly tool can be inserted into the planetary gear bore, and the planetary gear can be inserted into the first or second bearing recess of the planet carrier using the assembly tool. As mentioned at the beginning, the proposed planetary gear and planet carrier are suitable for being made of plastic. However, a situation arises where the function-related surfaces, particularly the surfaces of the first and second bearing portions and the teeth of the gears, are relatively sensitive to external influences, thus damage to these surfaces cannot always be reliably prevented, especially during assembly. On the other hand, the surfaces of the planetary gear bores are not functionally related. If they are damaged, for example, when a pin of the assembly tool is inserted into the planetary gear bore, this will not adversely affect the function of the planetary gear and thus the planetary gear. In this respect, compared with known manufacturing processes, planetary gears with the proposed planetary gears can be manufactured with a more stable manufacturing process and therefore have a smaller defect rate.

[0012] According to another embodiment, the planetary gear may have exactly one planetary gear bore that passes through the entire planetary gear. The planetary gear bore does not necessarily need to pass through the entire planetary gear in order to insert the pin of the aforementioned assembly tool. However, manufacturing a planetary gear bore that passes through the entire planetary gear, especially due to the boundary conditions of the injection molding process, is generally easier than a planetary gear bore that only partially protrudes into the planetary gear. Furthermore, the increased elasticity of the entire planetary gear, particularly the elasticity of the first and second bearing portions, is especially advantageous from an assembly technology perspective when the first and second bearing recesses of the planetary carrier have inherently elastic first and second locking protrusions. This will be discussed in more detail later.

[0013] In further embodiments, it may be specified that,

[0014] – The first bearing portion has a first extension starting from the end face of the first planetary gear and

[0015] – The second bearing portion has a second extension starting from the end face of the second planetary gear, wherein

[0016] - The first extension is not equal to the second extension.

[0017] As described above, the first bearing portion and the second bearing portion are inserted into the corresponding first bearing recess or second bearing recess of the planetary carrier. Particularly due to the specifications produced by the injection molding process, it may be necessary to design different lengths for the first bearing recess and the second bearing recess relative to the axis of rotation of the planetary carrier, especially when a separate insert is to be connected to the planetary carrier. In the case of different first extensions of the first bearing portion and second extensions of the second bearing portion, different extensions can be considered, thereby providing a maximized contact surface, resulting in correspondingly lower surface pressure. First bearing recesses and second bearing recesses with different mating arrangements can be provided to interact with the first bearing portion or the second bearing portion to accommodate different contact surfaces.

[0018] Since proper alignment of the planetary gears must be ensured during assembly in this case, it is recommended to mark one of the bearing sections in an identifiable manner, such as with grooves.

[0019] It should be noted that, depending on the design of the planet carrier and the expected load during operation, the first extension can also be chosen to be equal to the second extension. From a manufacturing perspective, this has the advantage that the planetary gears do not need to be inserted into the planet carrier in a fixed alignment.

[0020] In a further embodiment, the planetary gear axle can be formed from the gear body. In principle, for example, a planetary gear axle made of steel can be provided, with the planetary gears mounted on it. For example, the above-described case exists in WO 2014 / 095966 A1. However, in this embodiment, the planetary gear axle is an integrated component of the gear body, thus the gear body is designed as a single piece. This eliminates additional assembly steps. Furthermore, the number of components is reduced, thereby simplifying warehousing and maintaining low cost.

[0021] In another embodiment, the gear body may include a gear ring with a first number of teeth and a second number of ribs, wherein the ribs extend between the planetary gear shaft and the gear ring, and planetary gear projections are arranged on the ribs, protruding beyond the gear ring along the planetary gear axis of rotation. The first number of teeth may be equal to the second number of ribs, but this is not mandatory. Furthermore, the advantage of using ribs is that they can be positioned at the points of highest load on the planetary gear. This saves material without having to accept significant disadvantages in the strength of the planetary gear. The advantage of providing planetary gear projections is that they form wear surfaces without causing the location of wear to have a significant negative impact on the function of the planetary gear and thus the planetary gear. The arrangement of the planetary gear projections on the ribs allows them to be positioned at a relatively small distance from the axis of rotation of the planetary gear. Therefore, the circumferential speed of the planetary gear projections is reduced, keeping their stress correspondingly low. Providing planetary gear projections on the ribs is particularly suitable for spur gear meshing, where the axial force acting is smaller than that in helical gear meshing.

[0022] Another embodiment specifies that the wheel body may include a gear ring having a first number of teeth and a second number of ribs, wherein the wheel body has at least one continuous planetary gear protrusion disposed between the ribs and the gear ring. Again, the first number may be equal to the second number or different from each other. Because the planetary gear protrusions are continuous, they are designed to be uninterrupted and to make continuous contact with the corresponding mating surfaces. This allows for the compensation of misalignment of the planetary gear rotation axis relative to the planet carrier without significantly increasing the noise level. The arrangement of continuous planetary gear protrusions is particularly suitable for helical gear meshing where high axial forces occur.

[0023] According to another embodiment, the rib has a concave arched structure having: a radius located in a plane extending through the axis of rotation of the planetary gear, a first end, and a second end, wherein the arched structure transitions into the first bearing portion or the second bearing portion in the region of the first end, and transitions into the planetary gear protrusion in the region of the second end.

[0024] The arched structure ensures a uniform stress profile, thus avoiding stress peaks. The radius of the arch can be constant or variable. Variations in the radius can be chosen to produce a particularly uniform stress profile. For example, the radius can be minimized in the region where the tangent adjacent to the arch extends perpendicularly to the axis of rotation, and increases towards the radially inward and radially outward ends. This favorable stress profile reduces the formation of stress peaks at locations where planetary gears may fail during operation. Depending on the design of the arch, this can also be approximated by multiple flat surfaces that are inclined relative to each other. The inclination between the planes is gentler in the outer region of the arch and becomes steeper towards the center. However, the above design also applies to such embodiments.

[0025] In another embodiment, it can be proposed that:

[0026] - Between two adjacent teeth, the gear ring has a tooth root, and

[0027] - At least one rib is arranged radially aligned with one of the tooth roots.

[0028] It has been shown that the probability of tooth breakage is highest at the tooth root. Therefore, the radial alignment of the ribs with the tooth root ensures that the tooth root is supported. This significantly reduces the likelihood of gear failure at the tooth root.

[0029] According to another embodiment, the first number can be greater than the second number. As described above, the first number refers to teeth, and the second number refers to ribs. In this embodiment, not every tooth root has aligned ribs. Instead, some tooth roots have no ribs. This results in a larger circumferential distance between two adjacent ribs compared to two adjacent teeth. Therefore, the recess formed between two adjacent ribs is larger compared to embodiments where the first and second numbers are equal. This leads to the advantage of injection molding technology, namely avoiding or at least minimizing narrow radii and material buildup. These can cause overheating during planetary gear production, resulting in lungerbildung. Such lungerbildung can be corrected, but this leads to a longer and more complex manufacturing process. Since material buildup can be avoided in this embodiment, planetary gears can be manufactured faster and more economically.

[0030] In a further embodiment, the first quantity can be an integer multiple larger than the second quantity. This integer multiple is specifically 2. However, integer multiples such as 3 or 4 or larger can also be chosen. The recess formed between two adjacently arranged ribs can be chosen to be correspondingly larger. The integer multiple can be specifically based on the diameter of the planetary gear, where larger integer multiples can be used for smaller diameters.

[0031] In a further embodiment, the rib may:

[0032] - Forming a first rib group with a first rib and a second rib group with a second rib, and

[0033] - The ribs are the first rib on the end face of the first planetary gear and the second rib arranged on the end face of the second planetary gear, wherein

[0034] - The first rib is arranged to rotate relative to the second rib by a rotation angle, the rotation angle being located in a plane extending perpendicularly to the axis of rotation of the planetary gear.

[0035] For example, when the rotation angle is an integer multiple of 2, it can be chosen to correspond to the angle enclosed by the planetary gear shaft in two adjacent arrangement of teeth. Therefore, for example, each odd-numbered tooth root on the first planetary gear end face and each even-numbered tooth root on the second planetary gear end face are supported by a first rib or a second rib. This ensures that each tooth root is supported on the planetary gear end face, achieving uniform support for the tooth roots. This reduces the possibility of tooth breakage at the tooth roots.

[0036] Embodiments of the present invention relate to a planet carrier for a planetary gear according to one of the foregoing embodiments, comprising a support body, said support body:

[0037] - Extending along the axis of rotation of the planet carrier,

[0038] - Including the first disc-shaped main body, and

[0039] - Including the second disc-shaped body, in which

[0040] - The first disc-shaped body and the second disc-shaped body are connected to each other by at least one connector.

[0041] - The first disc-shaped body has at least one first bearing recess.

[0042] The first bearing portion of the planetary gear can be inserted into the at least one first bearing recess, and the at least one first bearing recess has at least one circumferentially extending first locking protrusion; and the second disc-shaped body has at least one second bearing recess.

[0043] The second bearing portion of the planetary gear can be inserted into the at least one second bearing recess, and the at least one second bearing recess has at least one second locking protrusion extending circumferentially. As mentioned at the beginning, the planetary gear may be provided with planetary gear bores, thereby giving the planetary gear increased elasticity, particularly in the first and second bearing portions. Also as described above, the planetary gear, its first bearing portion, and its second bearing portion are inserted into the first or second bearing recess of the planet carrier during the assembly of the planetary gear. The first and second locking protrusions are briefly elastically compressed and then return to their initial state. However, not only the first and second locking protrusions elastically deform, but also the first and second bearing portions elastically deform. The deformation is thus distributed to the first and second locking protrusions and the first and second bearing portions. This reduces the possibility of irreversible elastic deformation, particularly of the locking protrusions, or prevents elastic deformation.

[0044] Because of these processes that occur during assembly, latches, snaps, or clips are provided, which are characterized by particularly simple and quick assembly.

[0045] Viewed radially outward, the first and second locking protrusions surround the first or second bearing portion, thereby providing a radially outward undercut. The planetary gears inserted into the bearing recesses are thus pre-secured and cannot be released from the planet carrier, even before the planet carrier and planetary gears are inserted into the hollow gears. Furthermore, this pre-secured design allows for more stable planetary gear operation. The first and second bearing recesses include generally circular sector-shaped portions that guide and center the planetary gears during insertion. Therefore, the surface of the circular sector-shaped portions surrounds the recess angle. To minimize contact-induced friction and the resulting wear, planetary gears are typically lubricated with oil or grease. The locking protrusions create a suction effect during operation, drawing oil into the bearing recesses. By selecting the recess angle, the suction effect can be increased or decreased.

[0046] Therefore, the wear characteristics of the planetary gears in the sun gear and hollow gear are improved, which reduces the wear of the planetary gears. Furthermore, the noise level is kept low.

[0047] In another embodiment, it may be specified that,

[0048] - At least one first axially reverse protruding surface (axiale Gegenanlauffläche) surrounding the first bearing recess is provided on the first disc-shaped body and / or

[0049] - At least one second axially reverse protruding surface is provided on the second disc-shaped body surrounding the second bearing recess, wherein

[0050] - When the planetary gear is inserted into the first bearing recess and the second bearing recess, the first axially reversed protruding surface and / or the second axially reversed protruding surface interact with the protruding surface of the planetary gear, wherein...

[0051] – The first reverse protruding surface is connected to the first bearing recess via a first inclined surface, the first inclined surface being inclined at a first inclined angle relative to the first reverse protruding surface, and / or

[0052] - The second reverse protruding surface is connected to the second bearing recess via a second inclined surface, the second inclined surface being inclined at a second inclined angle relative to the second reverse protruding surface.

[0053] As described above, the planetary gear has planetary gear protrusions. During operation, these protrusions contact a first or second axially reversed protruding surface of the planet carrier, thereby transmitting the axial force acting on the planetary gear to the planet carrier and absorbing it. To minimize contact-induced friction and the resulting wear, as previously mentioned, the planetary gear is typically lubricated with oil or grease. A first and / or second ramp creates a suction effect, which, combined with the rotational motion of the planetary gear relative to the planet carrier, draws oil or grease between the planetary gear protrusions and the first or second axially reversed protruding surface. This ensures a sufficient amount of oil or grease is present to maintain low levels of the aforementioned friction and associated wear.

[0054] The suction effect can be stronger or weaker depending on the inclination of the first and / or second ramps.

[0055] According to a further embodiment, the first axially reverse protruding surface transitions into the first inclined surface via a convex first inclined arch structure, and the second axially reverse protruding surface transitions into the second inclined surface via a convex second inclined arch structure. Together with the corresponding inclined surfaces, the inclined arch structure enhances the aforementioned suction effect.

[0056] According to a further embodiment, the support body may:

[0057] - Has at least one radially external connector,

[0058] - Has at least one radially internal connecting body, and

[0059] - It has at least one additional connector disposed between the radially outer connector and the radially inner connector, wherein

[0060] - The radial outer connector, the radial inner connector, and the additional connector connect the first disc-shaped body to the second disc-shaped body.

[0061] All connectors are established between the first and second disc bodies. Referring to the planetary carrier shown in WO 2014 / 0095966A1, it is noteworthy that the first and second disc bodies are connected to each other only by a total of four connectors arranged on the outer periphery of the disc bodies. In contrast, radially inner connectors, radially outer connectors, and additional connectors are more evenly distributed throughout the planetary carrier. This results in a correspondingly uniform force line movement between the first and second disc bodies, which generally leads to increased stability of the carrier body. Since the increased stability also reduces deformation of the planetary gears during operation, the increased stability also leads to reduced wear.

[0062] In another embodiment, an additional connector may be specified to connect to both the radially outer connector and the radially inner connector. In this embodiment, a closed force curve is formed between the radially outer connector and the radially inner connector because the additional connector is connected to both. This also increases the stability of the support body with the aforementioned technical effects.

[0063] In a further embodiment, a radially outer connector and at least one additional connector may be provided to surround a closed recess in the second disc-shaped body. Because the closed recess is formed by the radially outer connector and the at least one additional connector, material can be saved for the second disc-shaped body without significantly negatively impacting its strength.

[0064] According to another embodiment, at least one of the additional connectors transitions to the first axially reversed convex surface via a concave first arch structure. For example, in the planetary carrier shown in WO 2014 / 0095966 A1, the first axially reversed convex surface and the additional connector directly collide and, at least theoretically, form an edge. At least no arch structure is provided to transition the first axially reversed convex surface to the additional connector. Instead, the concave first arch structure results in avoiding or at least reducing stress peaks during the transition from the first reversed convex surface to the additional connector. Therefore, the transition from at least the additional connector to the second axially reversed convex surface can be designed, wherein a concave second arch structure can be provided therein.

[0065] According to a further embodiment, the concave first arch structure has a radius and a first end and a second end, wherein the first arch structure transitions into the first axially reverse-projecting surface in the region of the first end and into the additional connector in the region of the second end, wherein the radius decreases from the first end and the second end. This creates a particularly favorable stress profile between the additional connector and the first disc-shaped body. This favorable stress profile avoids the formation of stress peaks at locations where the support body may fail during operation. Depending on the design of the arch structure, this can also be approximated by multiple flat surfaces that are inclined relative to each other. The inclination between the planes is gentler in the outer region of the arch structure and becomes steeper towards the center. However, the above design also applies to such embodiments.

[0066] Furthermore, at least one of the other connecting bodies can transition to a second axially reverse protruding surface via a concave second arch structure, wherein the radius of the second arch structure changes accordingly with the radius of the first arch structure.

[0067] According to a further embodiment, the first disk-shaped body may form a first free planetary carrier end face, on which a plurality of reinforcing ribs are arranged. In this embodiment, torque is introduced into or removed from the planetary carrier via the first disk-shaped body. Therefore, the first disk-shaped body has a significantly greater load capacity compared to the second disk-shaped body. The load is supported by the reinforcing ribs.

[0068] In another embodiment, the reinforcing rib may be specified as follows:

[0069] -Starting from the first locking protrusion, or

[0070] - Relative to the locking protrusion, radially inward from the first bearing recess, or

[0071] -Starting from the planetary gear rotation axis circle, and

[0072] - Extends radially inward.

[0073] The planetary gear rotation axis circle refers to the circle that extends through the planetary gear rotation axis when the planetary gear is inserted into the planet carrier. The reinforcing rib then extends from the point where the circle exits the first bearing recess and transitions into the first disc-shaped body.

[0074] The reinforcing ribs can be straight or have an arched structure. The force guidance from the planetary gears to the first disc-shaped body of the planet carrier occurs approximately at the origin of the ribs. The load on the first disc-shaped body is correspondingly high at this point. Because the reinforcing ribs originate from the areas of highest load, these areas are supported by the reinforcing ribs, thereby increasing the strength of the first disc-shaped body. The reinforcing ribs extend along the force lines within the first disc-shaped body.

[0075] The first disc-shaped body may have drive teeth radially inward. This can interact with an insert through which torque can be introduced into or removed from the planet carrier. The insert has an additional profile on the outside of the planet carrier, through which it can be attached to a shaft. However, the drive teeth can also interact with the shaft. On the radially inward side, the reinforcing ribs may be tangent to the drive teeth, particularly to the tip circle diameter of the drive teeth. This allows forces to be introduced particularly effectively into the drive teeth and / or the insert, and avoids stress peaks.

[0076] A further embodiment may specify that the first bearing recess has a first extension along the planetary carrier rotation axis, and the second bearing recess has a second extension along the planetary carrier rotation axis, wherein the first extension is larger than the second extension.

[0077] As described above, the insert is used to introduce torque into the support body, particularly into the first disc-shaped body, or to remove torque from the support body, particularly from the first disc-shaped body. To safely transfer torque between the insert and the support body, sufficient wall strength is required for the first disc-shaped body. This is achieved by making the first extension larger than the second extension. It is not necessary to provide additional wall strength for the second disc-shaped body. This would unnecessarily increase the size of the support body and thus increase material consumption.

[0078] According to a further embodiment, a plurality of planetary carrier protrusions may be provided on the first disc-shaped body, these protrusions being arranged adjacent to the first bearing recess. The planetary gears of the present invention are primarily configured for spur gear meshing, wherein helical gear meshing with a defined tilt angle can also be considered. In the case of spur gear meshing, the acting axial force is theoretically 0 or very low, but in practice, for example due to meshing errors within tolerance ranges, the acting axial force is very high and must therefore be taken into account. When the planetary carrier contacts adjacent components, the planetary carrier protrusions form wear surfaces. Wear occurring at the planetary carrier protrusions does not, or at least only to a negligible extent, affect the function of the planetary gears. As mentioned above, the highest force or highest torque is transmitted in the region of the bearing recess, particularly in the region of the locking protrusion between the carrier body and the planetary gears. Also as mentioned above, for this reason, reinforcing ribs extend from the bearing recess, particularly from the region of the locking protrusion. This serves to absorb the force introduced into the carrier body of the planetary carrier through the planetary carrier protrusions. Compared to a planetary carrier protrusion positioned approximately in the middle between two adjacent bearing recesses, the bending torque relative to the bearing recesses remains lower, thereby keeping the overall load on the support body lower.

[0079] According to a further embodiment, the insert can be connected to the first disc-shaped body, and the insert includes a fastener, the insert being connected to the support body via the fastener, wherein the fastener has a radially outward connecting surface, the connecting surface forming at least one radial extension and connecting teeth.

[0080] To reliably transmit the previously mentioned torque between the support body and the insert, the connector of the insert is provided with connecting teeth. These connecting teeth provide a large contact surface between the insert and the support body, thereby maintaining low surface pressure. With the radial extension, the contact surface can be further increased, and the surface pressure can be further reduced. Furthermore, the radial extension locally creates a degree of eccentricity, which has a positive effect on torque transmission. The radial extension allows the insert to have a shape similar to a hypotrochoide. The connecting teeth can have as many small teeth as possible with large cusp radii. This also avoids or keeps stress peaks low. Attached Figure Description

[0081] Exemplary embodiments of the present invention will now be explained in more detail with reference to the accompanying drawings. The drawings show:

[0082] Figure 1 A perspective view of the planetary gear according to the present invention is shown.

[0083] Figure 2 Show Figure 1 The top view of the planetary gear shown.

[0084] Figure 3 Show Figure 1 The front view of the planetary gear shown.

[0085] Figure 4 Show along Figure 3 Cross-sectional view of the defined section CC.

[0086] Figure 5 Showing three such Figures 1 to 4 The diagram shows a front view of the planetary gears according to the planetary carrier of the present invention.

[0087] Figure 6 Show Figure 5 The rear view of the planetary carrier according to the present invention,

[0088] Figure 7 Show Figure 5 The top view of the planetary carrier shown.

[0089] Figure 8 Show Figure 5 The diagram shows a top view of the planet carrier, excluding the planetary gears.

[0090] Figure 9 Show along Figure 8 Cross-sectional view of section AA as defined in the diagram.

[0091] Figure 10 Show along Figure 8 A cross-sectional view of section BB as defined in the diagram.

[0092] Figure 11 Show Figure 5 The diagram shows a perspective view of the planetary frame, in which the second disk-shaped main body is observed.

[0093] Figure 12 Show Figure 11 A magnified view of the portion X defined in the middle.

[0094] Figure 13 Show Figure 5 The diagram shows a perspective view of the planetary support structure, with the first disk-shaped main body visible.

[0095] Figure 14 Show Figure 13 A magnified view of the portion Y defined in the middle.

[0096] Figure 15 Show Figure 14 Enlarged view of the indicated radius,

[0097] Figure 16 A perspective view of the insert is shown, and

[0098] Figure 17 Show Figure 16 The front view of the insert shown. Detailed Implementation

[0099] Figure 1 A perspective view of the planetary wheel 10 according to the present invention is shown. Figure 2 It shows Figure 1 The top view of planetary gear 10 shown. Figure 3 and Figure 4 A front view and a cross-sectional view of the planetary gear 10 are shown. Unless otherwise stated, the following embodiments refer to... Figures 1 to 4 The planetary gear 10 can be inserted Figure 5 The planet carrier 44 is shown in the figure, and there it forms the planet gear 14 together with the hollow wheel 13, which is shown only in principle.

[0100] The planetary gear 10 has a gear body 16, which forms a first planetary gear end face 18 and a second planetary gear end face 20. Furthermore, the planetary gear 10 includes a planetary gear shaft 22, which in the illustrated embodiment is formed by the gear body 16. In this respect, the planetary gear shaft 22 is an integrated part of the planetary gear 10. The planetary gear shaft 22 defines the planetary gear rotation axis APR (…). Figure 4 During the operation of the planetary gear 14, the planetary gear 10 rotates about the axis of rotation. Furthermore, the planetary gear shaft 22 forms a first bearing portion 24 and a second bearing portion 26, which in... Figure 2 As can be particularly seen, the planetary gear 10 can be rotatably mounted in the planet carrier 44 via the first bearing portion 24 and the second bearing portion 26, which will be discussed in more detail later.

[0101] like Figure 2 As shown, the first bearing portion 24 has a first extension x1 along the planetary gear rotation axis APR, and the second bearing portion 26 has a second extension x2 along the same planetary gear rotation axis APR, wherein the first extension x1 is larger than the second extension x2.

[0102] Especially Figure 4 As shown, the planetary gear 10 has a planetary gear bore 28 extending coaxially with the planetary gear rotation axis APR, the planetary gear bore completely passing through the planetary gear 10. The exact function of the planetary gear bore 28 will be discussed in more detail below. It should be noted that the planetary gear bore 28 does not necessarily extend coaxially with the planetary gear rotation axis APR for its function. Furthermore, it does not necessarily have to have a circular cross-section. The ratio of the first extension x1 to the second extension x2 also has no significant impact on the functionality of the planetary gear bore 28.

[0103] The planetary gear 10 forms a gear ring 30 with a first number n1 of teeth 31, wherein in the illustrated embodiment, the first number n1 of teeth 31 is twenty-two (22), particularly from Figure 3 As can be seen from this. Furthermore, the planetary gear 10 is provided with a second number n2 of ribs 32, which extend radially between the gear ring 30 and the planetary gear shaft 22. From... Figure 3 As can be seen from this, the second number n2 of ribs 32 is eleven (11), and therefore smaller than the first number n1. The tooth ring 30 forms tooth roots 34 between two adjacent teeth 31, wherein the ribs 32 are arranged radially aligned with these tooth roots 34, which is particularly evident from Figure 1 and Figure 3 This is derived from...

[0104] As described above, the number of ribs 32 in the second quantity n2 is half the number of teeth 31 in the first quantity n1. Therefore, not every tooth root 34, but only every two tooth roots 34, is provided with radially inwardly aligned ribs 32. Ribs 32 arranged on the end face 18 of the first planetary gear can be assigned to a first rib group 36, wherein the ribs 32 of the first rib group 36 are referred to as first ribs 321. Accordingly, a second rib group 38 can be defined, wherein the ribs 32 are referred to as second ribs 322. Figure 4 As shown, the first rib 321 rotates relative to the second rib 322 by a rotational angle located in a plane perpendicular to the planetary gear shaft 22. This rotational angle corresponds to the angle surrounding two adjacent teeth 31 in the previously defined plane. This allows each tooth root 34 on the first planetary gear end face 18 or the second planetary gear end face 20 to be supported by either the first rib 321 or the second rib 322.

[0105] A planetary gear protrusion 40 is provided on the rib 32, the protrusion protruding above the gear ring 30 along the planetary gear rotation axis APR (see details). Figure 2 ). Figure 4 The planetary gear protrusion 40 is shown to connect radially inward to the concave arch structure 42. Figure 4 In this configuration, the arched structure 42 has a constant radius R, which can also be varied to provide a stress profile that is as uniform as possible and to avoid or at least reduce stress peaks. Therefore, the radius R can be selected such that the stress in the region of the arched structure 42 under the expected load during operation is less than the stress in the gear ring 30.

[0106] Figure 3 Another continuous planetary gear protrusion 41 is also shown by dashed lines, which may be alternately or cumulatively provided on the planetary gear protrusion 40. The continuous planetary gear protrusion 41 is arranged radially outward of the planetary gear protrusion 40 between the rib 32 and the gear ring 30.

[0107] exist Figures 5 to 14 In the diagram, the planet carrier 44 according to the invention is shown in different views. Unless otherwise stated, the following description refers to... Figures 5 to 14 The planetary carrier 44 includes a support body 46 extending along the planetary carrier's rotation axis APT, which in Figure 7 and Figure 8 It is best seen in the middle. The support body 46 includes a first disc-shaped body 48 and a second disc-shaped main body 50, wherein in Figure 5 The first disc-shaped main body 48 can be seen in the middle. Figure 6 The second disc-shaped body 50 can be seen. The first disc-shaped body 48 and the second disc-shaped body 50 are connected to a plurality of radially outer connectors 52, a plurality of radially inner connectors 54, and a plurality of additional connectors 56 arranged therebetween. (See reference) Figure 9 It can be seen that a total of three radially outer connecting bodies 52 with annular structures are provided. Correspondingly, there are three radially inner connecting bodies 54, wherein the circumferential outer end of the radially outer connecting body 52 is the starting point of a corresponding additional connecting body 56, which is joined within the radially inner connecting bodies. When the radially outer connecting body 52 is convexly bent, the two additional connecting bodies 56 are concavely bent. Due to the above embodiment, the radially outer connecting body 52 and the two additional connecting bodies 56 surround the recess 58 of the second disc-shaped body 50, which is particularly useful in... Figure 6 I saw it in the middle.

[0108] exist Figures 5 to 7 In the diagram, planetary carrier 44 is shown as being positioned within three planetary gears 10 (e.g., ...). Figures 1 to 4 (As shown) it is rotatably connected to the planetary carrier 44. For this purpose, the first disc-shaped body 48 has a total of three first bearing recesses 60, and the second disc-shaped body 50 has a total of three second bearing recesses 62. The first bearing recesses 60 are provided with first locking protrusions 64, and the second bearing recesses 62 are provided with second locking protrusions 66. Specifically from... Figure 7 and Figure 8 As can be seen, the first bearing recess 60 has a first extension y1 along the planetary carrier rotation axis APT, and the second bearing recess 62 has a second extension y2, wherein the first extension y1 is larger than the second extension y2. Figure 7 and Figure 8 This can also be seen from the fact that, in Figure 16 and Figure 17 The insert 68 shown in the diagram is connected to the first disc-shaped body 48, wherein the insert 68 is, for example, overmolded. The first extension y1 is selected such that the insert 68 can be integrated into the first disc-shaped body 48 as completely as possible. The insert 68 is used to insert torque into or remove torque from the planet carrier 44.

[0109] The procedure for assembling the planetary gearbox 14 is as follows: A pin of an assembly tool (not shown) is inserted into the planetary gear bore 28, and then the planetary gears 10 are inserted radially inward into the first bearing recess 60 and the second bearing recess 62. During insertion, the first bearing portion 24 and the second bearing portion 26 of the planetary gears 10, as well as the first locking protrusion 64 and the second locking protrusion 66, elastically deform. Once the first bearing portion 24 is fully inserted into the first bearing recess 60 and the second bearing portion 26 is fully inserted into the second bearing recess 62, the elastic deformation is canceled again. The first locking protrusion 64 and the second locking protrusion 66 form a radially outward undercut relative to the first bearing portion 24 and the second bearing portion 26 of the planetary gears 10 and protrude circumferentially into the bearing recesses. As a result, a certain pre-fixation of the planetary gears 10 prevents them from separating from the planet carrier 44 even before they are inserted into the hollow gear 13. Furthermore, the contact area between the bearing portions 24, 26 and the bearing recesses 60, 62 is increased, resulting in a more uniform wear distribution.

[0110] During the operation of planetary gear 14, the undercut formed by the locking protrusions 64 and 66 also causes lubricant to be drawn into the bearing recesses 60 and 62. Especially from Figure 9 As can be seen, the bearing recesses 60 and 62 include circular portions and circular fan-shaped portions, which merge with each other in the locking protrusions 64 and 66. The circular fan-shaped portions surround the corners of the recesses. With the concave angle Changes in the suction can increase or decrease the suction effect.

[0111] As described above, the circular sector portions in the regions of the locking protrusions 64 and 66 merge into a circular portion. In this configuration, the circular sector portions with a transition radius rv transition into the circular portion. The suction effect is also influenced by the transition radius rv.

[0112] Figure 5 The first free planetary carrier end face 70 is shown, on which a plurality of reinforcing ribs 72 are arranged. Figure 5 , Figure 6 and Figure 9 The planetary gear rotation axis circle PDK is indicated by a dashed line. When planetary gear 10 is inserted into planet carrier 44, the planetary gear rotation axis circle PDK passes through the planetary gear rotation axis APR (see in detail). Figure 9If we consider extending the reinforcing ribs 72, then when they are inserted into the planetary carrier 44, they originate from the planetary gear rotation axis APR. In the illustrated embodiment, the reinforcing ribs 72 extend slightly radially inward from the first bearing recess 60 on both sides of the first locking protrusion 64 and extend radially inward into the insert 68, such that they extend approximately tangentially to the teeth of the gear in the insert 68 at their radially inner ends.

[0113] In addition, on the first free planetary carrier end face 70, a total of six planetary carrier protrusions 74 are arranged adjacent to the first locking protrusion 64.

[0114] Especially from Figure 11 , Figure 13 and Figure 14 As can be seen, the first disc-shaped body 48 forms a first axially reversed protruding surface 76, which surrounds the first bearing recess 60. Correspondingly, the second disc-shaped body 50 forms a second axially reversed protruding surface 78, which surrounds the second bearing recess 62. In operation, the planetary gear protrusion 40 interacts with either the first reversed protruding surface 76 or the second reversed protruding surface 78. In this case, a first inclined surface 80 is connected to the first reversed protruding surface 76 relative to the first bearing recess 60, and the first inclined surface is inclined relative to the first reversed protruding surface 76 at a first inclined surface angle α1. The first inclined surface 80 is incorporated into the first axially reversed protruding surface 76 by a convex first inclined surface arch structure 84. Correspondingly, a second inclined surface 82 is connected to the second bearing recess 62, wherein the second inclined surface 82 is inclined relative to the second reversed protruding surface 78 at a second inclined angle α2. The second inclined surface 82 is incorporated into the second axially reversed protruding surface 78 by a second inclined surface arch structure 86.

[0115] The first inclined surface 80 and the second inclined surface 82, together with the rotation of the planetary gear 10, generate a suction effect, which draws in oil or grease to lubricate the planetary gear 14 between the planetary gear protrusion 40 and the first axially reversed protrusion surface 76 or the second axially reversed protrusion surface 78. The suction effect is stronger or weaker depending on the degree of inclination of the first inclined surface 80 and the second inclined surface 82. Furthermore, some misalignment of the planetary gear rotation axis APR relative to the planet carrier rotation axis APR, or deformation caused by the inserted torque, can be compensated for without increasing noise or wear.

[0116] exist Figure 11 In the middle, observe the first axially reverse protruding surface 76 and see the transition from the first axially reverse protruding surface 76 to the other connecting body 56, in which a first arched structure 871 is formed. Figure 14The second axially reversed protruding surface 78 and the additional connecting body 56 are shown. It can be seen that the additional connecting body 56 is incorporated into the second axially reversed protruding surface 78 via a second arched structure 872. The first arched structure 871 and the second arched structure 872 are as follows... Figure 15 As shown. The first arched structure 871 or the second arched structure 872 has a varying radius R. In contrast, Figure 15 A contrasting arch structure 88 with a constant radius R is also shown in dashed lines. The first arch structure 871 and the second arch structure 872 have a first end 90 and a second end 92. The radius R of the first arch structure 871 and the second arch structure 872 decreases towards the middle from the first end 90 and the second end 92, therefore... Figure 15 At the contact point between the first arch structure 871 or the second arch structure 872 and the control arch structure 88, the arch structure has a minimum radius R. This design of the first arch structure 871 or the second arch structure 872 provides a particularly uniform stress profile.

[0117] exist Figure 16 and Figure 17 The previously mentioned insert 68 is shown separately. The insert 68 includes a fastener 94, through which the insert 68 can be connected to the support body 46. The fastener 94 has a radially outward connecting surface 96, which forms connecting teeth 100. Furthermore, the connecting surface 96 forms three radial extensions 98, such that the connecting teeth 100 are partially eccentric. The three radial extensions 98 give the fastener 94 an inward spiral trajectory type shape. The number of eccentric extensions 98 corresponds to the number of planetary gears 10 of the planetary gear 14, wherein the maximum radius of the eccentric extensions 98 is set between two adjacent planetary gears 10. The number and characteristics of the eccentric extensions 98 can be selected to keep the applied stress low. The characteristics of the eccentric extensions 98 should be understood as their size and geometry. As mentioned above, the radial extensions 98 are based on inward spiral trajectories. By appropriately selecting relevant parameters, the radial extensions 98 can be designed so that the shape of the fastener 94 approximates a polygon, here a triangle or a circle. As described above, the insert 68 is surrounded by the first disc-shaped body 48 in the region of the fastener 94. The curve of the reinforcing rib 72 is chosen such that as much force as possible is inserted into the insert 68 approximately tangentially, and particularly into the teeth arranged in the radial extension 98. Thus, torque can be transmitted between the insert 68 and the planetary carrier 44.

[0118] List of reference numerals

[0119] 10 Planetary Wheels

[0120] 13 hollow wheels

[0121] 14 planetary gears

[0122] 16-wheel body

[0123] 18 First planetary gear end face

[0124] 20 Second planetary gear end face

[0125] 22 planetary gear axles

[0126] 24 First Bearing Section

[0127] 26 Second Bearing Section

[0128] 28 planetary gear holes

[0129] 30 gear ring

[0130] 31 teeth

[0131] 32 ribs

[0132] 321 First Rib

[0133] 322 Second Rib

[0134] 34 tooth roots

[0135] 36 First Rib Group

[0136] 38 Second rib group

[0137] 40 planetary gears with protrusions

[0138] 42 arched structures

[0139] 44 planetary frames

[0140] 46-bracket main body

[0141] 48 First disc-shaped main body

[0142] 50 Second disc-shaped main body

[0143] 52 Radial External Connector

[0144] 54 Radial Internal Connector

[0145] 56 Other connectors

[0146] 58 recess

[0147] 60 First bearing recess

[0148] 62 Second bearing recess

[0149] 64 First locking protrusion

[0150] 66 Second locking protrusion

[0151] 68 inserts

[0152] 70 First Free Planetary Carrier End Face

[0153] 72 Reinforcing Ribs

[0154] 74 planetary carrier protrusions

[0155] 76 First axial reverse protruding surface

[0156] 78 Second axial reverse protruding surface

[0157] 80 First inclined plane

[0158] 82 second slope

[0159] 84 First inclined arch structure

[0160] 86 Second inclined arch structure

[0161] 871 First Arch Structure

[0162] 872 Second Arch Structure

[0163] 88 Arched Structure

[0164] 90 First End

[0165] 92 Second End

[0166] 94 solids

[0167] 96 connecting surfaces

[0168] 98 radial extension

[0169] 100 connecting teeth

[0170] APR planetary gear rotation axis

[0171] APT planetary carrier rotation axis

[0172] n1 First quantity

[0173] n2 second quantity

[0174] R radius

[0175] x1 First Extension

[0176] x2 Second Extension

[0177] y1 First Extension

[0178] y2 second extension

[0179] α1 First inclined plane angle

[0180] α2 Second inclined plane angle

[0181] Recess angle.

Claims

1. A planetary gear (10) for a planetary gear, comprising: - Wheel body (16), which has a first planetary gear end face (18) and a second planetary gear end face (20). - Planetary gear shaft (22), the planetary gear shaft: o defines the planetary gear rotation axis (APR) of the planetary gear (10) and o includes the first bearing portion (24) and o includes a second bearing section (26), in which The first bearing portion (24) protrudes beyond the end face (18) of the first planetary gear, and the second bearing portion (26) protrudes beyond the end face (20) of the second planetary gear. -At least one planetary gear bore (28) extending coaxially or parallel to the planetary gear axis of rotation (APR) passes at least partially through the planetary gear shaft (22). The wheel body (16): -Including a gear ring (30) with a first number (n1) of teeth (31), and - Including the second number (n2) of ribs (32), where - The rib (32) extends between the planetary gear shaft (22) and the gear ring (30), and Planetary gear protrusions (40) are arranged on the rib (32), the planetary gear protrusions protruding beyond the gear ring (30) along the planetary gear rotation axis (APR), or The rib (32) extends between the planetary gear shaft (22) and the gear ring (30), and the gear body (16) has at least one continuous planetary gear protrusion (41) arranged between the rib (32) and the gear ring (30).

2. The planetary gear (10) according to claim 1. Its features are, The planetary gear (10) has exactly one planetary gear hole (28) that passes through the entire planetary gear (10).

3. The planetary gear (10) according to claim 1 or 2. Its features are, - The first bearing portion (24) has a first extension (x1) starting from the end face (18) of the first planetary gear and - The second bearing portion (26) has a second extension (x2) starting from the end face (20) of the second planetary gear, wherein - The first extension (x1) is not equal to the second extension (x2).

4. The planetary gear (10) according to any one of the preceding claims. Its features are, The planetary gear axle (22) is formed by the gear body (16).

5. The planetary gear (10) according to claim 1. Its features are, -The rib (32) has a concave arched structure (42): The arched structure has a radius (R) located in a plane extending through the axis of rotation of the planetary gear (APR). The arched structure has a first end (90) and a second end (92), and -The arched structure (42): o transitions to either the first bearing portion (24) or the second bearing portion (26) in the region of the first end (90), and o transitions to the planetary gear protrusion (40) in the region of the second end (92).

6. The planetary gear (10) according to claim 1 or 5. Its features are, -The gear ring (30) has a tooth root (34) between two adjacent teeth (31), and - At least one rib (32) is arranged to be radially aligned with the tooth root (34).

7. The planetary gear (10) according to any one of claims 1, 5 to 6. Its features are, The first quantity (n1) is greater than the second quantity (n2).

8. The planetary gear (10) according to claim 7. Its features are, The first quantity (n1) is an integer multiple of the second quantity (n2).

9. The planetary gear (10) according to any one of claims 1, 5 to 8. Its features are, The rib (32): - Forming a first rib group (36) having a first rib (321) and a second rib group (38) having a second rib (322), wherein - The first rib (321) is arranged on the end face (18) of the first planetary gear, and the second rib (322) is arranged on the end face (20) of the second planetary gear, wherein - The first rib (321) is arranged to rotate relative to the second rib (322) by a rotation angle, the rotation angle being located in a plane extending perpendicularly to the planetary gear rotation axis (APR).

10. A planetary carrier (44) for a planetary gear (10) according to any one of the preceding claims, the planetary carrier comprising a support body (46), the support body being: - Extending along the planetary carrier axis of rotation (APT), -Including the first disc-shaped body (48) and -Including the second disc-shaped body (50), in which - The first disc-shaped body (48) and the second disc-shaped body (50) are connected to each other by at least one connector (52, 54, 56). - The first disc-shaped body (48) has at least one first bearing recess (60). o enables the first bearing portion (24) of the planetary gear (10) to be inserted into the at least one first bearing recess, and The at least one first bearing recess has at least one first locking protrusion (64) extending in the circumferential direction, and - The second disc-shaped body (50) has at least one second bearing recess (62). o enables the second bearing portion (26) of the planetary gear (10) to be inserted into the at least one second bearing recess, and o The at least one second bearing recess has at least one second locking protrusion (66) extending in the circumferential direction. - At least one first axially reverse protruding surface (76) is provided on the first disc-shaped body (48) surrounding the first bearing recess (60) and / or - At least one second axially reverse protruding surface (78) is provided on the second disc-shaped body (50) surrounding the second bearing recess (62), wherein - When the planetary gear (10) is inserted into the first bearing recess (60) and the second bearing recess (62), the first axially reverse protruding surface (76) and / or the second axially reverse protruding surface (78) interact with the planetary gear protrusion (40), wherein - The first axially reverse protruding surface (76) is connected to the first bearing recess (60) via a first inclined surface (80), the first inclined surface being inclined at a first inclined surface angle (α1) relative to the first axially reverse protruding surface (76), and / or - The second axially reverse protruding surface (78) is connected to the second bearing recess (62) via a second inclined surface (82), the second inclined surface being inclined at a second inclined surface angle (α2) relative to the second axially reverse protruding surface (78).

11. The planetary carrier (44) according to claim 10. Its features are, - The first axially reverse protruding surface (76) transitions to the first inclined surface (80) through a convex first inclined arch structure, and / or - The second axial reverse protruding surface (78) transitions to the second inclined surface (82) through a convex second inclined arch structure.

12. The planetary carrier (44) according to claim 10 or 11. Its features are, The main body of the support (46): -Has at least one radial external connector (52). -Having at least one radially internal connecting body (54), and -Has at least one additional connector (56) disposed between the radially outer connector (52) and the radially inner connector (54), wherein - The radial outer connector (52), the radial inner connector (54) and the additional connector (56) connect the first disc body (48) to the second disc body (50).

13. The planetary carrier (44) according to claim 12. Its features are, The additional connector (56) is connected to the radial outer connector (52) and the radial inner connector (54).

14. The planetary carrier (44) according to claim 12 or 13. Its features are, The radially outer connector (52) and the at least one additional connector (56) surround the closed recess (58) of the second disc-shaped body (50).

15. The planetary carrier (44) according to any one of claims 12 to 14. Its features are, - At least one of the additional connectors (56) transitions to the first axially reverse protruding surface (76) via a concave first arch structure (871).

16. The planetary carrier (44) according to claim 15. Its features are, -The concave first arch structure (871) described therein: o has a radius (R), and o has a first end (90) and a second end (92), and - The first arched structure (871) transitions to the first axially reversed protruding surface (76) in the region of the first end (90), and transitions to the additional connector (56) in the region of the second end (92), wherein - The radius (R) decreases from the first end (90) and the second end (92).

17. The planetary carrier (44) according to any one of claims 10 to 16. Its features are, The first disk-shaped body (48) forms the first free planetary carrier end face (70), and multiple reinforcing ribs (72) are arranged on the first free planetary carrier end face.

18. The planetary carrier (44) according to claim 17. Its features are, The reinforcing rib (72): -Starting from the first locking protrusion (64), or -Relative to the first locking protrusion (64), radially inward from the first bearing recess (60), or -Start from the planetary gear rotation axis circle (PDK), and - Extends radially inward.

19. The planetary carrier (44) according to any one of claims 10 to 18. Its features are, - The first bearing recess (60) has a first extension (y1) along the planetary carrier rotation axis (APT) and - The second bearing recess (62) has a second extension (y2) along the planetary carrier rotation axis (APT), wherein - The first extension (y1) is larger than the second extension (y2).

20. The planetary carrier (44) according to any one of claims 10 to 19. Its features are, Multiple planetary carrier protrusions (74) are provided on the first disc-shaped body (48), and the multiple planetary carrier protrusions are arranged adjacent to the first bearing recess (60).

21. The planetary frame (44) according to any one of claims 10 to 20. Its features are, - The insert (68) is connected to the first disc-shaped body, and the insert (68): - Including a fastener (94), the insert (68) is connected to the support body (46) via the fastener, wherein - The solid (94) has a radially outward connecting surface (96), the connecting surface: o forms at least one radial extension (98), and o forms the connecting teeth (100).

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