Planetary gear transmission mechanism with planet carrier and gear ring

Abstract

The invention relates to a planetary gear train having a planet carrier and a ring gear, the planet carrier having a first cheek component, a second cheek component and a bridging region, the first cheek component being connected to the second cheek component by means of the bridging region, the first cheek component having an inclined surface on the inner side thereof, the ring gear being received in the first cheek component, and the ring gear being connected to the second cheek component by means of the inclined surface. And is axially arranged between the inclined surface and the bridging region.

Description

Technical Field

[0001] The present invention relates to a planetary gear transmission mechanism having a planet carrier and a ring gear. Background Art

[0002] As is well known, a planetary gear stage has a planet carrier and a ring gear.

[0003] As the closest prior art, a planetary gear transmission mechanism is known from US2004 / 0 235 609A1, in which an axle nut is screwed onto the driven shaft of the planetary gear transmission mechanism. The bearing of the drive shaft is received in the planet carrier of the planetary gear transmission mechanism.

[0004] A support device for a planetary gear transmission mechanism is known from DE 10 2020 007 324 A1.

[0005] A planetary gear transmission mechanism is known from US2007 / 0 078 037A1.

[0006] A planetary gear transmission mechanism is known from CN 1 15 013 484A.

[0007] A planetary gear transmission mechanism is known from CN 1 13 531 060A. Summary of the Invention

[0008] Therefore, the object of the present invention is to improve the planetary gear transmission mechanism in a compact manner so that the power per unit volume is as large as possible.

[0009] According to the present invention, this object is achieved by a planetary gear transmission mechanism according to the features given in claim 1.

[0010] In the planetary gear transmission mechanism, an important feature of the present invention is that the planetary gear transmission mechanism is designed to have a planet carrier and a ring gear, wherein the planet carrier has a first cheek member, a second cheek member and a bridging region, wherein the first cheek member is connected to the second cheek member through the bridging region, wherein the first cheek member has an inclined surface on its inner side, and wherein a snap ring is received in the first cheek member and is axially arranged between the inclined surface and the bridging region.

[0011] The advantage here is that due to this inclined surface, the retaining ring can be arranged in the region of the first cheek member with a relatively large wall thickness. In the region with a relatively thin wall thickness due to the inclined surface, an axle nut for adjusting the bearing preload can be arranged. Therefore, the radial wall thickness of the first cheek member in front of the inclined surface in the axial direction is thinner than the radial wall thickness of the first cheek member behind the inclined surface. In the case where the planet carrier shaft extends into the first cheek member, this inclined surface provides more structural space for driving the planet carrier shaft of the drive stage of the transmission mechanism, wherein the planet carrier shaft is non-rotatably connected to the sun gear of the planetary gear transmission mechanism, and the sun gear meshes with the planetary gears arranged in the planet carrier in a rotatably supported manner.

[0012] Therefore, when loaded with lateral forces, higher stability is provided by this inclined surface.

[0013] The retaining ring arranged in the thicker region of the first cheek member restricts the bolt passing through the corresponding through-hole of the first cheek member in the axial direction. In the opposite direction of the axial direction, the bolt is restricted by being inserted into the blind hole of the second cheek member. Therefore, the force generated by the axial restriction is led out through the thicker region of the first cheek member.

[0014] Generally speaking, the solution according to the invention achieves a stable structural form with little material input, and thus the transmission mechanism can withstand high power loading while having a very small structural volume.

[0015] In particular, the bearings of the planet carrier and the bearings of the drive shaft of the planetary gear transmission mechanism are spaced apart from the inclined surface, especially axially. Therefore, none of the bearings abuts against the inclined surface.

[0016] In an advantageous design, at least part of the bolt of the planetary gear transmission mechanism is inserted into the blind hole of the second cheek member, wherein the bolt passes through the hole penetrating the first cheek member. The advantage here is that the bolt is axially restricted on one side by the blind hole.

[0017] In an advantageous design, the retaining ring axially restricts the bolt or bolts of the planetary gear transmission mechanism. The advantage here is that the retaining ring is supported in the hard and stable region of the first cheek member, and thus can reliably carry out the restriction.

[0018] In an advantageous design, the inclined surface is designed such that in the region covered by the inclined surface in the axial direction, the radial wall thickness of the first cheek member monotonically, especially strictly monotonically, increases as the distance from the second cheek member decreases. The advantage here is that the axial end region of the first cheek member is implemented to be hard and stable.

[0019] In an advantageous design, the inclined surface has a conical shape, wherein the axis of the cone of the conical shape is oriented coaxially with the axis of rotation of the planet carrier. The advantage here is that the manufacturing can be made simple.

[0020] In an advantageous design, the region covered by the inclined surface in the axial direction overlaps or is adjacent to the region covered by the shaft nut screwed onto the external thread section of the first cheek member in the axial direction. The advantage here is that the mating region for the shaft nut is stabilized and strengthened.

[0021] In an advantageous design, a first bearing is sleeved on the first cheek member, wherein the region covered by the inner ring of the first bearing in the axial direction overlaps or is adjacent to the region covered by the inclined surface in the axial direction. The advantage here is that the bearing seat region of the bearing is strengthened by means of the inclined surface.

[0022] In an advantageous design, the bearings of the input shaft and the bearings in all other bearings are spaced apart from the conical inclined surface. That is, in particular, these bearings do not abut against the conical inclined surface through their inner or outer rings.

[0023] In an advantageous design, the snap ring is arranged between the inclined surface and the second cheek member in the axial direction. The advantage here is that the snap ring is arranged in the strengthened region of the first cheek member.

[0024] In an advantageous design, the snap ring is received on the step of the first cheek member. The advantage here is that the manufacturing can be made simple.

[0025] In an advantageous design, the shaft nut abuts against the inner ring of the first bearing. The advantage here is that the bearing preload can be adjusted in a simple manner.

[0026] In an advantageous design, the radial wall thickness of the first cheek member is greater in the region covered by the snap ring in the axial direction than in the region covered by the external thread section and / or the shaft nut in the axial direction. The advantage here is that the snap ring is arranged in a more strengthened region compared to the shaft nut.

[0027] In an advantageous design, a second bearing is sleeved on the second cheek member, wherein the inner ring of the second bearing abuts against the step of the second cheek member, and wherein the outer ring of the second bearing and the outer ring of the first bearing abut against, in particular, in an opposing manner, the protrusions that radially protrude inward on the housing part and have ring gear teeth. The advantage here is that the bearings can be arranged back-to-back.

[0028] In an advantageous design, the housing part serves as a ring gear, wherein the ring gear teeth are configured in the protrusions, in particular, wherein the ring gear teeth mesh with planetary gears which are rotatably supported on bolts, in particular by means of needle roller bearings, and the planetary gears mesh with a rotatably supported sun gear. The advantage here is that the number of parts is as small as possible and thus the manufacturing costs are low.

[0029] In an advantageous design, the planet carrier has such holes for receiving the planetary gear shafts of the planetary gears that the conical bevel is interrupted in the circumferential direction by these holes, in particular completely, and at this time, in particular, not only partially interrupted but even completely interrupted in the radial direction respectively. The advantage here is that the conical bevel has an interruption in the circumferential direction and thus the elastic conditions are further optimized. Here, the interruption caused by the corresponding holes is complete, i.e., correspondingly complete in the radial direction. Thereby, the optimal can be achieved in terms of elastic properties.

[0030] Here, the circumferential direction, the radial direction and the axial direction are always based on the rotation axis of the planet carrier.

[0031] In an advantageous design, the first bearing is designed as an angular contact bearing / radial thrust bearing / angular contact ball bearing inclined, and the second bearing is designed as an angular contact bearing / radial thrust bearing / angular contact ball bearing inclined, in particular arranged back-to-back. The advantage here is that large forces can be derived.

[0032] In an advantageous design, the planetary gear transmission has in particular a driven first planetary gear stage which has a planet carrier shaft extending into the first cheek member, wherein the region covered by the planet carrier shaft in the axial direction includes the region covered by the bevel in the axial direction, wherein the first cheek member is spaced apart from the planet carrier shaft, in particular, wherein, within the region covered by the bevel in the axial direction, the radial interval / part covered by the planet carrier shaft

[0033] - or is radially spaced from the radial interval / part covered by the bevel

[0034] - or includes the radial interval / part covered by the bevel.

[0035] The advantage here is that in the variant with a radial spacing, a larger oil volume can be provided in the internal space of the transmission and thus heat dissipation is improved, whereby a transmission with a higher performance per unit structural volume can be achieved. In the variant radially overlapping with the radial interval covered by the bevel, the planet carrier shaft can also be designed as inclined in this region, so that the planet carrier shaft can be strengthened. Since this is the region on the driven side of the planet carrier shaft, a large torque must be transmitted here with a smaller outer diameter of the planet carrier shaft, so that the planet carrier shaft implemented with reinforcement in this region makes a significant contribution to the highest possible compactness.

[0036] Other advantages are derived from the dependent claims. The invention is not limited to the feature combinations recited in the claims. For a person skilled in the art, other reasonable combinations of the claims and / or the features of individual claims and / or the description and / or the features of the drawings can be derived, in particular from the purpose setting and / or from the purposes put forward by comparison with the prior art. BRIEF DESCRIPTION OF THE DRAWINGS

[0037] The invention will now be explained in more detail with reference to the schematic drawings:

[0038] In Figure 1 a planetary gear transmission according to the invention is shown in an inclined view, which has a planet carrier with a conical bevel 3.

[0039] In Figure 2 the planet carrier is shown in an inclined view.

[0040] In Figure 3 a top view of the planet carrier is shown.

[0041] In Figure 4 a top view of the individual planet carrier is shown.

[0042] In Figure 5 an inclined view looking at the individual planet carrier is shown.

[0043] In Figure 6 an inclined view of a transmission stage of a planetary gear transmission with a planet carrier is shown. DETAILED DESCRIPTION

[0044] As shown in the drawings, the planetary gear transmission has a planet carrier which has a first cheek member 1 and a second cheek member 2, which are spaced apart from one another in the axial direction and are connected to one another by a bridging region 22 of the planet carrier. The bridging regions 22 are spaced apart from one another especially regularly in the circumferential direction.

[0045] Rectangular notches, especially radially passing through the planet carrier, are arranged in the circumferential direction between the respective closest neighboring bridging regions 22, and the corner regions of the notches have rounded portions 21. Thereby, the strength against the action of transverse forces is increased. In particular, the rounded portions 21 have an increased fracture resistance.

[0046] In the planet carrier, the planetary gears 7 are supported on pins 8, in particular by means of needle bearings, and the pins 8 are inserted into the first cheek member 1 on the one hand and into the second cheek member 2 on the other hand. The needle bearings are arranged on the pins and enable a compact structure.

[0047] The first cheek member 1 of the planet carrier has a conical inclined surface 3 on its inner side, and the end region of the planet carrier facing the drive side of the transmission mechanism can be strengthened by using this conical inclined surface 3.

[0048] The mathematical imaginary cone axis of the conical inclined surface 3 is oriented coaxially with the rotation axis of the planet carrier.

[0049] The planet carrier is integrally, especially integrally formed by the first cheek member 1, the second cheek member 2 and the bridging region 22.

[0050] During manufacturing, before milling off the corresponding remaining part of the notch, the circular part 21 is designed as a simple hole.

[0051] The first cheek member 1 has a bearing seat for the first bearing 4 of the planet carrier on its radial outer periphery, and the first bearing is received in the ring gear designed to form the housing. The ring gear teeth of the ring gear are axially spaced from the bearing seat of the first bearing 4.

[0052] On its radial outer periphery, the second cheek member 2 has a bearing seat for the second bearing 9 of the planet carrier, and the second bearing is received in the ring gear designed to form the housing. The ring gear teeth of the ring gear are axially spaced from the bearing seat of the second bearing 9. The first bearing 6 is axially spaced from the second bearing 9.

[0053] The planet gears 7 are circumferentially spaced from each other, especially regularly spaced from each other, and mesh with the ring gear teeth of the ring gear and mesh with the sun gear, and the sun gear is non-rotatably connected to the shaft 20 or designed integrally with the shaft, that is, especially integrally.

[0054] A retaining ring 6 for the axial limiting bolt 8 is provided, and the planet gear 7 is rotatably supported on the bolt by means of a needle bearing. Since the bolt 8 is inserted into the blind hole formed in the second cheek member 2 and extends through the hole penetrating the first cheek member 1, the end sides of the bolt 8 extending out of the through hole respectively abut against the retaining ring 6, and the retaining ring is received in the inner groove of the first cheek member 1 and extends radially inward beyond the first cheek member 1.

[0055] As can be seen in Figure 1 In the illustrated implementation variant, the inner groove is designed as a stepped portion on the inner side of the first cheek member 1. In this way, the installation can be made simple. Because after the bolt 8 is inserted from the inside, due to the centrally located through opening of the first cheek member, the retaining ring 6 can be radially expanded into the inner groove or stepped portion in an elastically preloaded driving manner. However, at this time, the bolt 8 must be inserted deep enough into the blind hole of the second cheek member 2 in the axial direction.

[0056] Preferably, the retaining ring 6 is axially spaced from the conical inclined surface 21.

[0057] A stepped portion is formed on the radially outer peripheral portion of the second cheek member 2, and the inner ring of the second bearing 2 abuts against this stepped portion.

[0058] The outer rings of the bearings 4 and 9 abut against the radially inwardly protruding protrusions of the ring gear, and the ring gear teeth are carried on these protrusions.

[0059] An external thread region is formed on the radially outer peripheral portion of the first cheek member 1, and a shaft nut is screwed onto this external thread region. The shaft nut abuts against the inner ring of the first bearing 1. Thus, the bearing preload can be adjusted by means of the shaft nut. The feedback of the bearing preload is achieved by means of the planet carrier, in particular also by means of the region with a conical inclined surface of the first cheek member of the planet carrier.

[0060] The teeth of the planet carrier 7 extend into the corresponding recesses.

[0061] In the region covered by the inclined surface 3 in the axial direction, the outer peripheral portion of the first cheek member 1 is designed as an external cylinder, i.e., in particular with a unique and in particular constant radial distance.

[0062] The radial distance, the radial direction, the axial direction, and the circumferential direction are always with respect to the direction of the rotational axis of the planet carrier.

[0063] In a further embodiment according to the invention, instead of the conical inclined surface 3, inclined surfaces of other shapes are used. However, in any case, in the planet carrier used, in the region covered by the inclined surface in the axial direction, as the distance from the cheek member 2 decreases, the radial wall thickness of the first cheek member 1 is a monotonically increasing, in particular strictly monotonically increasing function of this distance.

[0064] As shown in Figure 1 the planet carrier shaft of the preceding driving planetary gear stage extends into the first cheek member of the planet carrier and is spaced apart therefrom, in particular radially spaced apart, here.

[0065] The planet carrier shaft is rotatably supported in the housing part only by a single bearing, because the sun gear inserted into the planet carrier shaft is supported, so to speak, by the planetary gears 7. The planetary gears are in turn rotatably supported in the planet carrier shaft. The planetary gears mesh with the driven sun gear shaft and also with the ring gear teeth machined in the housing part.

[0066] Preferably, the dimensions of the planetary gear shafts of the planetary gears should be designed to be so stable, i.e., designed with such a diameter, that the conical inclined surface 3 is not only partially interrupted in the radial direction, but even completely interrupted, as can be seen in Figure 2 here.

[0067] The shaft nut 10 is screwed onto the first cheek member 1 by means of its internal thread, for which purpose the first cheek member has an external thread.

[0068] Also important here is that the region covered by the shaft nut 10 in the axial direction overlaps / abuts against the region covered by the conical bevel 3 in the axial direction. Thus, elastic properties can be optimally provided.

[0069] Another advantage of the planetary gear drive is that the support of the drive shaft and all other bearings are spaced apart from the conical bevel 3, i.e., in particular, the inner or outer ring does not abut against the conical bevel 3.

[0070] In a further embodiment according to the invention, within the region covered by the bevel in the axial direction, the radial interval covered by the planet carrier shaft includes the radial interval covered by the bevel, in particular the inner conical bevel. Thus, the planet carrier shaft effectively utilizes the spatial region created by the bevel and is thus designed with a correspondingly large wall thickness, thereby improving the diffusion of the heat flow and also increasing the rigidity, in particular against transverse forces. Preferably, the planet carrier shaft itself again has a corresponding bevel, in particular an outer conical bevel.

[0071] List of reference numerals

[0072] 1 First cheek member

[0073] 2 Second cheek member

[0074] 3 Conical bevel

[0075] 4 Bearing

[0076] 5 Ring gear, in particular forming the housing

[0077] 6 Retaining ring

[0078] 7 Planet gear

[0079] 8 Bolt

[0080] 9 Bearing

[0081] 10 Shaft nut

[0082] 20 Shaft

[0083] 21 Circular part

[0084] 22 Bridging region

[0085] 23 Hole for the planet gear shaft

Claims

1. A planetary gear transmission mechanism having a planet carrier and a ring gear, - Among them, The planet carrier has a first cheek member, a second cheek member, and a bridging region, - wherein the first cheek member is connected to the second cheek member through the bridging region, Characterized in that, - The first cheek member has an inclined surface on its inner side, - wherein a snap ring is received in the first cheek member and is axially arranged between the inclined surface and the bridging region, In particular, wherein the bearings of the planet carrier and the bearings of the drive shaft of the planetary gear transmission mechanism are spaced apart from the inclined surface, especially axially spaced apart.

2. The planetary gear transmission mechanism according to claim 1, wherein The pins of the planetary gears are at least partially inserted into the blind holes of the second cheek member, wherein the pins pass through the holes penetrating the first cheek member.

3. The planetary gear transmission mechanism according to any one of the above claims, characterized in that, The snap ring axially limits the pin or pins of the planetary gear transmission mechanism.

4. The planetary gear transmission mechanism according to any one of the above claims, characterized in that, The inclined surface is designed such that in the region covered by the inclined surface in the axial direction, the radial wall thickness of the first cheek member monotonically, especially strictly monotonically, increases as the distance from the second cheek member decreases.

5. The planetary gear transmission mechanism according to any one of the above claims, characterized in that The inclined surface has a conical shape, wherein the cone axis of the conical shape is coaxially oriented with the rotational axis of the planet carrier.

6. The planetary gear transmission mechanism according to any one of the above claims, characterized in that, The shaft nut is screwed onto the first cheek member through its internal thread. For this purpose, the first cheek member has an external thread, and / or the region covered by the inclined surface in the axial direction overlaps or abuts against the region covered by the shaft nut screwed onto the external thread section of the first cheek member in the axial direction.

7. The planetary gear transmission mechanism according to any one of the above claims, characterized in that, A first bearing is sleeved on the first cheek member, wherein the region covered by the inner ring of the first bearing in the axial direction overlaps with the region covered by the inclined surface in the axial direction, and / or the bearings of the input shaft and the bearings in all other bearings are spaced apart from the conical inclined surface, that is, especially do not abut against the conical inclined surface through their inner rings or outer rings.

8. The planetary gear transmission mechanism according to any one of the above claims, characterized in that, The snap ring is axially arranged between the inclined surface and the second cheek member.

9. The planetary gear transmission mechanism according to any one of the above claims, characterized in that, The snap ring is received on the step of the first cheek member.

10. The planetary gear transmission mechanism according to any one of the above claims, characterized in that, The region covered by the shaft nut in the axial direction overlaps with the region covered by the conical inclined surface in the axial direction, and / or the shaft nut abuts against the inner ring of the first bearing.

11. The planetary gear transmission mechanism according to any one of the above claims, characterized in that ,, The radial wall thickness of the first cheek member in the region covered by the snap ring in the axial direction is greater than the radial wall thickness in the region covered by the external thread section and / or the shaft nut in the axial direction.

12. The planetary gear transmission mechanism according to any one of the above claims, characterized in that, A second bearing is sleeved on the second cheek member, wherein the inner ring of the second bearing abuts against the step of the second cheek member, and wherein the outer ring of the second bearing and the outer ring of the first bearing abut against, especially in an opposing manner, the protrusions radially inwardly protruding on the housing member having the ring gear teeth.

13. The planetary gear transmission mechanism according to any one of the above claims, characterized in that, The housing member serves as a ring gear, wherein the ring gear teeth are formed in the protrusions, especially wherein the ring gear teeth mesh with the planetary gears rotatably supported on the pins by means of needle bearings, and the planetary gears mesh with the rotatably supported sun gear.

14. The planetary gear transmission mechanism according to any one of the above claims, characterized in that, The planet carrier has holes for receiving the planetary gear shafts of the planetary gears such that the conical inclined surface is especially completely interrupted in the circumferential direction by the holes, especially not only partially interrupted in the radial direction but even completely interrupted, and / or the first bearing is designed as an angular contact bearing, and the second bearing is designed as an angular contact bearing, especially arranged back-to-back.

15. The planetary gear transmission mechanism according to any one of the above claims, characterized in that, The planetary gear transmission has in particular a first planetary gear stage for driving, the first planetary gear stage having a carrier shaft that projects into a first cheek member, wherein the region axially covered by the carrier shaft includes the region axially covered by an inclined surface, wherein the first cheek member is spaced apart from the carrier shaft, in particular wherein, within the region axially covered by the inclined surface, the radial interval covered by the carrier shaft - or is radially spaced apart from the radial interval covered by the inclined surface; - or includes the radial interval covered by the inclined surface.

Images