Planetary gear transmission mechanism

Abstract

The invention relates to a planetary gear (1), comprising a housing (2), a sun gear (3), a planet carrier (4), at least one planet gear (5) and a ring gear (6). The planet carrier (4) is rotatably mounted in the housing (2). The housing (2) defines a mounting direction (7) for mounting the planet carrier (4). A bearing seat (8) of the planet carrier (4) serves to rotatably support the planet carrier (4) in the housing (2) and is arranged adjacent to the insertion end (9) of the planet carrier (4) and behind the ring gear (6) in the installation direction (7) in the use position of the planet carrier (4), the diameter of the bearing seat being smaller than the inner diameter, in particular the addendum diameter, of the ring gear (6).

Description

Technical Field

[0001] The invention relates to a planetary gear mechanism having a housing, a sun gear, a planet carrier, at least one planet gear and a ring gear, wherein the planet carrier is rotatably supported in the housing. Background Art

[0002] Such planetary gear mechanisms are known in practice, for example, as planetary gear transmissions and, due to their compact design, can achieve high transmission ratios while requiring little space. Therefore, these planetary gear mechanisms are suitable, for example, as transmission mechanisms for industrial robots.

[0003] For example, a planetary gear mechanism is known from the document WO 2015 / 185 036 A1, which has a split planet carrier. The individual components of the split planet carrier are inserted into the housing of the planetary gear mechanism from two different sides and then connected to each other. However, due to the established positional relationship, this may bring about a certain amount of cost and lead to a decrease in quality. Summary of the invention

[0004] The object of the invention is to provide a planetary gear of the type mentioned in the introduction which can be assembled in a simple manner.

[0005] In order to achieve this object, a planetary gear transmission mechanism having the device and features of the independent claim is proposed. Therefore, in order to achieve this object, a planetary gear transmission mechanism is particularly proposed, which has a housing, a sun gear, a planet carrier, at least one planetary gear and a ring gear, wherein the planet carrier is rotatably supported in the housing, the housing defines an installation direction for installing the planet carrier, and the planet carrier has a bearing seat on its outer side, the bearing seat is adjacent to the insertion end of the planet carrier and is arranged behind the ring gear in the use position of the planet carrier along the installation direction, and the outer diameter of the bearing seat is smaller than the inner diameter of the ring gear, in particular the tip circle diameter.

[0006] In this way, the planet carrier can be inserted from one side into its position of use in the housing of the gear mechanism. In this way, mounting on both sides (as is known in the prior art in planetary gear mechanisms) and the associated disassembly of the planet carrier can be avoided. In this way, the planet carrier can be designed, for example, in one piece or, if it is designed in two or more parts, can also be mounted outside the housing of the planetary gear mechanism. This can greatly simplify the assembly of the planetary gear mechanism and increase the precision.

[0007] Above-mentioned bearing seat can be called the bearing seat of the rear side or the far end of planet carrier.On this bearing seat, can be arranged with the rotary bearing of planetary gear transmission mechanism, for the planet carrier is rotatably supported in the housing.

[0008] According to the present invention, it is also provided that the bearing seat of the planetary carrier is arranged in front of the ring gear and / or adjacent to the end of the planetary carrier facing away from the insertion end in the installation direction and in the use position of the planetary carrier, and the diameter of the bearing seat of the planetary carrier is larger than the inner diameter of the ring gear, in particular, larger than the tooth tip circle diameter of the ring gear and / or larger than the diameter of the bearing seat of the planetary carrier adjacent to the insertion end. The at least one planetary gear is configured as a multi-stage planetary gear and has two bearing seats and at least two meshing parts, namely a sun gear meshing part meshing with the sun gear and a ring gear meshing part meshing with the ring gear. The ring gear meshing part of the planetary gear is arranged between the two bearing seats of the planetary gear. One of the two bearing seats of the planetary gear is arranged between the insertion end of the planetary gear and the ring gear meshing part, wherein the outer diameter of the bearing seat is smaller than the outer diameter of the ring gear meshing part. The other of the two bearing seats of the planetary gear is arranged between the ring gear meshing part and the sun gear meshing part of the planetary gear.

[0009] The housing can have a planet carrier receptacle with an insertion opening for the planet carrier, by which the installation direction of the planet carrier is defined. In the planet carrier receptacle, the planet carrier can then be arranged in a rotatably supported manner inside the housing. At least one bearing seat for a rotary bearing of the planet carrier can be constructed inside the planet carrier receptacle. The ring gear of the planetary gear mechanism can also be arranged inside the planet carrier receptacle. The ring gear can be arranged or formed in a non-rotatable manner inside the housing, in particular inside the planet carrier receptacle of the housing, and / or on the housing.

[0010] The planet carrier can have two bearing seats axially spaced apart from each other on its outer side with respect to its axis of rotation for rotatably supporting the planet carrier. This facilitates uniform force transmission between the planet carrier and the housing. When the planet carrier is in the use position in the housing, the ring gear of the planetary gear can be arranged between the two bearing seats. These bearing seats can be constructed on the outer side of the planet carrier. Rotary bearings for rotatably supporting the planet carrier in the housing can be arranged on these bearing seats.

[0011] As mentioned above, according to the invention, the planet carrier has a bearing seat, which is arranged in the installation direction and in the use position of the planet carrier before the ring gear and / or adjacent to the end of the planet carrier facing away from the insertion end. The bearing seat can be called the front bearing seat of the planet carrier, or can also be called the proximal bearing seat of the planet carrier, and is formed on the outer side of the planet carrier. As mentioned above, according to the invention, the diameter of the bearing seat is greater than the inner diameter of the ring gear, in particular greater than the tooth tip circle diameter of the ring gear and / or greater than the diameter of the rear bearing seat of the planet carrier adjacent to the insertion end.

[0012] The planet carrier can have a shaft, in particular an output shaft, or can be designed as a shaft, in particular an output shaft, of a planetary gear.

[0013] The at least one planet gear of the planetary gear mechanism can be rotatably supported in the planet carrier. The at least one planet gear can mesh with the sun gear and / or the ring gear of the planetary gear mechanism. In particular, when the planet gear is configured as a multi-stage planetary gear with two meshing parts, the at least one planet gear can mesh not only with the sun gear but also with the ring gear of the planetary gear mechanism.

[0014] The planet carrier can have at least one planet gear receptacle for a planet gear. The planet carrier preferably has a number of planet gear receptacles that corresponds to the number of planet gears of the planetary gear mechanism. The planet gears are rotatably supported in the planet gear receptacles in the use position.

[0015] The at least one planetary gear receptacle can be designed, for example, as a blind hole or as a stepped hole. If the planetary gear receptacle is designed as a stepped hole, the planetary gear can be inserted into the planetary gear receptacle from one side of the stepped hole. For example, a mounting aid can be inserted into the planetary gear receptacle from the other side of the stepped hole. With the aid of the mounting aid, for example a pin, the planetary gear shaft of the planetary gear can be supported when the pinion is mounted. If the planetary gear receptacle is designed as a blind hole, the preferably continuous stepped hole can be omitted.

[0016] The at least one planet gear receptacle may have an insertion opening through which the at least one planet gear can be inserted into its use position in the planet gear receptacle in an installation direction. The planet gear receptacle may be oriented with its insertion opening in such a way that the installation direction defined by the planet gear receptacle coincides with the installation direction of the planet carrier in its use position in the housing. The above-mentioned insertion opening of the housing and the insertion opening of the planet gear receptacle may each be arranged in an axial plane with respect to the axis of rotation of the planetary gear mechanism and / or on the same side of the planetary gear mechanism.

[0017] As described above, the at least one planetary gear is configured as a multi-stage planetary gear and has at least two toothings. The at least two toothings of the planetary gear may be different from each other, for example, having different tooth tip diameters and / or pitch circle diameters and / or pitch circle diameters.

[0018] The multi-stage planetary gear has a sun gear meshing portion meshing with the sun gear of the planetary gear mechanism and a ring gear meshing portion meshing with the ring gear of the planetary gear mechanism. In this way, torque can be transmitted from the sun gear via the planetary gear and the ring gear to the planet carrier of the planetary gear mechanism, and vice versa.

[0019] The teeth can be spaced apart from each other in the axial direction with respect to the rotation axis of the planetary gear. Thus, the planetary gear can be adapted with its teeth to the axial distance between the ring gear and the sun gear of the planetary gear mechanism.

[0020] The tip circle diameter and / or pitch circle diameter and / or pitch circle diameter of the sun gear meshing of the at least one planet gear can be selected independently of the tip circle diameter and / or pitch circle diameter and / or pitch circle diameter of the ring gear meshing of the planet gear. When the planet gear is in the use position, the ring gear meshing can project radially with respect to the rotation axis of the planet carrier beyond a rear or distal bearing seat of the planet carrier, which is arranged adjacent to the insertion end of the planet carrier.

[0021] In this context, it can be advantageous if at least one planet gear receptacle has a lateral opening oriented transversely to the axis of rotation of the planet carrier, through which the ring gear teeth of the planet gear can protrude in order to mesh with the inner teeth of the ring gear.

[0022] As mentioned above, the toothed ring meshing portion of the at least one planetary gear meshing with the toothed ring is arranged between the two bearing seats of the planetary gear. This is conducive to uniform distribution of the forces transmitted to the planetary gear when the planetary gear transmission is in operation. The other bearing seat of the planetary gear is arranged between the toothed ring meshing portion and the sun gear meshing portion of the planetary gear. The arrangement of the bearing seat between the toothed ring meshing portion and the sun gear meshing portion is conducive to the planetary gear being constructed as short as possible in the axial direction with respect to the longitudinal axis of the planetary gear. This makes it possible to provide a particularly compact planetary gear transmission.

[0023] The at least one planetary gear also has a bearing seat between the insertion end of the planetary gear in its use position and the toothed ring meshing portion, and the outer diameter of the bearing seat is smaller than the outer diameter of the toothed ring meshing portion. In this way, the at least one planetary gear can be inserted into its use position within the planetary gear receiving portion mentioned above of the planetary gear transmission mechanism from one side in the installation direction and / or as a one-piece element. Thus, the bearing seat on the rear side along the installation direction of the planetary gear can pass through the toothed ring based on its size without colliding with the toothed ring. The bearing seat on the rear side can also be referred to as the bearing seat at the far end of the planetary gear. The outer diameter of the rotary bearing arranged on the bearing seat can be smaller than the outer diameter of the toothed ring meshing portion of the at least one planetary gear. In this way, the rotary bearing (which can be a radial bearing) can be pushed onto the bearing seat and then pushed into the planetary gear receiving portion of the planetary carrier together with the planetary gear.

[0024] The at least one planetary gear receptacle may have a bearing seat for the outer side of the rotary bearing of the at least one planetary gear, in particular for the outer ring of the rotary bearing, which is arranged adjacent to the insertion opening of the planetary gear receptacle. The bearing seat is arranged in front of the ring gear in the installation direction of the planetary gear into the planetary gear receptacle and / or in front of the aforementioned side opening of the planetary gear receptacle. The inner diameter of the bearing seat may be at least as large as the outer diameter of the ring gear meshing of the at least one planetary gear, preferably larger than the outer diameter. The outer ring of the rotary bearing arranged on the bearing seat may be at least as large as the outer diameter of the ring gear meshing of the at least one planetary gear, preferably larger than the outer diameter. This facilitates the insertion of the planetary gear from one side into its use position in the planet carrier.

[0025] The aforementioned ring gear meshing portion of the at least one planetary gear may be a helical meshing portion. The aforementioned sun gear meshing portion of the at least one planetary gear may also be a helical meshing portion. The helical meshing portion can facilitate the smooth operation of the planetary gear transmission mechanism and also help reduce noise.

[0026] The helical teeth between at least one planet gear and the sun gear of the planetary gear mechanism (e.g. the aforementioned sun gear teeth) and the helical teeth between at least one planet gear and the ring gear of the planetary gear mechanism (e.g. the aforementioned ring gear teeth of the planetary gear mechanism) can be coordinated with each other so that the value of the effective axial force generated by the axial forces caused by these helical teeth during the operation of the planetary gear mechanism is less than 10% of the value of the axial force caused by the respective helical teeth, preferably 10% of the value of the smallest axial force. It is particularly advantageous that the helical teeth between at least one planet gear and the sun gear of the planetary gear mechanism (e.g. the aforementioned sun gear teeth) and the helical teeth between at least one planet gear and the ring gear of the planetary gear mechanism (e.g. the aforementioned ring gear teeth of the planetary gear mechanism) can be coordinated with each other so that the axial forces caused by the respective helical teeth during the operation of the planetary gear mechanism cancel each other out.

[0027] If small effective axial forces occur which are caused by the axial forces respectively caused by the individual bevel teeth and which are caused by the production tolerances of the bevel teeth matched to one another, a mutual compensation of the axial forces in this sense can also be achieved.

[0028] In this way, it is possible to rotatably support at least one planetary gear in a planet carrier with a relatively favorable radial bearing, for example by means of a needle roller bearing of compact design. Such needle roller bearings are characterized by their high radial load capacity and the small radial installation space required. However, needle roller bearings are not very suitable for absorbing axial forces. The axial forces that occur can be compensated by axial force compensation by means of mutually coordinated helical teeth, and the bearing of the at least one planetary gear can be designed accordingly. In order to support the remaining axial forces, the planetary gear mechanism can have at least one axial bearing element, which will be explained in more detail below.

[0029] It can be provided that the ratio of the inclination angles of the helical meshing corresponds to the ratio of the pitch circle diameters of the helical meshing. If this condition is met, this is conducive to completely offsetting each other or at least offsetting each other to a large extent the axial forces generated by the helical meshing. The pitch circle diameter of the sun gear meshing can be 20 mm, for example. The pitch circle diameter of the ring gear meshing can be 10 mm, for example. Therefore, the inclination angle of the sun gear meshing can be 10°, for example, and the inclination angle of the ring gear meshing can be 5°. The inclination angles of the two helical meshings can point in the same direction here. The inclination angle of the ring gear meshing can be, for example, between 2° and 15°. The inclination angle of the sun gear meshing can be, for example, between 4° and 30°.

[0030] The at least one planetary gear may have a planetary shaft. The sun gear meshing portion may be formed on a sun pinion arranged on the planetary shaft.

[0031] An adhesive may be arranged between the planet shaft and the sun pinion to prevent the sun pinion from slipping. Furthermore, a conical connection may be provided between the planet shaft and the sun pinion, by means of which the sun pinion is connected to the planet shaft. In a preferred embodiment of the planetary gear mechanism, it is provided that not only an adhesive is arranged between the sun pinion and the planet shaft, but also a conical connection is formed, so that the sun pinion can be particularly reliably fixed to the planet shaft in this embodiment.

[0032] The sun pinion can be fixed on the planetary shaft by means of a screw and / or by means of a nut, for example. If a screw is used to fix the sun pinion on the planetary shaft, the screw can be screwed into the planetary shaft at the end face, for example.

[0033] Depending on the pitch circle diameters of the individual toothings, the inclination angle of the sun gear toothing can be greater, smaller or equal to the inclination angle of the ring gear toothing of the planetary gear.

[0034] In particular, when a radial bearing is used as a rotary bearing for rotatably supporting at least one planet gear of a planetary gear train, which radial bearing is not very suitable for absorbing axial forces due to its type of construction, it may be advantageous for the planetary gear train to have at least one axial bearing element, for example an axial sliding disk, which is provided for absorbing axial forces. The at least one axial bearing element can be assigned to at least one rotary bearing for rotatably supporting the at least one planet gear. If axial forces are to act on at least one planet gear during operation of the planetary gear train, they can be absorbed and discharged by the at least one axial bearing element.

[0035] Such axial forces may occur, for example, due to gravity, if the planetary gear changes its position in space during its use. This may occur, for example, when the planetary gear is used in industrial robots or when the axial forces cannot be completely compensated.

[0036] Preferably, the planetary gear has at least one such axial bearing element for each rotary bearing of each planetary gear, which is provided for absorbing axial forces.

[0037] In summary, the present invention therefore relates to a planetary gear transmission mechanism, which has a housing, a sun gear, a planet carrier, at least one planet gear and a ring gear. The planet carrier is rotatably supported in the housing. The housing defines an installation direction for installing the planet carrier. A bearing seat of the planet carrier for a rotating bearing (which is used to rotatably support the planet carrier in the housing) is arranged adjacent to the insertion end of the planet carrier and on the rear side of the ring gear in the use position of the planet carrier along the installation direction, and the outer diameter of the bearing seat is smaller than the inner diameter of the ring gear, in particular the tooth tip circle diameter.

[0038] The invention is explained in more detail below with reference to exemplary embodiments, but the invention is not limited to these exemplary embodiments. Further exemplary embodiments result from the mutual combination of features of one or more claims and / or from the combination of one or more features of the exemplary embodiments. BRIEF DESCRIPTION OF THE DRAWINGS

[0039] In the attached picture:

[0040] Figure 1 A sectional side view of a planetary gear transmission is shown, wherein a housing defines an installation direction for installing a planet carrier of the planetary gear transmission, wherein a bearing seat of the planet carrier is adjacent to an insertion end of the planet carrier and is arranged at the rear side of a gear ring of the planetary gear transmission in the use position of the planet carrier along the installation direction, and the diameter of the bearing seat is smaller than the inner diameter of the gear ring;

[0041] Figure 2 Show Figure 1 Isometric view of the planetary gear transmission mechanism;

[0042] Figure 3 An isometric view of a planet carrier of a planetary gear train shown in the above-mentioned figures, the planet carrier having planet gears with spur gears, which are arranged upstream of a total of six planet gear receptacles of the planet carrier, which are arranged evenly distributed about the axis of rotation of the planet carrier;

[0043] Figure 4 Shown in Figure 3 A side view of a section of a planet carrier and planet gears shown in FIG.

[0044] Figures 5 to 7 Different views of a planetary gear designed as a multi-stage planetary gear, wherein the planetary gear has two straight teeth spaced axially apart from one another; and

[0045] Figures 8 to 10 Shown in Figure 4 Different views of a planetary gear shown in FIG. Figure 1 and Figure 2 In the planetary gear mechanism shown in , the planetary gear is constructed as a multi-stage planetary gear and has two helical teeth. DETAILED DESCRIPTION

[0046] All the figures show at least parts of a planetary gear, which is designated as a whole by 1 and is designed as a planetary gear.

[0047] The planetary gear mechanism 1 comprises a housing 2, a sun gear 3, a planet carrier 4 serving as an output shaft, and a plurality of planetary gears 5 configured as multi-stage planetary gears. A ring gear 6 of the planetary gear mechanism 1 is arranged inside the housing 2. The planet carrier 5 is supported in a rotationally relative manner to the fixed ring gear 6 inside the housing 2.

[0048] Figure 3 and Figure 4 The planet carrier 4 and the planet gears 5 are shown in separate views. Figure 5 , Figure 6 and Figure 7 A first embodiment of a planetary gear 5 is shown, which has a straight toothing. Figure 8 , Fig. 9 and Fig.10 A second embodiment of a planetary gear 5 is shown, which is also designed as a multi-step planetary gear and has two helical teeth. Figure 1 The planetary gears 5 of the planetary gear mechanism 1 shown in FIG. 1 are planetary gears 5 having helical teeth.

[0049] The housing 2 of the planetary gear mechanism 1 shown in the drawings defines an installation direction 7 for installing the planet carrier 4. The planet carrier 4 has a bearing seat 8 on its outer side, which is adjacent to the insertion end 9 of the planet carrier 4 and is arranged behind the ring gear 6 in the use position of the planet carrier 4 along the installation direction 7 and can also be called a distal bearing seat. The outer diameter of the distal bearing seat 8 is smaller than the inner diameter, that is, smaller than the tooth tip circle diameter of the ring gear 6.

[0050] In this way, the planet carrier 4 can be inserted into its use position inside the housing 2 from one side of the housing 2. This facilitates the one-piece construction of the planet carrier 5, which consists of Figure 3 and Figure 4 Especially clearly visible.

[0051] The housing 2 has a planet carrier receptacle 10 with an insertion opening 11 for the planet carrier 4. The planet carrier receptacle 10 and its insertion opening 11 predetermine the installation direction 7 of the planet carrier 4.

[0052] The ring gear 6 is arranged in the planet carrier receptacle 10 of the housing 2 and is otherwise non-rotatable. The planet carrier 4 has a total of two bearing seats on its outer side, which are axially spaced apart from each other about its rotation axis R, namely the above-mentioned rear or distal bearing seat 8 and the front or proximal bearing seat 12. The front bearing seat 12 of the planet carrier 4 is the bearing seat arranged closer to the insertion opening 11 of the planet carrier receptacle 10 for the planet carrier 4 in the use position of the planet carrier 4. When the planet carrier 4 is in the use position, the ring gear 6 is arranged between the two bearing seats 8 and 12. The two bearing seats 8 and 12 are constructed on the outer side of the planet carrier 4 and are used to rotatably support the planet carrier 4 in the housing 2 of the planetary gear transmission.

[0053] The front bearing seat 12 of the planet carrier 4 is arranged in front of the ring gear 6 in the installation direction 7 and in the use position of the planet carrier 4 and is also arranged adjacent to the end 13 of the planet carrier 4 facing away from the insertion end 9 of the planet carrier 4. The diameter of the front bearing seat 12 is larger than the inner diameter of the ring gear 6, that is, larger than the tip circle diameter of the ring gear and larger than the diameter of the rear bearing seat 8 of the planet carrier 4 adjacent to the insertion end 9 of the planet carrier 4.

[0054] The planetary gears 5 are rotatably supported in the planet carrier 4. The planetary gears 5 mesh with both the sun gear 3 and the ring gear 6 of the planetary gear mechanism 1. The planet carrier 4 has a planetary gear receptacle 14 for each planetary gear 5. In general, the planet carrier 4 is provided with six planetary gear receptacles 14.

[0055] Each planet gear receptacle 14 is designed as a blind hole and has an insertion opening 15 , through which the planet gear 5 can be inserted in a mounting direction 16 into its use position within the planet gear receptacle 14 .

[0056] The installation direction 16 of the planetary gear 5 is consistent with the installation direction 7 of the planetary carrier 4. Therefore, the planetary carrier 4 and the planetary gear 5 can be installed from the same side of the housing 2. The planetary carrier 4 has a side opening 17 for each of the planetary gear receptacles 14 thereof. The planetary gear receptacles 14 of the planetary carrier 4 are accessible in the lateral direction through the side openings 17. The ring gear meshing 18 of the planetary gear 5 configured as a multi-stage planetary gear, which will be described in detail below, can pass through the side openings 17 to mesh with the ring gear 6 of the planetary gear mechanism 1.

[0057] As described above, the planetary gear 5 is configured as a multi-stage planetary gear and has two toothings 18 and 19. The toothings 18 and 19 are axially spaced apart from one another with respect to the rotation axis of the respective planetary gear 5. The two toothings 18 and 19 differ from one another, for example in their different tooth tip diameters and / or pitch circle diameters and / or pitch circle diameters.

[0058] Each planetary gear 5 has a sun gear toothing 19 meshing with the sun gear 3 of the planetary gear 1 and a ring gear toothing 18 meshing with the ring gear 6 of the planetary gear 1 .

[0059] The sectional view of the planetary gear 1 and its component parts shows in particular that the ring gear toothing 18 passes through the lateral opening 17 of the planet carrier 4 and meshes with the ring gear 6 of the planetary gear 1 .

[0060] The ring gear teeth 18 of the planetary gears 5 meshing with the ring gear 6 are arranged between two bearing seats 20 and 21 of the corresponding planetary gears 5. Each planetary gear 5 has a bearing seat 20 arranged between an insertion end 22 of the corresponding planetary gear 5 and the ring gear teeth 18.

[0061] The diameter of the bearing seat 20 is smaller than the outer diameter of the toothed ring meshing 18. A rotary bearing 23, i.e. a radial bearing, is arranged on the bearing seat 20. The outer diameter of the rotary bearing 23, i.e. its outer ring 24, is at most as large as the outer diameter of the toothed ring meshing 18 of the planetary gear 5 and is preferably smaller than the outer diameter of the toothed ring meshing of the planetary gear. Based on this size, the bearing seat 20 together with the rotary bearing 23 arranged on the bearing seat 20 can be moved through the toothed ring 6 to its target position (e.g. Figure 1 ), and in doing so the ring gear meshing 18 of the planetary gear 5 meshes with the ring gear 6 of the planetary gear mechanism 1 .

[0062] The figure further shows that in each planetary gear 5 a bearing seat, respectively designated by 21 , is arranged between the respective ring gear toothing 18 and the respective sun gear toothing 19 of the planetary gear 5 .

[0063] Each planetary gear receptacle 14 has, adjacent to the insertion opening 15 into the planetary gear receptacle 14 and also in front of the side opening 17, a bearing seat 25 for the outer ring 24 of the rotary bearing 23 of the planetary gear 5 to be positioned in the planetary gear receptacle 14. The bearing seat 25 is also located in front of the ring gear 6 in the installation direction 16 of the planetary gear 5 and is therefore arranged between the axial insertion opening 15 and the radial side opening 17 of the planetary gear receptacle 14.

[0064] Here, the inner diameter of the bearing seat 25 is at least as large as the outer diameter of the toothed ring meshing 18 of the planetary gear 5 to be inserted into the planetary gear receptacle 14. Therefore, logically, the outer diameter of the outer ring 24 of the rotary bearing 23 arranged on the bearing seat 25 is at least as large as the outer diameter of the toothed ring meshing 18 of the planetary gear 5 and is preferably larger than the outer diameter of the toothed ring meshing of the planetary gear. In this way, it is ensured that the planetary gear receptacle 14 provides sufficient space in its region downstream of the insertion opening 15 in order to bring the toothed ring meshing 18 of the planet carrier 5 into its use position on the toothed ring 6 of the planetary gear mechanism 1.

[0065] Figures 8 to 10 An embodiment of a planetary gear 5 is shown which is likewise designed as a multi-step planetary gear and has a ring gear toothing 18 and a sun gear toothing 19 which are each designed as helical teeth.

[0066] Therefore, in Figures 8 to 10 The planetary gears 5 shown in FIG. 1 allow for a helical toothing between the sun gear 3 and the planetary gears 5 of the planetary gear set 1 as well as a further helical toothing between the planetary gears 5 and the ring gear 6 of the planetary gear set 1 .

[0067] The helical teeth are coordinated with one another so that the axial forces caused by the helical teeth 18 , 19 during operation of the planetary gear 1 cancel each other out, or at least the value of the effective axial force caused by the respective axial forces is less than 10% of the value of the smaller of the axial forces caused by the helical teeth 18 , 19 .

[0068] Optimally, the ratio of the inclination angles of the two oblique teeth 18 , 19 corresponds to the ratio of the pitch circle diameters of the oblique teeth 18 , 19 , in order to achieve an optimal compensation of the axial forces caused by the oblique teeth in each case.

[0069] Here, depending on the pitch circle diameters of the teeth 18 and 19 , the inclination angle of the sun gear toothing 19 can be greater or smaller than or equal to the inclination angle of the ring gear toothing 18 of the planetary gear 5 .

[0070] The planetary gear mechanism 1 has two axial bearing elements 26 in the form of axial sliding disks for each planet gear 5. The axial bearing elements 26 are assigned to the rotary bearings 23 of the planet gears 5 and are provided for absorbing axial forces. The axial bearing elements 26 are arranged on both sides of the toothed ring meshing 18 of the corresponding planet gear 5.

[0071] The axial bearing element 26 is used when the axial force balance provided by the ring gear meshing 18 and the sun gear meshing 19 of the planetary gear 5 is not completely achieved. The axial bearing element 26 can also be advantageous if axial forces, for example due to a change in the position of the planetary gear 1 in space, still act on the planetary gears 5 of the planetary gear 1 under certain circumstances and must be dissipated.

[0072] As long as the magnitude of the axial forces caused by the helical meshing of the ring gear meshing 18 and the sun gear meshing 19 is different, the helical meshing 18 and 19 are still at least coordinated with each other so that the value of the effective axial force caused by the axial forces of different magnitudes is less than 10% of the value of the smaller of the two axial forces caused by the helical meshing 18, 19. Such small axial forces that occur can be absorbed by the aforementioned axial bearing element 26.

[0073] The figures show that the planetary gears 5 each have a planetary shaft 27. The sun gear meshing 19 of the planetary gears 5 is respectively formed on a sun pinion 28 arranged on the planetary shaft 27 of the respective planetary gear 5. In order to fix the sun pinion 28 in its position on the respective planetary shaft 27, an adhesive is introduced between the sun pinion 28 and the planetary shaft 27. In addition, each sun pinion 28 is connected to its planetary shaft 27 via a conical connection 29. The conical connection 29 comprises an outer conical portion on the planetary shaft 27 and an inner conical portion on the sun pinion 28.

[0074] The figures also show that the sun pinion 28 is fixed to the corresponding planetary shaft 27 either by means of a screw 30 or a nut 31. In a variant of the planetary gear mechanism 1, the sun pinion 28 is fixed to the planetary shaft 27 by means of a screw 30, and it may also be appropriate to press the corresponding sun pinion 28 onto the planetary shaft 27 using a pressing tool.

[0075] In a variant of the planetary gear mechanism 1, the sun pinion 28 is fixed to the corresponding planetary shaft 27 by means of a nut 31, and by tightening the nut 31, the sun pinion 28 can be pressed onto the cone 29 of the planetary shaft 27. Here, the nut 31 is screwed onto the threaded section 32 of the planetary shaft 27.

[0076] Reference numerals list

[0077] 1Planetary gear transmission mechanism

[0078] 2 Shell

[0079] 3Sun gear

[0080] 4 Planet carrier

[0081] 5Planetary gear

[0082] 6 gear ring

[0083] 7 4 Installation direction

[0084] 8 Rear, distal bearing seat on 4

[0085] 9 4 Insertion end

[0086] 10 Planet carrier receptacle in 2 for 4

[0087] 11 Insert opening

[0088] 12 4 front side, proximal bearing seat

[0089] 13 4 The end facing away from the insertion end

[0090] 14 Planetary gear housing

[0091] 15 Insert opening

[0092] 165 installation direction

[0093] 17 side opening

[0094] 185 ring gear meshing part

[0095] 195 sun gear meshing part

[0096] 20 on 5 bearing seat

[0097] 21 on 5 bearing seat

[0098] 22 Insertion end

[0099] 23Swivel bearing

[0100] Outer ring of 2423

[0101] 25 is in the bearing seat of 14, adjacent to 15

[0102] 26 axial bearing elements

[0103] 27 Planetary axis

[0104] 28 Sun pinion

[0105] 29 tapered connection

[0106] 30 screws

[0107] 31 Nut

[0108] 32 thread segments

Claims

1. A planetary gear mechanism (1), comprising a housing (2), a sun gear (3), a planet carrier (4), at least one planetary gear (5) and a ring gear (6), wherein: The planet carrier (4) is rotatably supported in the housing (2), the housing (2) defines an installation direction (7) for installing the planet carrier (4), and the planet carrier (4) has a bearing seat (8) on its outer side, the bearing seat is arranged adjacent to the insertion end (9) of the planet carrier (4) and is arranged behind the ring gear (6) along the installation direction (7) in the use position of the planet carrier (4), and the outer diameter of the bearing seat is smaller than the inner diameter of the ring gear (6), in particular the tooth tip circle diameter, It is characterized in that The bearing seat (12) of the planet carrier (4) is arranged in the installation direction (7) and in the use position of the planet carrier (4) before the ring gear (6) and / or adjacent to the end (13) of the planet carrier (4) facing away from the insertion end (9), the diameter of the bearing seat is larger than the inner diameter of the ring gear (6), in particular larger than the tooth top circle diameter of the ring gear and / or larger than the diameter of the bearing seat (8) of the planet carrier (4) adjacent to the insertion end (9), and the at least one planetary gear (5) is constructed as a multi-stage planetary gear, having two bearing seats (20, 21) and at least two meshing portions (18, 19), namely, with the sun gear ( 3) a meshing sun gear meshing portion (19) and a meshing ring gear meshing portion (18) meshing with the ring gear (6), the ring gear meshing portion (18) of the planetary gear (5) being arranged between two bearing seats (20, 21) of the planetary gear (5), one bearing seat (20) of the planetary gear (5) being arranged between an insertion end (22) of the planetary gear (5) and the ring gear meshing portion (18), the outer diameter of the bearing seat (20) being smaller than the outer diameter of the ring gear meshing portion (18), and the other bearing seat (21) of the planetary gear (5) being arranged between the ring gear meshing portion (18) and the sun gear meshing portion (19) of the planetary gear (5).

2. The planetary gear transmission mechanism (1) according to claim 1, wherein: The housing (2) has a planet carrier receptacle (10) with an insertion opening (11) for the planet carrier (4), the insertion opening defining an installation direction (7) of the planet carrier (4), and / or the ring gear (6) is arranged or formed in a rotationally fixed manner inside and / or on the housing (2), and / or the planet carrier (4) is constructed in one piece.

3. The planetary gear transmission mechanism (1) according to claim 1 or 2, wherein: The planet carrier (4) has on its outer side two bearing seats (8, 12) which are axially spaced apart from one another with respect to its axis of rotation (R) and between which the ring gear (6) is arranged when the planet carrier (4) is in the operating position.

4. The planetary gear mechanism (1) according to any one of the preceding claims, wherein: The planet carrier (4) has a shaft, in particular an output shaft, or is designed as a shaft, in particular an output shaft.

5. The planetary gear mechanism (1) according to any one of the preceding claims, wherein: The at least one planet gear (5) is rotatably mounted in the planet carrier (4) and meshes with the sun gear (3) and with the ring gear (6).

6. A planetary gear mechanism (1) according to any one of the preceding claims, wherein: The planet carrier (4) has at least one planet gear receptacle (14) for the at least one planet gear (5).

7. A planetary gear mechanism (1) according to the preceding claim, wherein: The planetary gear receiving portion (14) has an insertion opening (15), through which the at least one planetary gear (5) can be inserted into the planetary gear receiving portion (14) along an installation direction (16) into the planetary gear receiving portion (14) into a use position of the planetary gear. Preferably, the installation direction (7) of the planet carrier (4) into the housing (2) is consistent with the installation direction (16) of the at least one planetary gear (5) into the planetary gear receiving portion (14), and / or the planetary gear receiving portion (14) is constructed as a blind hole or a stepped hole.

8. The planetary gear mechanism (1) according to any one of the two preceding claims, wherein: The planet carrier (4) has at least one lateral opening (17) which leads into a planet gear receptacle (14) of the planet carrier (4).

9. The planetary gear mechanism (1) according to any one of the preceding claims, wherein: The two toothings (18, 19) of the planetary gear (5) are different, preferably have different tip circle diameters and / or pitch circle diameters and / or pitch circle diameters, and / or the two toothings (18, 19) are axially spaced apart from each other with respect to the rotation axis of the planetary gear (5).

10. The planetary gear mechanism (1) according to any one of claims 6 to 9, wherein: The planetary gear receptacle (14) has a lateral opening (17) oriented transversely to the axis of rotation (R) of the planet carrier (4) for a ring gear toothing (18) of the planetary gear (5).

11. The planetary gear transmission mechanism (1) according to any one of claims 1 to 10, wherein: A rotary bearing (23), in particular a radial bearing, is arranged on a bearing seat (20) arranged between an insertion end (22) of the planetary gear (5) and the toothed ring meshing portion (18), wherein the outer diameter of the rotary bearing is smaller than the outer diameter of the toothed ring meshing portion (18) of the at least one planetary gear (5).

12. The planetary gear transmission (1) according to any one of claims 6 to 11, wherein: The at least one planetary gear receptacle (14) has, adjacent to its insertion opening (15), a bearing seat (25) for the outer side, in particular the outer ring (24), of a rotary bearing (23) of the at least one planetary gear (5), the bearing seat having an inner diameter at least as large as the outer diameter of the toothed ring meshing portion (18) of the at least one planetary gear (5), and / or the outer diameter of the rotary bearing (23) arranged on the bearing seat (25) is at least as large as the outer diameter of the toothed ring meshing portion (18) of the at least one planetary gear (5).

13. The planetary gear transmission (1) according to any one of claims 1 to 12, wherein: The ring gear toothing (18) of the at least one planetary gear (5) is a helical toothing and / or the sun gear toothing (19) of the at least one planetary gear (5) is a helical toothing.

14. The planetary gear mechanism (1) according to any one of the preceding claims, wherein: The helical meshing between the at least one planetary gear (5) and the sun gear (3) of the planetary gear mechanism (1) and the helical meshing between the at least one planetary gear (5) and the ring gear (6) of the planetary gear mechanism (1) are coordinated with each other so that the value of the effective axial force generated by the axial force caused by each of the helical meshing parts (18, 19) during the operation of the planetary gear mechanism (1) is less than 10% of the value of the axial force caused by each of the helical meshing parts (18, 19), preferably 10% of the value of the minimum axial force, or the axial forces caused by each of the helical meshing parts (18, 19) during the operation of the planetary gear mechanism (1) cancel each other out.

15. The planetary gear mechanism (1) according to the preceding claim, wherein: The ratio of the inclination angles of the oblique toothing portions (18, 19) corresponds to the ratio of the pitch circle diameters of the oblique toothing portions (18, 19).

16. The planetary gear mechanism (1) according to any one of the preceding claims, wherein: The at least one planetary gear (5) has a planetary shaft (27), and the sun gear toothing (19) is formed on a sun pinion (28) arranged on the planetary shaft (27).

17. A planetary gear mechanism (1) according to the preceding claim, wherein: An adhesive is arranged between the planetary shaft (27) and the sun pinion (28) and / or a conical connection portion (29) is formed, and the sun pinion (28) is connected to the planetary shaft (27) via the conical connection portion; and / or the sun pinion (28) is fixed to the planetary shaft (27) by means of a screw (30) and / or by means of a nut (31).

18. The planetary gear mechanism (1) according to any one of the preceding claims, wherein: The planetary gear mechanism (1) has at least one axial bearing element (26), in particular an axial sliding disk, which is assigned to at least one rotary bearing (23) for rotatably supporting the at least one planetary gear (5) and is provided for absorbing axial forces, preferably each rotary bearing (23) of the planetary gear (5) is respectively assigned at least one axial bearing element (6).

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