Gearbox device

Abstract

A transmission device is provided that can improve the lubrication of a bearing in a planetary gear. The present disclosure includes the transmission device, which includes a sun gear, a ring gear, planetary gears, bearings through which shafts of the plate gears are inserted, a differential cage including bearing holders holding the respective bearings, a differential mechanism disposed within the differential cage, and a transmission case rotatably supporting the differential cage. Each bearing holder includes a cylindrical member holding a corresponding one of the bearings and a pocket recessed from a radially inner side to a radially outer side to have an internal space overlapping with the corresponding one of the bearings. The transmission case includes a projection disposed to overlap with the pockets from the radially inner side of the sun gear and axially projecting toward the bearings.

Description

TECHNICAL FIELD

[0001] The present disclosure relates to a transmission device. TECHNICAL BACKGROUND

[0002] In a transmission device having a differential mechanism, a configuration is known in which lubricating oil is supplied to a bearing from a passage provided inside a gear shaft (see Patent Document 1). CONVENTIONAL DOCUMENTSPATENT DOCUMENTS

[0003] Patent document 1: WO2011 / 077869 SUMMARY OF THE INVENTION PROBLEMS TO BE SOLVED BY THE INVENTION

[0004] In the gear device described above, it is possible to supply lubricating oil to a bearing in a gear without increasing the number of components. However, there is room for improvement in the lubrication of the bearing (i.e., an oil supply volume).

[0005] In one aspect of the present disclosure, it is preferable to provide a transmission device that can increase the lubrication of a bearing in a planetary gear. MEANS TO SOLVE THE PROBLEMS

[0006] One aspect of the present disclosure is a transmission device comprising: a sun gear; a ring gear arranged concentrically with the sun gear; planetary gears meshing with the sun gear and with the ring gear; bearings through each of which a shaft of a corresponding one of the planetary gears is inserted; a differential cage including bearing holders each holding a corresponding one of the bearings; a differential mechanism arranged within the differential cage; a first output shaft and a second output shaft connected to the differential mechanism; and a transmission case rotatably supporting the differential cage.

[0007] The bearing holders each include a cylindrical member that holds a corresponding one of the bearings, and a pocket that is recessed from a radially inner side to a radially outer side of the sun gear to have an internal space, and that overlaps with the corresponding one of the bearings in an axial direction of the sun gear. The gear case includes a projection that is arranged to overlap with the pocket of each bearing holder from the radially inner side of the sun gear and that projects toward the bearings in the axial direction of the sun gear.

[0008] In this configuration, oil in the gear housing flows along the outer surface of the boss by gravity or centrifugal force and is stored in the pocket. This allows the oil stored in the pocket to be supplied to the bearings. As a result, the oil supply volume to the planetary gear bearings increases, thereby improving lubrication.

[0009] In one aspect of the present disclosure, the transmission case may further include a tapered surface that slopes toward the protrusion from a position farther from each bearing in the axial direction of the sun gear than the protrusion and located on an inner side relative to the protrusion in a radial direction of the sun gear. In this configuration, the tapered surface can guide the oil in the transmission case into the protrusion. As a result, the oil storage efficiency in the pocket increases.

[0010] In one aspect of the present disclosure, the transmission case may further include a recess formed in a rear side of the protrusion on the radially outer side of the sun gear and recessed toward the radially inner side of the sun gear. This configuration prevents oil from being led out of the pocket along the rear side of the protrusion. As a result, oil can easily drop from the protrusion to the pocket, thereby increasing the oil storage efficiency in the pocket.

[0011] In one aspect of the present disclosure, the cylindrical part and the pocket may be integrated with each other. In this configuration, it is possible to perform a hole forming process in the cylindrical part and a pocket forming process simultaneously. Accordingly, it is possible to form the pocket with higher strength in the differential cage while preventing an increase in the number of manufacturing processes. BRIEF DESCRIPTION OF THE DRAWINGS Fig. 1 is a schematic sectional view of a transmission device in one embodiment. Fig. 2 is a partially enlarged schematic sectional view of the transmission device of Fig. 1. Fig. 3 is a schematic perspective view of planetary gears and a differential cage in the transmission device of Fig. 1. Fig. 4 is a schematic perspective view of a portion of the differential cage of Fig. 3. Fig. 5 is a schematic rear view of a portion of the differential cage of Fig. 3. Fig. 6 is a schematic perspective view of a portion of a gear housing in the transmission device of Fig. 1. Fig. 7 is a schematic cross-sectional view taken along line VII-VII of Fig. 1. Fig. 8 is a partially enlarged view of Fig. 2. Fig. 9A is a schematic diagram showing a state in which the differential cage relatively rotates in a first direction. Fig. 9B is a schematic diagram showing a state in which the differential cage rotates relatively in a second direction. Fig. 10 is a schematic front view of a portion of the differential cage of Fig. 3. EXPLANATION OF THE REFERENCE FIGURES

[0012] 1... transmission device, 2... sun gear, 3... ring gear, 4... planetary gears, 5... planetary gear bearings, 6... differential cage, 7... differential mechanism, 8A... first output shaft, 8B... second output shaft, 9... transmission case, 10... motor shaft, 22... enlarged diameter part, 23... connecting holes, 61... case, 62... carrier, 63... bearing holder, 64... first sleeve, 65A to 65D... oil discharge grooves, 66... ​​second sleeve, 67A to 67D... oil introduction grooves, 71 and 72... pinion gears, 73... pinion shaft, 74 and 75... side gears, 631... cylindrical parts, 632... legs, 633... pockets, 661 and 662... extension, 911...projection, 912...inclined surface, 913...recess. MODE FOR CARRYING OUT THE INVENTION

[0013] Embodiments to which the present disclosure is applied will now be described with reference to the drawings. [1. First execution][1-1. Configuration]

[0014] One in Fig. The transmission device 1 shown in Fig. 1 is a device mounted in an automobile and transmitting a driving force from a driving source of the automobile to its wheels.

[0015] The transmission device 1 comprises a sun gear 2, a ring gear 3, planetary gears 4, planetary gear bearings 5, a differential cage 6, a differential mechanism 7, a first output shaft 8A, a second output shaft 8B, a transmission housing 9 and a motor shaft 10.

[0016] In the present embodiment, an axial direction of the sun gear 2 is an X-axis, a vertical direction of the sun gear 2 is a Z-axis, and a direction perpendicular to both the X-axis and the Z-axis is a Y-axis. <motorwelle>

[0017] The motor shaft 10 is drivingly connected to a motor (not shown) and is axially rotated by a driving force of the motor. <sonnenrad>

[0018] The sun gear 2, together with the ring gear 3 and the planetary gears 4, forms a planetary gear mechanism (i.e., a gear reduction mechanism). The sun gear 2 is arranged outside the differential cage 6 and inside the transmission case 9.

[0019] The sun gear 2 is drivingly connected to the motor shaft 10 and is axially rotated by the driving force of the motor. An axial rotation center of the sun gear 2 is equal to an axial rotation center of the first output shaft 8A and the second output shaft 8B.

[0020] The first output shaft 8A and the first sleeve 64 of the differential cage 6 are inserted through the sun gear 2. As shown in Fig. 2, the sun gear 2 includes a toothed part 21, a diameter-enlarged part 22, connecting holes 23 and a connecting part 24. Fig. 2 illustrates a state in which the planetary gear 4 rotates from an upper position to Fig. 1 is moved downwards.

[0021] The gear part 21 is an external gear, which is cylindrical and meshes with the planetary gears 4. The first sleeve 64 of the differential cage 6 is inserted into the gear part 21 such that a small radial gap is provided. In other words, the sun gear 2 overlaps with the first sleeve 64 in the radial direction of the sun gear 2. An inner diameter of the gear part 21 is larger than an outer diameter of the first sleeve 64.

[0022] The diameter-enlarged part 22 is a tubular portion connected to the gear part 21. The diameter-enlarged part 22 is connected to one end of the gear part 21 opposite the differential mechanism 7. An inner diameter D1 of the diameter-enlarged part 22 is larger than an inner diameter D2 of an outer end 64A of the first sleeve 64. The first sleeve 64 is not fitted into the diameter-enlarged part 22. The inner diameter D1 of the diameter-enlarged part 22 is larger than an outer diameter of a portion of the motor shaft 10 fitted into the connecting part 24.

[0023] The communication holes 23 each allow an opening in the outer end 64A of the first sleeve 64 to communicate with a space outside the sun gear 2. The communication holes 23 are spaced apart from each other in the circumferential direction of the diameter-enlarged portion 22. In the present embodiment, four communication holes 23 are spaced 90° apart from each other in the circumferential direction of the sun gear 2. However, the number of communication holes 23 is not limited to four.

[0024] The connecting holes 23 allow lubricating oil discharged from the first sleeve 64 to be discharged by gravity or centrifugal force into a planetary gear accommodating space located between the differential cage 6 and the transmission case 9. The sun gear 2 serves as a gear constituting a planetary gear mechanism in the present embodiment, and as a connecting member defining a circulation path for the lubricating oil.

[0025] The connecting part 24 is a tubular section that adjoins the enlarged diameter part 22. The connecting part 24 is connected to an end of the enlarged diameter part 22 opposite the toothed part 21. As shown in Fig. As shown in Figure 1, an end portion of the motor shaft 10 is longitudinally splined with the connecting part 24. An inner diameter of the connecting part 24 is smaller than that of the enlarged diameter part 22. <ringrad>

[0026] The ring gear 3 is arranged concentrically with the sun gear 2. The ring gear 3 is attached to an inner surface of the gear housing 9 and does not rotate relative to the gear housing 9. The ring gear 3 has internal teeth with which the planetary gears 4 mesh. <planetenrad>

[0027] The planetary gears 4 mesh with the sun gear 2 and the ring gear 3, respectively. The planetary gears 4 revolve around the center of the rotational axis of the sun gear 2. In the present embodiment, three planetary gears 4 are arranged, but the number of planetary gears 4 is not limited to three.

[0028] The rotational center of each of the planetary gears 4 is parallel to the rotational center of the sun gear 2 (i.e., the X-axis). The planetary gears 4 are held by the differential cage 6. Each of the planetary gears 4 includes a first gear part 41, a second gear part 42, a first shaft 43, and a second shaft 44.

[0029] The first gear part 41 is an external gear that meshes with the sun gear 2. The second gear part 42 is an external gear that meshes with the ring gear 3. The outer diameter of the second gear part 42 is smaller than that of the first gear part 41. The second gear part 42 is arranged closer to an opening end 9A of the gear housing 9 than the first gear part 41.

[0030] The first shaft 43 constitutes an end portion of each planetary gear 4 opposite the opening end 9A. The first shaft 43 is supported by a carrier 62 of the differential cage 6. Specifically, the first shaft 43 is inserted through a ball bearing 5A supported by the carrier 62.

[0031] The second shaft 44 represents an end portion of each planetary gear 4 closer to the opening end 9A. The second shaft 44 is supported by the differential cage 6. Specifically, the second shaft 44 is inserted through a corresponding planetary gear bearing 5, which is supported by a bearing retainer 63 of the differential cage 6. <planetenradlager>

[0032] Through each of the planetary gear bearings 5, a corresponding one of the second shafts 44 of the planetary gears 4 is inserted. The planetary gear bearings 5 ​​are not subject to any particular limitation as long as the bearings can rotatably support the planetary gears 4, but are preferably known needle bearings, for example. <Differentialkäfig>

[0033] The differential cage 6 rotatably supports the planetary gears 4 and houses the differential mechanism 7. The differential cage 6 is mounted on the transmission housing 9. As the planetary gears 4 rotate, the differential cage 6 rotates around the center of rotation of the sun gear 2.

[0034] As in Fig. 2, the differential cage 6 includes a housing 61, the carrier 62, the bearing holders 63, the first sleeve 64, oil discharge grooves 65A, 65B, 65C, 65D, a second sleeve 66, and oil introduction grooves 67A, 67B, 67C, 67D.

[0035] Fig. 2 shows only the first oil discharge groove 65A and the third oil discharge groove 65C, and the second oil discharge groove 65B and the fourth oil discharge groove 65D are in Fig. 4. Similarly, Fig. 2 only the first oil introduction groove 67A and the third oil introduction groove 67C, and the second oil introduction groove 67B and the fourth oil introduction groove 67D are in Fig. 5 shown. <Gehäuse>

[0036] The housing 61 is a main body of the differential cage 6 and accommodates the differential mechanism 7. As shown in Fig. 1, the housing 61 is formed by joining a first part 61A and a second part 61B in a direction parallel to the X-axis. <Träger>

[0037] The bracket 62 is arranged such that the bracket 62 covers the housing 61 from a position opposite to the opening end 9A of the gear case 9 (ie, a position closer to the motor shaft 10). The bracket 62 is fixed to the housing 61 by a fastening member, for example, a bolt. <lagerhalter>

[0038] The bearing holders 63 each hold one of the planetary gear bearings 5. As in Fig. 3, the bearing holders 63 are arranged on an outer peripheral surface of the housing 61.

[0039] The bearing holders 63 are arranged at a distance from each other in the circumferential direction of the housing 61 (i.e., in the circumferential direction of the sun gear 2). The bearing holders 63 each include a cylindrical part 631, a leg 632, and a pocket 633.

[0040] Each of the cylindrical parts 631 holds one of the planetary gear bearings 5. Specifically, the planetary gear bearings 5 ​​are axially inserted into the cylindrical parts 631. The leg 632 extends radially outward from the outer peripheral surface of the housing 61 and connects the housing 61 and the cylindrical part 631.

[0041] The pocket 633 of each bearing holder 63 protrudes from one end of the cylindrical portion 631 opposite the corresponding planetary gear 4. The pocket 633 is recessed from a radially inner side of the sun gear 2 to a radially outer side of the sun gear 2 (i.e., in the direction away from the rotational axis center of the sun gear 2) to have an internal space. Also, each pocket 633 overlaps with the corresponding planetary gear bearing 5 in the axial direction of the sun gear 2.

[0042] In other words, each pocket 633 includes a bottom wall intersecting the radial direction of the sun gear 2, two side walls intersecting the circumferential direction of the sun gear 2, and a front wall intersecting the X-axis. The front wall in each pocket 633 covers a portion of the corresponding planetary gear bearing 5 and a portion of the corresponding cylindrical part 631 in a direction parallel to the X-axis. The internal space in each pocket 633 allows fluid to enter from the radially inner side of the sun gear 2. The internal space in each pocket 633 communicates with a cavity in the cylindrical part 631.

[0043] The bearing retainers 63 are integrated with the housing 61 and serve as a portion of the first part 61A. The cylindrical part 631 and the pocket 633 in each pocket 633 are integral with each other. Each pocket 633 is formed simultaneously with a hole in the corresponding cylindrical part 631 when the first part 61A is machined. This makes it relatively easy to form the pockets 633, which are difficult to form by casting due to their small thickness. <Erste Hülse>

[0044] The Fig. The first sleeve 64 shown in Fig. 1 is a tubular portion connected to the housing 61 and through which the first output shaft 8A is inserted.

[0045] The first sleeve 64 extends from the housing 61 to the motor shaft 10 along the X-axis. The first sleeve 64 allows an interior of the housing 61 and an exterior of the housing 61 (in particular, an interior in the sun gear 2) to communicate with each other.

[0046] A portion of the first sleeve 64 is inserted into the sun gear 2. A center axis of the first sleeve 64 coincides with the rotational axis center of the sun gear 2. An inner diameter of the first sleeve 64 is smaller than a maximum inner diameter of the housing 61. <Oil drainage groove>

[0047] As in Fig. 4, the first oil discharge groove 65A, the second oil discharge groove 65B, the third oil discharge groove 65C, and the fourth oil discharge groove 65D are provided on an inner peripheral surface of the first sleeve 64 and extend from the outer end 64A of the first sleeve 64 into the housing 61.

[0048] The first oil discharge groove 65A, the second oil discharge groove 65B, the third oil discharge groove 65C, and the fourth oil discharge groove 65D are spaced apart from each other in the circumferential direction of the first sleeve 64. Details of the shapes of the oil discharge grooves 65A to 65D are described below. <zweite Hülse>

[0049] The Fig. The second sleeve 66 shown in Fig. 1 is a tubular portion connected to the housing 61 and through which the second output shaft 8B is inserted.

[0050] The second sleeve 66 extends from the housing 61 to the opening end 9A of the gear case 9 along the X-axis. The second sleeve 66 allows the interior of the housing 61 and the exterior of the housing 61 (specifically, the interior of the gear case 9) to communicate with each other.

[0051] The second sleeve 66 is inserted into a differential cage bearing 93. A center axis of the second sleeve 66 coincides with the rotational axis center of the sun gear 2. An inner diameter of the second sleeve 66 is smaller than the maximum inner diameter of the housing 61.

[0052] As in Fig. 3, the second sleeve 66 includes a first extension 661 and a second extension 662. The first extension 661 and the second extension 662 each protrude relative to other positions on an outer end 66A of the second sleeve 66 in the axial direction of the second side gear 75 (ie, along the X-axis).

[0053] One end of the first projection 661 in the circumferential direction of the second sleeve 66 is located at a position adjacent to the first oil introduction groove 67A, and the other end is located at a position adjacent to the third oil introduction groove 67C.

[0054] In other words, the first projection 661 is located in a region between one end of the first oil introduction groove 67A and one end of the third oil introduction groove 67C, at the outer end 66A of the second sleeve 66. The first projection 661 constitutes a guide for guiding oil into the first oil introduction groove 67A and the third oil introduction groove 67C.

[0055] The second projection 662 has the shape of the first projection 661, which is rotated 180° around the rotational axis center of the differential cage 6. One end of the second projection 662 in the circumferential direction of the second sleeve 66 is located in a position adjacent to the second oil introduction groove 67B (see Fig. 5), and the other end is in a position adjacent to the fourth oil introduction groove 67D (see Fig. 5).

[0056] In other words, the second projection 662 is located in a region between one end of the second oil introduction groove 67B and one end of the fourth oil introduction groove 67D, at the outer end 66A of the second sleeve 66. The second projection 662 constitutes a guide for guiding oil into the second oil introduction groove 67B and the fourth oil introduction groove 67D. <Oil introduction groove>

[0057] As in Fig. 5, the first oil introduction groove 67A, the second oil introduction groove 67B, the third oil introduction groove 67C, and the fourth oil introduction groove 67D are provided on an inner peripheral surface of the second sleeve 66 and extend from the outer end 66A of the second sleeve 66 into the housing 61.

[0058] The first oil introduction groove 67A, the second oil introduction groove 67B, the third oil introduction groove 67C, and the fourth oil introduction groove 67D are spaced apart from each other in the circumferential direction of the second sleeve 66. Details of the shapes of the oil introduction grooves 67A to 67D will be described below. <differentialmechanismus>

[0059] The Fig. The differential mechanism 7 shown in Fig. 1 is a known mechanism that distributes and transmits the rotation of the differential cage 6 to the first output shaft 8A and the second output shaft 8B while the first output shaft 8A and the second output shaft 8B rotate at different speeds.

[0060] The differential mechanism 7 includes a first pinion 71, a second pinion 72 (see Fig. 5), a pinion shaft 73, a first side gear 74, and the second side gear 75. The differential mechanism 7 is arranged within the differential cage 6. Specifically, the first pinion 71, the second pinion 72, the pinion shaft 73, the first side gear 74, and the second side gear 75 are housed in the housing 61 of the differential cage 6. <Ritzel und Ritzelwelle>

[0061] As in Fig. 5, each of the first pinion 71 and the second pinion 72 is a bevel gear whose rotational axis center is perpendicular to the rotational axis center of the sun gear 2 (i.e., X-axis).

[0062] The center of rotation of the first pinion 71 and the center of rotation of the second pinion 72 coincide. The first pinion 71 and the second pinion 72 are arranged opposite each other. The first pinion 71 and the second pinion 72 have the same shape and are mirror images of each other.

[0063] The pinion shaft 73 supports the first pinion 71 and the second pinion 72 for individual rotation. A central axis (i.e., longitudinal direction) of the pinion shaft 73 is perpendicular to the X-axis. The pinion shaft 73 is fixed to the housing 61 and does not rotate with respect to the differential cage 6. In other words, the pinion shaft 73 rotates together with the housing 61 around the rotational axis center of the sun gear 2. <seitenrad>

[0064] As in Fig. 1, each of the first side gear 74 and the second side gear 75 is a bevel gear whose rotational axis center coincides with the rotational axis center of the sun gear 2 (ie, the X-axis).

[0065] The center of rotation of the first side gear 74 and the center of rotation of the second side gear 75 coincide. The first side gear 74 and the second side gear 75 are arranged opposite each other.

[0066] The first side gear 74 is positioned closer to the motor shaft 10 than the second side gear 75 along the X-axis. The first side gear 74 and the second side gear 75 have the same shape and are mirror images of each other.

[0067] The first side gear 74 and the second side gear 75 are each rotatably supported by the housing 61. The first side gear 74 meshes with the first pinion gear 71 and the second pinion gear 72 and is connected to the first output shaft 8A. The second side gear 75 meshes with the first pinion gear 71 and the second pinion gear 72 and is connected to the second output shaft 8B.

[0068] The first side gear 74 and the second side gear 75 rotate together with the differential cage 6 and also rotate simultaneously relative to the differential cage 6 by rotation transmitted from the first pinion 71 and the second pinion 72. <ausgangswelle>

[0069] The first output shaft 8A and the second output shaft 8B are each longitudinally toothed with the first side gear 74 and the second side gear 75, respectively.

[0070] The first output shaft 8A and the second output shaft 8B each output rotation to a wheel of an automobile. The first output shaft 8A and the second output shaft 8B rotate according to a rotation direction of the engine shaft 10 (ie, the rotation direction of the differential cage 6) while rotating at different speeds through the differential mechanism 7 connected thereto. <Getriebegehäuse>

[0071] The gear housing 9 accommodates the sun gear 2, the ring gear 3 and the planet gears 4 and rotatably supports the differential cage 6.

[0072] The transmission case 9 includes a first body 91, a second body 92, the differential cage bearing 93, and an oil guide 94. The first body 91 and the second body 92 are connected to each other to thereby form the planetary gear housing space that houses the gears and the differential cage 6. A motor (not shown) serving as a drive source is arranged within the second body 92.

[0073] The first body 91 has an opening end 9A through which the second output shaft 8B is inserted. Lubricating oil for lubricating the gears and shafts is stored in the planetary gear housing 9. The planetary gear housing is sealed with a sealing element or the like.

[0074] The differential cage bearing 93 rotatably supports the differential cage 6. Specifically, the second sleeve 66 of the differential cage 6 is inserted through the differential cage bearing 93. The differential cage bearing 93 is held by the first body 91. The differential cage bearing 93 is a shielded bearing through which the lubricating oil supplied from the oil guide 94 can flow.

[0075] The Fig. 6 and Fig. The oil guide 94 shown in Figure 7 is a flow channel having a groove-like shape and arranged in the planetary gear accommodation space. An inlet 941 of the oil guide 94 is arranged above the rotational axis center of the sun gear 2 and on a radially outer side relative to an orbit of the planetary gears 4. The inlet 941 is arranged at a position overlapping with the first gear parts 41 of the planetary gears 4 in the radial direction of the sun gear 2.

[0076] When an automobile moves forward, Fig. 7, the sun gear 2 and the differential cage 6 rotate clockwise, and each planetary gear 4 rotates clockwise while rotating counterclockwise around its own axis. The direction of rotation of each component when the car is moving backward is opposite to the direction in which the car is moving forward.

[0077] The lubricating oil stored in a lower portion of the planetary gear receiving space is scooped up by the rotating planetary gear 4 and then drops into the inlet 941. As a result, the lubricating oil can be fed into the oil guide 94.

[0078] An outlet 942 of the oil guide 94 is arranged below the inlet 941 and near the upper end of the outer end 66A of the second sleeve 66 of the differential cage 6 (see Fig. 1). The lubricating oil supplied from the inlet 941 to the oil guide 94 flows downward within the oil guide 94 and is guided near the second sleeve 66.

[0079] As in Fig. 2 with an arrow, the lubricating oil that has been supplied to the vicinity of the second sleeve 66 flows through the second sleeve 66 and is supplied to the interior of the housing 61. This allows the differential mechanism 7 to be lubricated. The lubricating oil inside the differential mechanism 7 passes through the first sleeve 64 and is discharged into the interior of the sun gear 2 (ie, a connecting member).

[0080] The lubricating oil discharged into the interior of the sun gear 2 is discharged from the connecting holes 23 into the planetary gear receiving space and then stored again in the lower part of the planetary gear receiving space. The lubricating oil stored in the planetary gear receiving space is supplied by the planetary gears 4 to the oil guide 94, as described above. The lubricating oil is thus circulated in the gear case 9.

[0081] A part of the lubricating oil that has been fed to the vicinity of the second sleeve 66 is not supplied to the housing 61, but passes through the shield of the differential cage bearing 93, and then flows downward under the second sleeve 66 and the housing 61 and is stored in the lower part of the planetary gear receiving space. <Zufuhr von Schmieröl zum Planetenradlager>

[0082] As in Fig. As shown in Figure 8, a portion of the lubricating oil is supplied to each planetary gear bearing 5 along an inner peripheral surface of the first body 91 of the gear case 9. The flow of the lubricating oil is described in detail below.

[0083] The first body 91 of the gear housing 9 includes a projection 911, a slant surface 912, and a recess 913. The projection 911 is arranged to overlap with the pocket 633 of each bearing holder 63 from the radially inner side of the sun gear 2 and to project toward the planetary gear bearings 5 ​​in the axial direction of the sun gear 2.

[0084] In other words, the protrusion 911 is a portion that protrudes from an inner surface of the first body 91 and covers a portion of an opening of each pocket 633. The protrusion 911 is arranged closer to the radially inner side of the sun gear 2 than a rotation axis L of each planetary gear 4 (ie, a center axis of each planetary gear bearing 5).

[0085] In the present embodiment, when viewed along the axial direction of the sun gear 2, the protrusion 911 is formed in an annular shape. In other words, the protrusion 911 is provided in the entire circumferential direction of the first body 91. However, the protrusion 911 only needs to be provided at the lower portion of the first body 91 (for example, a portion below the rotational axis center of the sun gear 2).

[0086] The inclined surface 912 is inclined toward the projection 911 from a position that is farther from the planetary gear bearings 5 ​​than the projection 911 in the axial direction of the sun gear 2 and that is located on an inner side relative to the projection 911 in the radial direction of the sun gear 2.

[0087] In other words, the inclined surface 912 is formed from a portion of the inner surface of the first body 91 extending from the projection 911 toward the opening end 9A. The inclined surface 912 may be formed from a flat surface or may be curved or bent.

[0088] The recess 913 is a portion that is located in a back surface of the projection 911 on the radially outer side of the sun gear 2 (ie, a surface opposite to the inclined surface 912) and is also recessed toward the radially inner side of the sun gear 2. The recess 913 is a groove that extends along the circumferential direction of the sun gear 2. The recess 913 may be provided in the entire circumferential direction of the first body 91 or may be provided only at the lower portion of the first body 91 (for example, at a portion where the lubricating oil entering the recess 913 flows downward).

[0089] As in Fig. 8 with an arrow, the lubricating oil that passes through the shield of the differential cage bearing 93 via the oil guide 94 and flows down under the second sleeve 66, or the lubricating oil that does not pass through the oil guide 94 but directly reaches the inclined surface 912 because it is splashed in the transmission case 9, moves along the inclined surface 912 to the projection 911. The lubricating oil that reaches the projection 911 flows down from its tip end and is collected in the pocket 633.

[0090] The lubricating oil that has moved from the tip end of the projection 911 to the back of the projection 911 is removed from the back of the projection 911 through the recess 913. Accordingly, the lubricating oil is prevented from flowing along the inner surface of the first body 91 below the pocket 633. <Formen von Ölzufuhrnut und der Ölabführnut>

[0091] As in Fig. 5, the oil introduction grooves 67A to 67D each reach the interior of the housing 61 at a radially outer side of the second side gear 75 relative to the second side gear 75, as viewed along an axial direction of the second side gear 75 (i.e., a direction parallel to the X-axis). The exit ends of the oil introduction grooves 67A to 67D each have portions that do not overlap with the rotating second side gear 75.

[0092] Further, the oil introduction grooves 67A to 67D are each arranged such that the oil introduction grooves 67A to 67D do not overlap with either the first pinion 71 or the second pinion 72 when viewed along the axial direction of the second side gear 75.

[0093] The first oil introduction groove 67A and the second oil introduction groove 67B are arranged side by side between the first pinion 71 and the second pinion 72 in the circumferential direction of the second side gear 75. The shape of the second oil introduction groove 67B is symmetrical with that of the first oil introduction groove 67A with respect to a virtual plane perpendicular to the Y-axis.

[0094] The shape of each of the third oil introduction groove 67C and the fourth oil introduction groove 67D is symmetrical with the shape of the first oil introduction groove 67A or the second oil introduction groove 67B with respect to a virtual plane orthogonal to the Z axis. That is, the third oil introduction groove 67C and the fourth oil introduction groove 67D are arranged opposite to the first oil introduction groove 67A and the second oil introduction groove 67B across the pinion shaft 73 and are arranged side by side between the first pinion 71 and the second pinion 72 in the circumferential direction of the second side gear 75.

[0095] The oil introduction grooves 67A to 67D each extend linearly. In other words, a line connecting the center points of each of the oil introduction grooves 67A to 67D in the width direction thereof is a straight line. Furthermore, the width of each of the oil introduction grooves 67A to 67D increases toward the housing 61. In other words, the width of each of the oil introduction grooves 67A to 67D is minimum at the outer end 66A of the second sleeve 66 and maximum inside the housing 61.

[0096] As in Fig. 9A and Fig. 9B, the first oil introduction groove 67A and the second oil introduction groove 67B are arranged in the circumferential direction of the second side gear 75 (ie, in the circumferential direction of the second sleeve 66) between the first extension 661 and the second extension 662 of the second sleeve 66, and also the third oil introduction groove 67C and the fourth oil introduction groove 67D are arranged in the other area between the first oil introduction groove 67A and the second oil introduction groove 67B.

[0097] Specifically, the ends of each of the first oil introduction groove 67A and the second oil introduction groove 67B are located in a region between a first end portion 661A of the first extension 661 and a first end portion 662A of the second extension 662. The ends of each of the third oil introduction groove 67C and the fourth oil introduction groove 67D are located in a region between a second end portion 661B of the first extension 661 and a second end portion 662B of the second extension 662.

[0098] As in Fig. As shown in Fig. 9A, when the differential cage 6 rotates relative to the second output shaft 8B in a first direction R1, the lubricating oil O in the planetary gear accommodating space impacts the first end portion 661A of the first projection 661 and is guided into the first oil introduction groove 67A. Alternatively, the lubricating oil O impacts the second end portion 662B of the second projection 662 and is guided into the fourth oil introduction groove 67D.

[0099] As in Fig. 9B, when the differential cage 6 rotates relative to the second output shaft 8B in a second direction R2 opposite to the first direction R1, the lubricating oil O in the planetary gear accommodating space impacts the second end portion 661B of the first projection 661 and is introduced into the third oil introduction groove 67C. Alternatively, the lubricating oil O impacts the first end portion 662A of the second projection 662 and is introduced into the second oil introduction groove 67B.

[0100] As in Fig. As shown in FIG. 10, the oil discharge grooves 65A to 65D each reach the interior of the housing 61 at a radially outer side of the first side gear 74 relative to the first side gear 74, as viewed along an axial direction of the first side gear 74 (ie, the direction parallel to the X-axis). The exit ends of the oil discharge grooves 65A to 65D each have portions that do not overlap with the rotating first side gear 74.

[0101] Fig. 10 is a diagram of the interior of the housing 61, when viewed from the second sleeve 66. The first pinion 71, the second pinion 72, the pinion shaft 73 and the second side gear 75 are shown in Fig. 10 omitted.

[0102] The oil discharge grooves 65A to 65D are each arranged in a position where they overlap with the first pinion 71 or the second pinion 72 when viewed along the axial direction of the first side gear 74. Further, the oil discharge grooves 65A to 65D are each arranged between any two of the oil introduction grooves 67A to 67D in the circumferential direction of the first side gear 74 when viewed along the axial direction of the first side gear 74.

[0103] As in Fig. 4, the oil discharge grooves 65A to 65D each extend linearly. Furthermore, the width of the oil discharge grooves 65A to 65D each increases toward the outer end 64A of the first sleeve. In other words, the width of each of the oil introduction grooves 67A to 67D is minimum at the housing 61 and maximum at the inner side of the outer end 64A of the first sleeve 64. [1-2. Effects]

[0104] According to the above detailed explanations, the following effects can be achieved.

[0105] (1a) The oil in the gear case 9 flows along an outer surface of the projection 911 by gravity or centrifugal force and is stored in the pocket 633. This allows the oil stored in the pocket 633 to be supplied to the planetary gear bearings 5. As a result, the oil supply volume of the planetary gear bearings 5 ​​increases, thereby improving lubrication.

[0106] (1b) The inclined surface 912 can guide the oil in the gear case 9 into the projection 911. As a result, the oil storage efficiency in the pocket 633 increases.

[0107] (1c) The recess 913 can prevent the oil from being led out of the pocket 633 along the back of the projection 911. As a result, the oil can easily flow down from the projection 911 to the pocket 633, thereby increasing the oil storage efficiency in the pocket 633.

[0108] (1d) The cylindrical part 631 and the pocket 633 are integral with each other, whereby the forming process of the hole in the cylindrical part 631 and the forming process of the pocket 633 can be performed simultaneously. Accordingly, it becomes possible to form the pocket 633 with higher strength in the differential cage 6 while preventing an increase in the manufacturing processes. [2. Other versions]

[0109] Although the embodiment of the present disclosure has been described above, it should be understood that the present disclosure is not limited to the embodiment described above, but may be implemented in various forms.

[0110] (2a) In the gear device of the above-described embodiment, the gear case does not necessarily need to include the inclined surface or the recess.

[0111] (2b) In the transmission device of the above-described embodiment, the pocket of the differential cage need not necessarily be integral with the cylindrical part. For example, the pocket may be fixed to the cylindrical part by welding, fastening, or the like. Further, the differential cage may include a single annular pocket across the cylindrical parts. In other words, the pockets may be connected to each other in the circumferential direction of the sun gear.

[0112] (2c) Two or more functions of one component in the embodiments described above may be distributed among two or more components, or the functions of two or more components may be integrated into a single component. Also, part of the configurations of the embodiments may be omitted. At least part of the configurations of the embodiments may be added to or replaced by other configurations of the embodiments. Note that any form included in the technical idea defined by the wording of the appended claims may be an embodiment of the present disclosure. QUOTES CONTAINED IN THE DESCRIPTION

[0000] This list of documents submitted by the applicant was generated automatically and is included solely for the convenience of the reader. This list is not part of the German patent or utility model application. The DPMA assumes no liability for any errors or omissions. Cited patent literature

[0000] WO 2011 / 077869

[0003] < / ausgangswelle> < / seitenrad> < / differentialmechanismus> < / lagerhalter> < / planetenradlager> < / planetenrad> < / ringrad> < / sonnenrad> < / motorwelle>

Claims

[1] Transmission device comprising: a sun gear; a ring gear arranged concentrically with the sun gear; planetary gears meshing with the sun gear and the ring gear; bearings through each of which a shaft of a corresponding one of the planetary gears is inserted; a differential cage including bearing retainers, each of which holds a corresponding one of the bearings; a differential mechanism disposed within the differential cage; a first output shaft and a second output shaft connected to the differential mechanism; and a gearbox housing rotatably supporting the differential cage, the bearing holders each containing: a cylindrical part holding a corresponding one of the bearings, and a pocket which is recessed from a radially inner side to a radially outer side of the sun gear to have an inner space and which overlaps with the corresponding one of the bearings in an axial direction of the sun gear, and the gear housing includes a projection arranged to overlap with the pocket of each bearing retainer from the radially inner side of the sun gear and projecting in the axial direction of the sun gear toward the bearings. [2] The transmission device according to claim 1, wherein the transmission case further includes a slant surface inclined toward the projection from a position farther from each bearing in the axial direction of the sun gear than the projection and located on an inner side relative to the projection in a radial direction of the sun gear. [3] The transmission device according to claim 1 or 2, wherein the transmission case further includes a recess which is arranged in a back side of the projection on the radially outer side of the sun gear and which is recessed toward the radially inner side of the sun gear. [4] The transmission device according to claim 1 or 2, wherein the cylindrical member and the pocket are integrated with each other.

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