JP4513635B2 - Ring gear flange - Google Patents

Description

  The present invention relates to a ring gear flange provided to prevent a ring gear of a planetary gear device provided in an automatic transmission from moving in an axial direction.

  Since the ring gear of the planetary gear device is usually a helical tooth, a thrust force is generated by rotation. In order to prevent the ring gear from moving in the axial direction by the thrust force, the ring gear may be fixed to a ring gear flange that is not movable in the axial direction (for example, Non-Patent Document 1).

  In the ring gear flange of Non-Patent Document 1, since the outer peripheral edge is fixed to the ring gear, the thrust force from the ring gear is applied to the outer peripheral edge, while the inner peripheral portions of both side surfaces are brought into contact with the thrust bearing. Therefore, the inner peripheral portion is fixed in the axial direction. For this reason, if the ring gear flange is deformed by the applied thrust force, the outer peripheral portion of the ring gear flange is inclined to one side in the axial direction with respect to the inner peripheral portion, so the thrust bearings disposed on both side surfaces of the ring gear flange. The contact surface is inclined, leading to a reduction in the life of the thrust bearing.

However, since the ring gear flange of Non-Patent Document 1 is fitted to the outer periphery of the input shaft via the bush, and the inner peripheral side is supported by the bush, the ring gear flange is deformed by the thrust force applied to the ring gear. Is suppressed.
“Vista New Car Manual”, published by Toyota Motor Corporation, August 22, 2001, page 2-2 Japanese Utility Model Publication No. 8-233065

  In recent years, with the improvement in vehicle output, the thrust force applied to the ring gear flange has increased. To suppress deformation of the ring gear flange even if the thrust force increases, the rigidity of the ring gear flange can be increased by increasing the thickness of the ring gear flange. It is necessary to improve. However, increasing the thickness of the ring gear flange increases the cost, and is contrary to the recent demand for smaller automatic transmissions.

  The present invention has been made against the background of the above circumstances, and its object is to provide a ring gear flange capable of improving the life of a thrust bearing disposed adjacently without increasing the cost. It is in.

The first invention for achieving the above object, in order to prevent the ring gear of the planetary gear device provided in the automatic transmission is moved in the axial direction, and the monitor side outer peripheral edge is fixed to the ring gear A ring gear flange in which a thrust bearing is brought into contact with the inner peripheral portion of the shaft , and in a state after assembly, a portion with which the thrust bearing is in contact with a side surface is a shaft between the thrust bearing and the outer peripheral side. It is characterized by a tapered shape that is inclined so that the gap in the direction becomes large.

The second invention provides a ring gear flange of the first invention, wherein the inner portion is not fitted on the other member.

In the thrust bearing of the first invention as well, the outer peripheral edge is fixed to the ring gear, while the inner peripheral portion is brought into contact with the thrust bearing to prevent movement in the axial direction of the thrust bearing. when it is deformed by the thrust force, although the amount of deformation of the axial direction becomes larger as the outer periphery, the ring gear flange of the first invention, in a state after the assembling, the outer peripheral portion of the thrust bearing of its sides is brought into contact Since it is inclined in advance so that the axial gap with the thrust bearing becomes larger toward the side, the inclination of the side surface becomes relatively vertical when deformed by receiving the thrust force. Accordingly, the life of the thrust bearing is improved. Further, it is not necessary to increase the thickness of the ring gear flange, so there is no cost increase.

In addition, the ring gear flange of the structure of the second invention has the advantage of being compact, but the rigidity is lower than that in which the inner peripheral portion is supported like the ring gear flange described in Patent Document 1, It is easily deformed by the thrust force from the ring gear. That is, when the ring gear flange has the structure of the second invention, the contact surface of the thrust bearing adjacent to the ring gear flange tends to be vertical . Therefore, the life improvement effect of the thrust bearing by making the side surface into a tapered shape as in the first invention is great.

  Next, the present invention will be described more specifically based on the drawings. FIG. 1 is a partial cross-sectional view of an automatic transmission 10 for a vehicle. The automatic transmission 10 includes a first planetary gear device 20 having a ring gear flange 80 of the present invention and a second planetary gear device 60. ing.

  The first and second planetary gear devices 20 and 60 are so-called Ravigneaux types that are adjacent to each other and are shared by connecting carriers and ring gears to each other. That is, the first planetary gear unit 20 is a single pinion type planetary gear unit, and is relatively rotatable around an input shaft 12 that is a turbine shaft of a torque converter that is rotationally driven by a driving source such as an engine. A first sun gear 22 fitted to the outer peripheral side of the input shaft 12, a plurality of long pinions 24 that mesh with the first sun gear 22, a ring gear 26 that meshes with the long pinion 24, and the long pinion 24 that rotates and rotates. And a carrier 28 which is revolved. A pinion shaft 32 is inserted through the axial center of the long pinion 24 to fix the long pinion 24 to the carrier 28 via a needle bearing 30. The teeth formed on the first sun gear 22, the long pinion 24, and the ring gear 26 are helical teeth.

  The carrier 28 includes a shaft portion 34 and a support portion 36 that is connected to one end of the shaft portion 34 and supports the pinion shaft 32 and a pinion shaft 68 described later. The shaft portion 34 is a bearing 38. The carrier 28 is fixed to the case 40 so as to be rotatable relative to the case 40. In addition, disk-shaped first and second support walls 42 and 44 perpendicular to the shaft portion 34 are formed at both ends in the axial direction of the support portion 36 of the carrier 28.

  The first and second support walls 42 and 44 are formed with a number of through holes 46 corresponding to the number of long pinions 24 and short pinions 64 described later. A pinion shaft 68 for fixing the pinion shaft 32 or the short pinion 64 to the carrier 28 is inserted into the through hole 46, and both ends of the pinion shafts 32, 68 are connected to the support walls 42, 44. It is supported.

  The second support wall 44 has an outer radial hole 48 that is radially inward from the outer peripheral surface and communicates with the through-hole 46, and is on the same axis line as the outer radial hole 48. An inner radial hole 50 that communicates with the through hole 46 is formed in a radially outward direction.

  The pinion shafts 32 and 68 are formed with a radial hole 52 communicating with the outer radial hole 48 and the inner radial hole 50 formed in the second support wall 44 at one end in the axial direction. Yes. Then, the pin 56 passes through the outer radial hole 48 of the second support wall 44 and is inserted to the vicinity of the center of the radial hole 52 formed in the pinion shafts 32 and 68, whereby the pinion shafts 32 and 68 become the carrier. 28 is fixed.

  The second planetary gear device 60 is a double pinion type planetary gear device, and is fitted to the outer peripheral side of the input shaft 12 so as to be rotatable relative to the input shaft 12 at a position adjacent to the first sun gear 22. The second sun gear 62 and a plurality of short pinions 64 that mesh with the second sun gear 62 and also mesh with the long pinion 24 are provided. The second sun gear 62 and the short pinion 64 are also helical teeth. The second sun gear 62 and the short pinion 64, the long pinion 24, the carrier 28, the ring gear 26 and the like constitute a second planetary gear device 60. The pinion shaft 68 is inserted through the shaft center of the short pinion 64 in order to fix the short pinion 64 to the carrier 28 via a needle bearing 66.

  An intermediate support wall 70 parallel to the first and second support walls 42 and 44 is formed in the support portion 36 of the carrier 28 in the vicinity of the center in the axial direction, and the short pinion 64 is provided with this intermediate support wall. It is disposed between the wall 70 and the first support wall 42.

  An outer peripheral end of an annular plate-shaped ring gear flange 80 is joined to an end of the inner peripheral surface of the ring gear 26 on the second support wall 44 side by welding. The ring gear flange 80 is configured to be gradually separated from the second support wall 44 toward the inner peripheral side, and a vertical wall portion perpendicular to the axis of the input shaft 12 is formed on the inner peripheral portion. 80a is formed. A cylindrical portion 80b is formed at the inner peripheral end of the ring gear flange 80 continuous with the vertical wall portion 80a by being bent toward the carrier 28 in the axial direction. The position of the cylindrical portion 80 b in the radial direction is slightly inside the radial direction from the inner peripheral end of the second support wall 44.

  Thrust bearings 82 and 84 are brought into contact with both side surfaces of the vertical wall portion 80a of the ring gear flange 80, respectively. One thrust bearing 82 is welded to the vertical wall portion 80a of the ring gear flange 80 and is first welded. It is clamped by a side plate 86 of a clutch drum fixed to the sun gear 22. The other thrust bearing 84 has its radial position determined by being guided by the cylindrical portion 80b of the ring gear flange 80 (that is, by being brought into contact with the outer peripheral surface of the cylindrical portion 80b of the ring gear flange 80). Yes. Further, the thrust bearing 84 is a bearing in which the surface opposite to the side in contact with the vertical wall 80 a of the ring gear flange 80 is locked to the inner peripheral end of the second support wall 44 of the carrier 28. It is brought into contact with the side surface of the second support wall 44 via the race 88.

  With this configuration, the ring gear flange 80 and the ring gear 26 fixed to the ring gear flange 80 are rotatable relative to the sun gears 22 and 62 and the carrier 28, and the movement of the input shaft 12 in the axial direction is prohibited. Further, when the ring gear 26 is rotated, a thrust force is generated, and the thrust force is applied to the ring gear flange 80.

  FIG. 2 is an enlarged cross-sectional view of the inner peripheral side portion of the ring gear flange 80. FIG. 2 shows a no-load state in which no thrust force is applied to the ring gear flange 80. As shown in FIG. 2, the left side surface of the vertical wall portion 80a of the ring gear flange 80 (the first planetary gear unit 20). 80c is a taper shape slightly inclined toward the ring gear 26 side (right side in the drawing) in the axial direction toward the outer peripheral side, in other words, the axial direction formed between the thrust bearing 82 and the outer peripheral side. The taper shape is inclined so that a slight gap d of the gap is increased. When the ring gear flange 80 is deformed by inputting a thrust force in the direction of the thrust bearing 82 (the left direction in the figure) from the ring gear 26 to the ring gear flange 80 having such a structure, the portion that is in contact with the thrust bearing 82 on the inner peripheral portion As a fulcrum, the gap d is narrowed or disappears.

  Next, the inclination of the tapered side surface 80c, that is, the size of the gap d will be described with reference to FIG. In FIG. 3, V indicates a vertical surface including one side surface of the thrust bearing 82, and S indicates a plane including the side surface 80 c of the ring gear flange 80. Further, the horizontal line Y (out) indicates the radial position of the outer peripheral end of the thrust bearing 82, and d (out) indicates the gap d on the horizontal line Y (out). In FIG. 3, the gap d is exaggerated.

  When the amount of deformation in the axial direction (lateral direction in FIG. 3) of the ring gear flange 80 on the horizontal line Y (out) is t, the amount of deformation t varies depending on the thrust force from the ring gear 26, and the inclination of the side surface 80c is It is determined based on the deformation amount t. That is, assuming that the maximum deformation amount obtained in advance by experiment or calculation is t (max), the inclination of the side surface 80c indicates that the gap d in the no-load state is less than or equal to the maximum deformation amount t (max) (d ≦ t (max) ).

  For example, when d = t (max), when the load is most applied to the thrust bearing 82 and the ring gear flange 80 is deformed by the maximum amount, the side surface of the thrust bearing 82 and the side surface 80c of the ring gear flange 80 are set. And even when the deformation amount t is smaller than that, the inclination of the side surface 80c is closer to the vertical than in the case where the side surface 80c is vertical in the no-load state. The degree is relaxed.

  When d <t (max), the side surface of the thrust bearing 82 and the side surface 80c of the ring gear flange 80 are parallel at some point where the thrust force applied from the ring gear 26 is smaller than the maximum value. Further, even when the thrust force is larger than that, the gap d exists in the no-load state, so that the inclination of the side surface 80c becomes closer to the vertical than in the case where the side surface 80c is vertical in the no-load state. Therefore, the degree per piece with respect to the thrust bearing 82 is relaxed.

  As described above, the thrust bearing 82 of the present embodiment has the outer peripheral edge fixed to the ring gear 26, while the inner peripheral portion is brought into contact with the thrust bearing 82 to move the thrust bearing 82 in the axial direction. Therefore, when it is deformed by the thrust force from the ring gear 26, the amount of deformation in the axial direction increases toward the outer peripheral side, and the inner peripheral portion of the ring gear flange 80 is externally fitted to another member. Since it is difficult to ensure rigidity, it is easily deformed by the thrust force from the ring gear 26. However, in the thrust bearing 82 of this embodiment, the side surface 80c on the thrust bearing 82 side is inclined in advance so that an axial gap d with the thrust bearing 82 increases toward the outer peripheral side. When received and deformed, the inclination of the side surface 80c becomes relatively vertical. Accordingly, the life of the thrust bearing 82 is improved. Further, since it is not necessary to increase the thickness of the ring gear flange 80, there is no cost increase.

  As mentioned above, although the Example of this invention was described in detail based on drawing, this invention is applied also in another aspect.

  For example, in the above-described embodiment, the planetary gear devices 20 and 60 are so-called Ravigneaux type, but the present invention can also be applied to planetary gear devices other than Ravigneaux type.

  In the ring gear flange 80 of the above-described embodiment, the inner peripheral portion is not externally fitted to another member. However, as described in Patent Document 1, the inner peripheral portion is externally fitted to another member. The present invention may be applied to the flange.

  Further, in the ring gear flange 80 of the above-described embodiment, only the side surface 80c opposite to the first planetary gear device 20 is tapered, but the present invention is applied to the other side surface to be tapered. May be.

  Further, the side surface 80c of the ring gear flange 80 of the above-described embodiment is tapered in a range wider than the range in which the thrust bearing 82 is brought into contact, but the range in which the thrust bearing 82 is brought into contact, that is, in the radial direction. The range from the inner peripheral end to the outer peripheral end of the thrust bearing 82 may be tapered.

  The above description is only an embodiment, and the present invention can be implemented in variously modified and improved forms based on the knowledge of those skilled in the art.

It is a fragmentary sectional view of the automatic transmission for vehicles which has the planetary gear apparatus provided with the ring gear flange of this invention. It is an expanded sectional view of the inner peripheral side part of the ring gear flange of FIG. FIG. 3 is a diagram schematically showing FIG. 2.

Explanation of symbols

20: First planetary gear unit, 26: Ring gear, 80: Ring gear flange, 80c: Side surface, 84: Thrust bearing

Claims (2)

To the ring gear of the automatic transmission planetary gear device provided in is prevented from moving in the axial direction, the thrust bearing in the inner peripheral portion of the monitor side outer peripheral edge is fixed to the ring gear is brought into contact Ring gear flange,
In a state after assembling, a portion of the side surface on which the thrust bearing is brought into contact has a tapered shape inclined so that an axial clearance between the thrust bearing and the thrust bearing becomes larger toward the outer peripheral side. And ring gear flange. The ring gear flange according to claim 1, wherein the inner peripheral portion is not externally fitted to another member.

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