WO2011108316A1

WO2011108316A1 - Sprocket support structure

Info

Publication number: WO2011108316A1
Application number: PCT/JP2011/051810
Authority: WO
Inventors: 洋介野老
Original assignee: 本田技研工業株式会社
Priority date: 2010-03-02
Filing date: 2011-01-28
Publication date: 2011-09-09

Abstract

The disclosed sprocket support structure is compact, reduces friction loss accompanying sprocket rotation, and simplifies the process of machining a torque converter case. The sprocket support structure is provided with a bearing (40) for supporting the sprocket (30) so as to allow free rotation relative to the torque converter case (11), and an oil seal (39) which seals the gap between the torque converter case (11) and a sleeve (20). The bearing (40) is a ball bearing disposed in the radial gap between the inner surface (35a) of an opening (35) formed in the torque converter case (11) and the outer surface (31a) of the sprocket. Further, a first annular groove (36) for fitting the ball bearing (40) provided in the torque converter case (11) has a larger radius than that of a second annular groove (37) for fitting the oil seal (39). By this means, the machining direction of the second annular groove (37) can be identical to that of the first annular groove (36).

Description

Sprocket support structure

The present invention relates to a sprocket support structure in which a sprocket fixed to the pump impeller side of a torque converter and rotating about a central axis is rotatably supported with respect to a torque converter case.

In an automatic transmission including a conventional torque converter, for example, as shown in Patent Document 1, an automatic transmission including an oil pump disposed radially away from an input shaft to which rotation of the torque converter is transmitted is provided. is there. As a mechanism for driving such an oil pump, a drive side sprocket to which the rotation of the pump impeller of the torque converter is transmitted and a driven side sprocket installed on the oil pump side are connected by a chain. There is a drive mechanism. In such a drive mechanism, the drive-side sprocket is fixed to the outer periphery of a sleeve (torque converter sleeve) attached to the impeller shell of the torque converter, and rotates integrally with the sleeve around the input shaft. Yes.

In the drive mechanism of Patent Document 1, as a support structure that rotatably supports the drive-side sprocket (first sprocket) with respect to the torque converter case, the axial end surface of the sprocket flange and the axial direction of the torque converter case are provided. Thrust needle bearing installed between the end face and receiving thrust load, and press fit into the radial gap between the inner peripheral surface of the opening formed in the torque converter case and the outer peripheral surface of the sprocket to apply the radial load. A receiving bush (bearing cylinder) is installed. The sprocket is rotatably supported with respect to the torque converter case by both the thrust needle bearing and the bush.

JP 2006-64009 A

However, the conventional sprocket support structure shown in Patent Document 1 has the following problems.
(1) The thrust needle bearing installed in the axial clearance between the sprocket flange and the torque converter case makes it difficult to reduce the axial dimensions of the sprocket and its support structure. In addition, the thrust needle bearing is supported by the side surface on the inner diameter side of the sprocket teeth, and a bush is installed in the radial gap between the inner peripheral surface of the opening of the torque converter case and the outer peripheral surface of the sprocket. Therefore, it is difficult to reduce the size in the radial direction of the sprocket and its support structure.

(2) Since the periphery of the sprocket is difficult to form a lubricating oil introduction path, it is difficult to effectively guide the lubricating oil to the bush supporting the sprocket. Therefore, there is a problem that the supply of lubricating oil to the bush becomes insufficient and fretting wear is likely to occur. In addition, as a countermeasure for guiding the lubricating oil to the periphery of the bush supporting the sprocket, providing a lubricating hole for leading a part of the hydraulic oil in the torque converter to the bush is also performed. However, if the hydraulic oil in the torque converter is led out to the bush, the hydraulic pressure in the torque converter may be reduced. As a result, the responsiveness of the lockup clutch and the lockup clutch capacity are reduced, and there is a concern that the control of the torque converter will be affected.

(3) In the conventional structure shown in Patent Document 1, an annular groove for press-fitting a bush and an annular groove for press-fitting an oil seal are formed in the portion of the torque converter case that supports the sprocket. And the annular groove which press-fits an oil seal is set to the larger diameter dimension than the annular groove which press-fits a bush (refer FIG. 1 of patent document 1). However, in this configuration, when processing the torque converter case, the processing direction of the annular groove for press-fitting the oil seal is opposite to the processing direction of the other parts of the torque converter case including the annular groove for press-fitting the bush. There is a problem of becoming a direction. The reason is that on the outer surface of the torque converter case (surface on the transmission mechanism side), there is a support flange that supports the bearing of the rotary shaft (pulley shaft, differential shaft, etc.) provided in the transmission together with the annular groove for press-fitting the bush. Is formed. The support flange has a bag structure (concave shape) that opens to the outer surface of the torque converter case. For this reason, both the annular groove for press-fitting the bush and the inner surface of the support flange are usually processed from the outer surface side of the torque converter case. Then, the annular groove into which the oil seal is press-fitted must be processed in a separate process from the opposite side (the inner surface side of the torque converter case). As a result, the number of steps required to process the torque converter case increases, which may lead to complicated operations. Also, if the processing direction of the annular groove that press-fits the bush and the annular groove that press-fits the oil seal is reversed, the accuracy of the position of the oil seal and the bush cannot be increased, and the quality against oil leakage may be reduced. There is.

The present invention has been made in view of the above-mentioned points, and an object of the present invention is to reduce the size of the sprocket and its support structure, to reduce the friction loss associated with the rotation of the sprocket, and to process the torque converter case. It is an object of the present invention to provide a sprocket support structure capable of simplifying the above.

In order to solve the above problems, a sprocket support structure according to the present invention includes a torque converter case (11) that houses a torque converter (TC), and a sleeve that rotates integrally with an impeller shell (48) of the torque converter (TC) ( 20), a sprocket (30) attached to the sleeve (20) and rotating about the central axis of the torque converter (TC), and a bearing for rotatably supporting the sprocket (30) with respect to the torque converter case (11) (40) and a seal member (39) for sealing a radial gap between the torque converter case (11) and the sleeve (20), wherein the bearing (40) The inner peripheral surface (35a) of the opening (35) formed in the converter case (11) and the sprocket ( 0) is a ball bearing (40) interposed in a radial gap between the outer peripheral surface (31a) and the ball bearing (35a) on the inner peripheral surface (35a) of the opening (35) of the torque converter case (11). A first annular groove (36) for fitting (40) and a second annular groove (37) for fitting the seal member (39) are formed, and the first annular groove (36) is formed. Is set to have a diameter equal to or larger than that of the second annular groove (37).

In the sprocket support structure configured as described above, the first annular groove (36) and the second annular groove (37) are provided on the outer surface (11a) side and the inner surface (11b) side of the torque converter case (11), respectively. A transmission mechanism (4) having a plurality of rotating shafts (10, 12, 8b) is installed outside the outer surface (11a) of the torque converter case (11), and the torque converter case (11) A support flange (57, 58, 59) for supporting the rotating shaft (10, 12, 8b) is formed on the outer surface (11a) of the shaft, and the support flange (57, 58, 59) has a torque. It may be a bag structure that opens to the outer surface (11a) of the converter case (11).

According to the sprocket support structure of the present invention, the ball bearing is used as the bearing that rotatably supports the sprocket, so that the axial dimension and the radial dimension of the sprocket and its support structure can be reduced compared to the conventional structure. Can be achieved. That is, in the conventional structure shown in Patent Document 1, the axial length of the sprocket and its supporting structure is set by the thrust needle bearing installed between the axial end face of the sprocket and the axial end face of the torque converter case. In the present invention, the axial dimension of the sprocket support structure can be shortened by installing a ball bearing in the radial gap between the inner peripheral surface of the opening of the torque converter case and the outer peripheral surface of the sprocket. . Further, in the conventional structure shown in Patent Document 1, the thrust needle bearing is supported by the side surface on the inner diameter side of the sprocket teeth, and a bush is installed in the gap between the inner peripheral surface of the torque converter case and the outer peripheral surface of the sprocket. As a result, the radial dimensions of the sprocket and its support structure have increased, but in this embodiment, the installation of the bush is omitted and the sprocket teeth are arranged in the axial direction with respect to the ball bearing. Therefore, the radial dimension of the sprocket support structure can be shortened. Accordingly, it is possible to reduce the axial dimension and the radial dimension of the sprocket support structure.

Further, in the sprocket support structure of the present invention, since the sprocket is configured to be supported by a ball bearing, even in an environment where sufficient lubrication oil cannot be supplied compared to the conventional sprocket support structure using a bush, Fretting wear can be reduced by using a ball bearing with strong toughness against wear.

In the sprocket support structure of the present invention, the first annular groove for fitting the ball bearing formed in the torque converter case is set to have a diameter that is the same as or larger than the second annular groove for fitting the seal member. Thus, in processing the torque converter case, the second annular groove can be processed from the same side as the first annular groove. Thereby, the processing direction of a 2nd annular groove can be united with the processing direction of a 1st annular groove and another part. Therefore, the processing steps of the torque converter case can be reduced, and work efficiency can be improved.

In particular, a support flange for supporting the rotating shaft of the transmission mechanism portion is formed on the outer surface of the torque converter case, and the support flange has a bag structure that opens to the outer surface of the torque converter case. Since the machining directions of the first annular groove and the second annular groove can be matched with the machining directions of the inner surfaces of these support flanges, the machining process of the torque converter case can be effectively reduced.

Further, in the support structure of the present invention, the processing accuracy such as the degree of position of each part of the torque converter case can be improved, so that the life of the needle bearing press-fitted into the torque converter case can be improved and the gear of the transmission mechanism can be rotated. Reduction of generated noise can be expected.

Furthermore, the conventional sprocket support structure with bushes includes, as an assembly process, a step of processing an annular groove for press-fitting the bush into the torque converter case, a step of press-fitting the bush into the annular groove, and an inner peripheral surface of the press-fitted bush. In contrast, the sprocket support structure of the present invention includes a ball bearing instead of the bush, so that the step of press-fitting the bush and the step of processing the inner peripheral surface of the bush are performed. Can be omitted. Thereby, the assembly process of a sprocket support structure can be simplified.

Further, in the sprocket support structure described above, the movement of the ball bearing (40) in the thrust direction relative to the first annular groove (36) is restricted between the ball bearing (40) and the first annular groove (36). The first locking member (73) is installed between the ball bearing (40) and the sprocket (30) to restrict the movement of the sprocket (30) in the thrust direction relative to the ball bearing (40). The second locking member (75) may be installed.

According to this configuration, the ball bearing can be prevented from sliding in the thrust direction with respect to the torque converter case, and the sprocket can be prevented from sliding in the thrust direction with respect to the ball bearing. Therefore, it is possible to fit the sprocket and the ball bearing in a non-slidable state by press fitting or the like. Thereby, the clearance between a sprocket and a ball bearing can be made small, and the play of a sprocket can be suppressed few. In addition, if the first locking member is provided, the ball bearing can be fitted in a state in which the movement in the thrust direction is restricted with respect to the first annular groove. It is possible to set the groove to the same diameter. If the first annular groove and the second annular groove can be set to have the same diameter as described above, the first annular groove and the second annular groove can be processed in one step from the same direction. It becomes possible to reduce.
In addition, the code | symbol in said parenthesis shows the code | symbol of the component in embodiment mentioned later as an example of this invention.

According to the sprocket support structure of the present invention, the sprocket and the support structure can be downsized, the friction loss associated with the rotation of the sprocket can be reduced, the torque converter case processing process and the sprocket support structure assembly process can be efficiently performed, and the torque converter. The processing accuracy of each part of the case can be improved.

It is sectional drawing which shows a part of transmission with the sprocket support structure concerning 1st Embodiment of this invention. It is a partial expanded sectional view which shows the sprocket support structure concerning 1st Embodiment. It is a main sectional view showing an example of the entire configuration of a transmission. It is a partial expanded sectional view which shows the sprocket support structure concerning 2nd Embodiment of this invention.

Hereinafter, embodiments of the present invention will be described in detail with reference to the accompanying drawings.
[First Embodiment]
FIG. 1 is a cross-sectional view showing a part of a transmission including a sprocket support structure according to a first embodiment of the present invention. FIG. 2 is a partially enlarged cross-sectional view showing the sprocket support structure of the first embodiment. FIG. 3 is a main cross-sectional view showing an example of the overall configuration of the transmission. In FIG. 3, only the torque converter case 11 and the

bearings

60, 61, 62 described later are shaded for convenience of explanation.

The transmission 1 shown in FIGS. 1 to 3 includes a torque converter TC and a speed change mechanism 4 that changes the rotation input from the torque converter TC. As shown in FIG. 3, in the speed change mechanism unit 4, a metal V-belt 14 is stretched between a drive pulley 10 a fixed to the drive pulley shaft 10 and a driven pulley 12 a fixed to the driven pulley shaft 12. A belt type continuously variable transmission mechanism 5 is provided.

The transmission 1 also includes a main shaft 2 to which a driving force of a driving source (not shown) such as an engine is transmitted via a torque converter TC. A forward clutch 6 is provided on the main shaft 2. It is arranged. On the other hand, a reverse clutch 7 is disposed on the drive pulley shaft 10. Between the main shaft 2 and the drive pulley shaft 10, the gear mechanism 6 a that transmits the driving force from the main shaft 2 to the drive pulley shaft 10 by the engagement of the forward clutch 6 and the reverse clutch 7 is engaged. Is provided with a gear mechanism 7 a for transmitting the driving force from the main shaft 2 to the driving pulley shaft 10.

Thereby, the driving pulley shaft 10 of the belt type continuously variable transmission mechanism 5 is rotated by the driving force transmitted from the main shaft 2. On the other hand, the driving force from the driven pulley shaft 12 is transmitted to the left and right wheels (not shown) via the differential mechanism 8 and the left and

right axle shafts

8a and 8b. In addition, description is abbreviate | omitted about the detailed structure and operation | movement of the belt-type continuously variable transmission mechanism 5 here. Further, the specific configuration of the speed change mechanism 4 to which the driving force of the main shaft 2 is transmitted is not limited to the belt type continuously variable speed change mechanism 5 described above. It may be a type transmission mechanism.

The torque converter TC is housed in a bottomed container-shaped torque converter case 11. Further, a transmission case 19 that accommodates components of the speed change mechanism section 4 such as the belt-type continuously variable transmission mechanism 5 is attached to the outer surface (bottom face) 11 a in the axial direction of the torque converter case 11. Further, on the outer surface 11a of the torque converter case 11, a support flange 57 for supporting

bearings

60, 61, 62 attached to the drive pulley shaft 10, the driven pulley shaft 12, the axle shaft 8b and the like provided in the speed

change mechanism unit

4, 58 and 59 are formed. These

support flanges

57, 58 and 59 will be described later.

As shown in FIG. 1, the torque converter TC includes a pump impeller 41 driven by the crankshaft 3, a turbine runner 42 coupled to the main shaft 2 in a state of facing the pump impeller 41, a pump impeller 41, and a turbine runner And a one-way clutch 44 provided between the stator 43 and the stator shaft 13. A lockup clutch piston 46 with a damper is disposed between the turbine runner 42 and the engine drive plate 45. An impeller shell 48 is connected to the end of the converter cover 47 opposite to the crankshaft 3, and a torque converter sleeve (hereinafter simply referred to as “sleeve”) is connected to the inner peripheral side of the impeller shell 48. 20 is connected.

The outside of the turbine runner 42 is covered with a turbine shell 52. An inner peripheral portion of the turbine shell 52 is fixed to the main shaft 2 via a hub 53. A one-way clutch 44 that supports the stator 43 is splined to the stator shaft 13. The stator shaft 13 includes a hollow cylindrical portion 13a through which the main shaft 2 passes, and a substantially flat flange portion 13b extending radially outward from an end portion of the cylindrical portion 13a on the transmission mechanism portion 4 side. Have. Further, a protruding portion 15 for supporting the outer diameter side of the sprocket 30 is formed on the side surface of the flange portion 13b on the torque converter TC side.

Further, a gear-type oil pump (driven device) 16 is installed at a position spaced radially outward from the main shaft 2. The oil pump 16 is driven by the rotation of the oil pump drive shaft 16a. The oil pump drive shaft 16a extends in parallel with the main shaft 2 from the oil pump 16, and a driven sprocket 17 is attached to the tip of the oil pump drive shaft 16a. On the other hand, a drive-side sprocket 30 is fitted on the outer peripheral side of the sleeve 20 around the main shaft 2. A chain 18 is stretched between the drive-side sprocket 30 and the driven-side sprocket 17. The oil pump 16 is operated by transmitting the rotation of the drive-side sprocket 30 to the driven-side sprocket 17 via the chain 18.

As shown in FIG. 2, the sleeve 20 installed on the inner side of the sprocket 30 extends from the center of the torque converter TC toward the speed change mechanism portion 4, and has a substantially cylindrical shape surrounding the outer side of the cylindrical portion 13 a of the stator shaft 13. The cylindrical portion 21 is provided. The cylindrical portion 21 has a diameter dimension that can be fitted to the inner peripheral side of the sprocket 30. An O-ring (seal member) 23 is installed at a position on the torque converter TC side on the outer peripheral surface 21 a of the cylindrical portion 21.

The sprocket 30 has a substantially cylindrical main body 31. Sprocket teeth 32 for engaging the chain 18 are formed near the center in the axial direction on the outer peripheral surface 31 a of the main body 31. A ball bearing 40 described later is fitted to a position on the torque converter TC side on the outer peripheral surface 31 a of the main body 31. Further, the speed change mechanism portion 4 side on the outer peripheral surface 31 a of the main body portion 31 faces the protruding portion 15 provided on the flange portion 13 b of the stator shaft 13 with a slight gap in the radial direction. In this portion, an O-ring 33 for sealing a gap with the protruding portion 15 is installed. Note that the end of the inner peripheral surface 30 a of the sprocket 30 on the transmission mechanism portion 4 side is spline-fitted to the outer peripheral surface 21 a of the cylindrical portion 21.

The sprocket 30 is rotatably supported by a ball bearing 40 with respect to the torque converter case 11. The ball bearing 40 includes an outer ring 40 a that is fitted to the inner circumferential surface 35 a of the opening 35 formed in the torque converter case 11, and an inner ring 40 b that is fitted to the outer circumferential surface 31 a of the sprocket 30. An oil seal (seal member) 39 is press-fitted between the inner peripheral surface 35 a of the opening 35 of the torque converter case 11 and the outer peripheral surface 20 a of the sleeve 20. The oil seal 39 is disposed adjacent to the ball bearing 40 on the torque converter TC side. Thus, an oil passage 38 surrounded by the ball bearing 40 and the oil seal 39 is defined in the gap between the inner peripheral surface 35a of the opening 35 of the torque converter case 11 and the outer peripheral surface 20a of the sleeve 20. Lubricating oil is supplied to the ball bearing 40 through the oil passage 38.

A first annular groove 36 for fitting the ball bearing 40 and a second annular groove 37 for fitting the oil seal 39 are formed on the inner peripheral surface 35 a of the opening 35 of the torque converter case 11. Is formed. The ball bearing 40 is press-fitted into the clearance with the outer peripheral surface 31 a of the sprocket 30 in the first annular groove 36, and the oil seal 39 is connected to the outer peripheral surface 20 a of the sleeve 20 in the second annular groove 37. It is press-fitted into the gap.

The mounting state of the ball bearing 40 will be described in detail. The outer ring 40a of the ball bearing 40 is press-fitted and fitted into the inner peripheral surface 35a of the first annular groove 36. On the other hand, the inner ring 40b is fitted in a so-called loose state (relatively movable state) to the outer peripheral surface 31a of the sprocket 30, so that the inner ring 40b and the sprocket 30 slide with each other. Here, the reason why the outer peripheral surface 31a of the sprocket 30 and the inner ring 40b are fitted in a loose state is that the outer periphery of the sprocket 30 that is a fitting portion between the iron members due to a temperature change inside the transmission 1. This is to prevent the clearance of the sliding surface between the surface 31a and the inner ring 40b from fluctuating.

In the present embodiment, as described above, the sprocket 30 is supported while being slidable in the thrust direction by fitting the outer peripheral surface 31a of the sprocket 30 and the inner ring 40b in a loose state. Yes. The sprocket 30 is in a state of being pushed toward the torque converter TC by the hydraulic pressure of the hydraulic oil in the gap with the flange portion 13 b of the stator shaft 13. Therefore, the outer peripheral surface 31a of the sprocket 30 and the inner ring 40b do not slide during steady operation of the transmission 1. However, when the sprocket 30 is close to the flange portion 13b side of the stator shaft 13 such as immediately after the operation of the transmission 1 is started, a short time is required until the hydraulic pressure between the flange portion 13b and the sprocket 30 increases. The outer peripheral surface 31a of 30 may slide with respect to the inner ring 40b of the ball bearing 40.

Also, the first annular groove 36 and the second annular groove 37 are arranged coaxially on the outer surface 11a side and the inner surface 11b side of the torque converter case 11, and are in communication with each other. Here, the diameter of the first annular groove 36 is set to be larger than the diameter of the second annular groove 37.

In the sprocket support structure of the present embodiment, the bearing for rotatably supporting the sprocket 30 is the ball bearing 40, so that the sprocket 30 and its support structure can be downsized compared to the conventional structure. That is, in the conventional structure shown in Patent Document 1, the axial dimension of the sprocket and its support structure can be reduced by the thrust needle bearing installed between the axial end face of the sprocket and the axial end face of the torque converter case. On the other hand, in this embodiment, the ball bearing 40 is installed in the radial gap between the inner peripheral surface 35a of the opening 35 of the torque converter case 11 and the outer peripheral surface 31a of the sprocket 30 in the present embodiment. The axial dimension of the sprocket support structure can be shortened. Further, in the conventional structure shown in Patent Document 1, the thrust needle bearing is supported by the side surface on the inner diameter side of the sprocket teeth, and a bush is installed in the gap between the inner peripheral surface of the torque converter case and the outer peripheral surface of the sprocket. In this embodiment, the sprocket teeth 32 are arranged side by side in the axial direction with respect to the ball bearing 40. By omitting the installation of the bush, the radial dimension of the sprocket support structure can be shortened. Accordingly, it is possible to reduce the axial dimension and the radial dimension of the sprocket support structure.

Further, according to the sprocket support structure of the present embodiment, the sprocket 30 is configured to be supported by the ball bearing 40, thereby reducing the friction loss associated with the rotation of the sprocket 30 compared to the support structure using the conventional bush. it can. That is, since the periphery of the sprocket 30 is a place where it is difficult to form a lubricating oil introduction path, it is difficult to effectively guide the lubricating oil to the bearing that supports the sprocket 30. Therefore, the conventional support structure using bushes has a problem that fretting wear is likely to occur because sufficient lubricating oil cannot be supplied to the bushes. On the other hand, in the present embodiment, since the sprocket 30 is configured to be supported by the ball bearing 40, even if sufficient lubricating oil cannot be supplied to the ball bearing 40, In comparison, fretting wear can be reduced by using a ball bearing that is tough against wear. Further, unlike the conventional configuration, it is not necessary to derive a part of the hydraulic oil in the torque converter and guide it to the periphery of the sprocket, so that it is not necessary to reduce the hydraulic pressure in the torque converter TC. As a result, it is possible to prevent the responsiveness of the lock-up clutch and the lock-up clutch capacity from being lowered, and the torque converter can be controlled satisfactorily. In addition, the configuration around the sprocket 30 can be simplified.

In addition, the conventional sprocket support structure with bushes includes, as an assembling process, a step of processing an annular groove for press-fitting the bush into the torque converter case, a step of press-fitting the bush into the annular groove, and a process for processing the inner diameter surface of the press-fitted bush. However, in the sprocket support structure of this embodiment, the ball bearing 40 is installed instead of the bush, so that the step of press-fitting the bush and the step of processing the inner diameter surface of the bush are performed. Can be omitted. Therefore, the assembly process of the sprocket support structure can be simplified.

Next, the machining process of the torque converter case 11 will be described. As shown in FIG. 3, the torque converter case 11 includes a support flange for supporting a bearing 60 attached to the drive pulley shaft 10 in addition to the first annular groove 36 and the second annular groove 37 provided in the opening 35. 57, a support flange 58 for supporting the bearing 61 attached to the driven pulley shaft 12, a support flange 59 for supporting the bearing 62 attached to the axle shaft 8b, and the like are formed. These

support flanges

57, 58, 59 are open to the outer surface 11 a of the torque converter case so that the hydraulic oil (lubricating oil) in the transmission case 19 can be held therein and the

bearings

60, 61, 62 can be lubricated. It has a bag structure having a recess at the bottom. Therefore, it is necessary to process the inner surfaces of these

support flanges

57, 58, 59 from the outer surface 11a side of the torque converter case 11 (processing in the direction indicated by the arrow X in FIG. 3). The first annular groove 36 for press-fitting the ball bearing 40 also needs to be processed from the outer surface 11a side of the torque converter case 11.

Here, in the sprocket support structure of the present embodiment, as described above, the diameter dimension of the first annular groove 36 is set to be larger than the diameter dimension of the second annular groove 37. Thereby, in processing the torque converter case 11, the second annular groove 37 can be processed from the first annular groove 36 side. Therefore, the processing direction of the second annular groove 37 can be matched with the processing direction of the first annular groove 36. it can. Therefore, both the first annular groove 36 and the second annular groove 37 can be processed from the outer surface 11 a side of the torque converter case 11. Thereby, since the processing direction of the 1st annular groove 36 and the 2nd annular groove 37 and each

support flange

57,58,59 can be unified, the 1st, 2nd

annular groove

36,37 and the

support flanges

57,58, The number of steps required for processing the inner surface of 59 can be reduced. Further, since the processing directions of the first annular groove 36 for press-fitting the ball bearing 40 and the second annular groove 37 for press-fitting the oil seal 39 can be unified, the accuracy of the positional degree of the ball bearing 40 and the oil seal 39 can be increased. . Therefore, quality against oil leakage can be improved. Furthermore, it can be expected that the position of each part of the torque converter case 11 is improved. Therefore, it is possible to improve the life of a needle bearing or the like press-fitted into the torque converter case 11 and to reduce noise generated by rotation of a gear or the like provided in the transmission mechanism unit 4.

[Second Embodiment]
Next, a second embodiment of the present invention will be described. In the description of the second embodiment and the corresponding drawings, the same or corresponding components as those in the first embodiment are denoted by the same reference numerals, and detailed description thereof will be omitted below. In addition, matters other than those described below are the same as those in the first embodiment.

FIG. 4 is a partially enlarged cross-sectional view showing a sprocket support structure according to a second embodiment of the present invention. The sprocket support structure of the present embodiment includes a circlip (first locking member) 73 installed between the outer ring 40 a of the ball bearing 40 and the inner peripheral surface 35 a of the opening 35, the inner ring 40 b of the ball bearing 40, and the sprocket 30. The circlip (second locking member) 75 installed between the outer peripheral surface 31a of the ball bearing 40 and the sprocket 30 in the thrust direction is moved by the

circlips

73 and 75 with respect to the torque converter case 11. It is configured to regulate.

The circlip 73 installed between the outer ring 40a of the ball bearing 40 and the inner peripheral surface 35a of the opening 35 is a locking member made of a substantially C-shaped strip made of elastic metal, for example. It is fitted between an annular locking groove 73b provided on the outer peripheral surface of the outer ring 40a and an annular locking groove 73a formed on the inner peripheral surface 35a of the opening 35. The circlip 73 restricts the ball bearing 40 from moving in the thrust direction with respect to the inner peripheral surface 35 a of the opening 35. The circlip 75 installed between the inner ring 40b of the ball bearing 40 and the outer peripheral surface 31a of the sprocket 30 is a locking member made of, for example, a substantially C-shaped strip made of elastic metal, like the circlip 73. And is fitted into an annular locking groove 75a provided on the outer peripheral surface 31a of the sprocket 30. The circlip 75 restricts the movement of the ball bearing 40 in the thrust direction by sandwiching the inner ring 40b of the ball bearing 40 between the circlip 75 and the step portion 31b provided on the outer peripheral surface 31a of the sprocket 30. This restricts the sprocket 30 from moving in the thrust direction with respect to the ball bearing 40.

In the present embodiment, as described above, the circlip 73 installed between the outer ring 40 a of the ball bearing 40 and the inner peripheral surface 35 a of the opening 35, the inner ring 40 b of the ball bearing 40, and the outer peripheral surface 31 a of the sprocket 30. The movement of the ball bearing 40 and the sprocket 30 in the thrust direction with respect to the torque converter case 11 is restricted by the circlip 75 installed therebetween. Thereby, even when the hydraulic pressure of the hydraulic oil between the flange portion 13b and the sprocket 30 varies, the sprocket 30 can be prevented from sliding in the thrust direction with respect to the ball bearing 40.

And in 1st Embodiment, since it slides between the outer peripheral surface 31a of the sprocket 30 and the inner ring | wheel 40b of the ball bearing 40, by making these fit in a loose state, rather than a normal bearing attachment part. While it was necessary to ensure a wide clearance, in the present embodiment, the circlip 75 is installed, so that the outer peripheral surface 31a of the sprocket 30 and the inner ring 40b do not slide. Therefore, the outer peripheral surface 31a of the sprocket 30 can be fitted into the inner ring 40b of the ball bearing by press fitting. Thereby, since the clearance between the outer peripheral surface 31a of the sprocket 30 and the inner ring 40b can be reduced, the backlash of the sprocket 30 with respect to the ball bearing 40 can be reduced.

In the first embodiment, since the circlip 73 is not provided, the outer ring 40a of the ball bearing 40 is press-fitted into the inner peripheral surface 35a of the first annular groove 36, so that the ball against the first annular groove 36 is obtained. The movement of the bearing 40 in the thrust direction was restricted. On the other hand, in this embodiment, the circlip 73 is installed, so that the movement of the ball bearing 40 in the thrust direction with respect to the first annular groove 36 can be restricted. Therefore, the inner peripheral surface 35a of the first annular groove 36 and the outer ring 40a of the ball bearing 40 can be fitted in a so-called loose state.

Further, if a circlip 73 for locking the ball bearing 40 to the first annular groove 36 is provided as in the present embodiment, the circlip 73 causes a thrust to the first annular groove 36. The ball bearing 40 can be fitted in a state in which the movement in the direction is restricted. Thereby, although detailed illustration is omitted, even if the first annular groove 36 and the second annular groove 37 are set to have the same diameter, there is no possibility that the ball bearing 40 is shifted to the oil seal 39 side. And if the 1st annular groove 36 and the 2nd annular groove 37 can be set to the same diameter size as mentioned above, since the 1st annular groove 36 and the 2nd annular groove 37 can be processed only by one process from the same direction, Further reduction in the number of processing steps of the torque converter case 11 is possible.

On the other hand, as shown in FIG. 4, when the first annular groove 36 is set to have a larger diameter than the second annular groove 37, the diameter of the oil seal 39 can be kept small. The manufacturing cost can be reduced. Further, since the pressure receiving area of the oil seal 39 is reduced, durability against the oil seal 39 can be improved.

Although the embodiments of the present invention have been described above, the present invention is not limited to the above-described embodiments, and various modifications can be made within the scope of the technical idea described in the claims and the specification and drawings. Is possible. For example, a transmission to which the present invention is applied includes a sprocket that is attached to a sleeve (torque converter sleeve) and rotates around the center axis of the torque converter, and a bearing that rotatably supports the sprocket with respect to the torque converter case. As long as the transmission is provided, the other specific configuration is not limited to the transmission provided with the belt-type continuously variable transmission mechanism shown in the above embodiment, but the transmission provided with other mechanisms such as a planetary gear mechanism. It may be. In addition, the driven device driven by the rotation of the sprocket according to the present invention is not limited to the oil pump 16 shown in the above embodiment, and may be other types of devices.

Claims

A torque converter case containing the torque converter;
A sleeve that rotates integrally with the impeller shell of the torque converter;
A sprocket attached to the sleeve and rotating about a central axis of the torque converter;
A bearing that rotatably supports the sprocket with respect to the torque converter case;
A sprocket support structure comprising: a seal member that seals a radial gap between the torque converter case and the sleeve;
The bearing is a ball bearing interposed in a radial gap between an inner peripheral surface of an opening formed in the torque converter case and an outer peripheral surface of the sprocket,
A first annular groove for fitting the ball bearing and a second annular groove for fitting the seal member are formed on the inner peripheral surface of the opening of the torque converter case. ,
A sprocket support structure, wherein the first annular groove has a diameter equal to or larger than that of the second annular groove.
The first annular groove and the second annular groove are provided side by side on the outer surface side and the inner surface side of the torque converter case, respectively.
A transmission mechanism having a plurality of rotating shafts is installed outside the outer surface of the torque converter case,
A support flange for supporting the rotating shaft is formed on the outer surface of the torque converter case,
The sprocket support structure according to claim 1, wherein the support flange has a bag structure that opens to the outer surface of the torque converter case.
Between the ball bearing and the first annular groove, a first locking member for restricting the movement of the ball bearing in the thrust direction with respect to the first annular groove is installed,
The second locking member for restricting movement of the sprocket in the thrust direction with respect to the ball bearing is installed between the ball bearing and the sprocket. Sprocket support structure.