JP2017219111A - Continuously variable transmission - Google Patents

Abstract

PROBLEM TO BE SOLVED: To provide a continuously variable transmission which can reduce the number of assembly processes and the number of components to inhibit cost increase.SOLUTION: A continuously variable transmission (CVT) 40 includes: a counter drive gear 51 which is fitted in a secondary shaft 44 so as to be abutted with a step part 44s of the secondary shaft 44 at a large diameter cylinder part 511 and integrally rotate with the secondary shaft 44; a first bearing 91 which is supported by a rear case 22c and supports a secondary pulley 45 side end part of the secondary shaft 44; a second bearing 92 which is supported by a housing 22a and supports the counter drive gear 51 fitted in the secondary shaft 44 at an opposite side of the first bearing 91 with respect to the secondary pulley 45; and a single shim member 100 which restricts axial displacement of the secondary shaft 44 and the counter drive gear 51 relative to a transmission case 22.SELECTED DRAWING: Figure 2

Description

  The present disclosure includes a primary shaft having a primary pulley, a secondary shaft having a secondary pulley, a transmission belt wound around the primary pulley and the secondary pulley, and a case housing the primary shaft, the secondary shaft, and the transmission belt. The present invention relates to a step transmission.

  Conventionally, as this type of continuously variable transmission, a stopper plate that presses an outer race of a bearing that rotatably supports one end of a secondary shaft against a case (rear case), and an end of the secondary shaft opposite to the stopper plate side And a pair of bearings (conical roller bearings) that rotatably support both ends of the drive gear are known (for example, see Patent Document 1). In this continuously variable transmission, the axial displacement of the movable sheave of the secondary pulley is restricted by the stopper plate, thereby suppressing the inclination of the transmission belt (the axial displacement of the transmission belt). Further, in this continuously variable transmission, for example, a shim member is interposed between the outer race of the bearing that supports the drive gear and the case, whereby the axial displacement of the drive gear can be regulated.

JP 2010-96337 A

  In the conventional continuously variable transmission described above, the axial displacement of the transmission belt and the drive gear is restricted by using the stopper plate and the shim member, thereby suppressing the deterioration of the torque transmission efficiency and durability of the transmission belt and the drive gear. can do. However, when both the stopper plate and the shim member are used, the assembly process and the number of parts of the continuously variable transmission increase, leading to an increase in the cost of the continuously variable transmission.

  Accordingly, the main object of the invention of the present disclosure is to provide a continuously variable transmission that can reduce the assembly process and the number of parts to suppress the cost increase.

  The continuously variable transmission of the present disclosure includes a primary shaft having a primary pulley, a secondary shaft having a secondary pulley, a transmission belt wound around the primary pulley and the secondary pulley, the primary shaft, the secondary shaft, and the A continuously variable transmission including a case that houses a transmission belt; and a drive gear fitted to the secondary shaft so that one end abuts against a part of the secondary shaft and rotates integrally with the secondary shaft; A first bearing supported by a case and supporting an end of the secondary shaft on the secondary pulley side; and supported by the case and on the opposite side of the secondary pulley from the first bearing. Mated to shaft A second bearing that supports the drive gear has said is disposed around the secondary shaft is intended and a single shim member for regulating the axial displacement relative to the case of the secondary shaft and the drive gear.

  In this continuously variable transmission, the drive gear is fitted to the secondary shaft such that one end thereof abuts against a portion of the secondary shaft and rotates integrally with the secondary shaft. The first bearing is supported by the case to support the end portion of the secondary shaft on the secondary pulley side, and the second bearing is supported by the case, and on the opposite side of the secondary bearing from the first bearing. A drive gear fitted to the secondary shaft is supported. Thus, if the axial displacement of either the secondary shaft or the drive gear is restricted between the first bearing and the second bearing, the other axial displacement can be restricted. Therefore, in this continuously variable transmission, the single shim member regulates the axial displacement of the secondary shaft and the drive gear with respect to the case, thereby suppressing the inclination of the transmission belt (axial displacement of the transmission belt), The axial displacement of the drive gear can be regulated. As a result, it is possible to reduce the assembly process and the number of parts of the continuously variable transmission, thereby suppressing an increase in cost.

It is a schematic block diagram of the power transmission device containing the continuously variable transmission of this indication. It is an enlarged view which shows the principal part of the continuously variable transmission of this indication.

  Next, embodiments for carrying out the invention of the present disclosure will be described with reference to the drawings.

  FIG. 1 is a schematic configuration diagram illustrating a power transmission device 20 including a continuously variable transmission (hereinafter referred to as “CVT” as appropriate) 40 of the present disclosure. The power transmission device 20 shown in the figure is mounted on a front wheel drive vehicle, and is disposed horizontally so that a crankshaft and left and right drive shafts 59 connected to drive wheels (not shown) are substantially parallel. It is configured as a transaxle connected to the engine. As shown in the figure, the power transmission device 20 includes a housing (first case) 22a, a transaxle case (second case) 22b, and a rear case (third case) 22c that are integrally coupled in addition to the CVT 40. 22, a starting device 23 housed in the transmission case 22 together with the CVT 40, an oil pump 30, a forward / reverse switching mechanism 35, a gear mechanism 50, a differential gear (differential mechanism) 57, and the like.

  The starting device 23 is configured as a fluid starting device with a lock-up clutch, and is accommodated in the housing 22a. As shown in FIG. 1, the starting device 23 includes a pump impeller 23p connected to an engine crankshaft via a front cover 21 as an input member, a turbine runner 23t fixed to an input shaft 41 of a CVT 40, and a pump impeller. 23p and a stator 23s disposed inside the turbine runner 23t to rectify the flow of hydraulic oil (ATF) from the turbine runner 23t to the pump impeller 23p, a one-way clutch 23o that restricts the rotational direction of the stator 23s in one direction, and a damper mechanism 24, a lock-up clutch 25 and the like.

  The pump impeller 23p, the turbine runner 23t, and the stator 23s function as a torque converter by the action of the stator 23s when the rotational speed difference between the pump impeller 23p and the turbine runner 23t is large, and function as a fluid coupling when the rotational speed difference between the two decreases. To do. However, in the starting device 23, the stator 23s and the one-way clutch 23o may be omitted, and the pump impeller 23p and the turbine runner 23t may function as only a fluid coupling. For example, the damper mechanism 24 is connected to the input element connected to the lockup clutch 25, the intermediate element connected to the input element via the plurality of first elastic bodies, and connected to the intermediate element via the plurality of second elastic bodies. And an output element fixed to the turbine hub. The lock-up clutch 25 selectively locks up and releases the lock-up mechanically connecting the pump impeller 23p and the turbine runner 23t, that is, the front cover 21 and the input shaft 41 of the CVT 40 (via the damper mechanism 24). To be executed. The lock-up clutch 25 may be configured as a hydraulic single-plate friction clutch, or may be configured as a hydraulic multi-plate friction clutch.

  The oil pump 30 includes a pump assembly including a pump body 31 and a pump cover 32 disposed between the starting device 23 and the forward / reverse switching mechanism 35, an inner rotor (external gear) 33, and an outer rotor (internal gear). 34 is configured as a so-called gear pump. The pump body 31 and the pump cover 32 are fixed to the housing 22a and the transaxle case 22b. The inner rotor 33 is connected to the pump impeller 23p through a hub. Therefore, when the inner rotor 33 is rotated by the power from the engine, hydraulic oil (ATF) in an oil pan (hydraulic oil reservoir) (not shown) is sucked by the oil pump 30 via a strainer (not shown) and boosted. The hydraulic fluid thus supplied is supplied (discharged) to a hydraulic control device (not shown).

  The forward / reverse switching mechanism 35 is accommodated in the transaxle case 22b, and includes a double pinion planetary gear mechanism 36, and a brake B1 and a clutch C1 as hydraulic friction engagement elements. The planetary gear mechanism 36 includes a sun gear fixed to the input shaft 41 of the CVT 40, a ring gear, a pinion gear meshing with the sun gear, and a carrier supporting the pinion gear meshing with the ring gear and coupled to the primary shaft 42 of the CVT 40. The brake B1 releases the ring gear of the planetary gear mechanism 36 rotatably with respect to the transaxle case 22b, and when the hydraulic pressure is supplied from the hydraulic control device, the brake B1 moves the ring gear of the planetary gear mechanism 36 to the transaxle case 22b. Fix it so that it cannot rotate. Further, the clutch C1 releases the carrier of the planetary gear mechanism 36 so as to be rotatable with respect to the input shaft 41 (sun gear), and the carrier of the planetary gear mechanism 36 when the hydraulic pressure is supplied from the hydraulic control device. Connect to

  Thus, when the brake B1 is released and the clutch C1 is engaged, the power transmitted to the input shaft 41 can be transmitted to the primary shaft 42 of the CVT 40 as it is to advance the vehicle. Further, when the brake B1 is engaged and the clutch C1 is released, the rotation of the input shaft 41 is converted in the reverse direction and transmitted to the primary shaft 42 of the CVT 40, and the vehicle can be moved backward. Furthermore, if the brake B1 and the clutch C1 are released, the connection between the input shaft 41 and the primary shaft 42 can be released.

  The CVT 40 includes a primary pulley 43 provided on a primary shaft (first axis) 42 as a driving side rotation axis, and a secondary shaft (second axis) 44 as a driven side rotation axis arranged in parallel with the primary shaft 42. The secondary pulley 45 provided, the transmission belt 46 spanned between the pulley groove of the primary pulley 43 and the pulley groove of the secondary pulley 45, and a primary cylinder which is a hydraulic actuator for changing the groove width of the primary pulley 43 47 and a secondary cylinder 48 which is a hydraulic actuator for changing the groove width of the secondary pulley 45. The primary pulley 43 includes a fixed sheave 43a formed integrally with the primary shaft 42, and a movable sheave 43b supported by the primary shaft 42 so as to be slidable in the axial direction via a ball spline. The secondary pulley 45 is supported by a fixed sheave 45a formed integrally with the secondary shaft 44, and is supported by the secondary shaft 44 through a ball spline so as to be slidable in the axial direction, and by a return spring 49 which is a compression spring. And a movable sheave 45b biased in the direction.

  The primary cylinder 47 is formed behind the movable sheave 43 b of the primary pulley 43, and the secondary cylinder 48 is formed behind the movable sheave 45 b of the secondary pulley 45. Hydraulic oil is supplied to the primary cylinder 47 and the secondary cylinder 48 from the hydraulic control device so as to change the groove width between the primary pulley 43 and the secondary pulley 45. As a result, the power transmitted from the engine to the primary shaft 42 via the starting device 23 and the forward / reverse switching mechanism 35 can be steplessly shifted and transmitted to the secondary shaft 44. The power transmitted to the secondary shaft 44 is transmitted to the left and right drive wheels via the gear mechanism 50, the differential gear 57, and the drive shaft.

  The gear mechanism 50 includes a counter drive gear 51 that rotates integrally with the secondary shaft 44, and a counter shaft that extends in parallel with the secondary shaft 44 and the drive shaft 59 and is rotatably supported by the transmission case 22 via a bearing. (Third axis) 52, a counter driven gear 53 fixed to the counter shaft 52 and meshing with the counter drive gear 51, and a drive pinion gear (molded integrally with the counter shaft 52 or fixed to the counter shaft 52) Final drive gear) 54 and a differential ring gear (final driven gear) 55 that meshes with drive pinion gear 54 and is connected to differential gear 57.

  FIG. 2 is an enlarged view showing a main part of the CVT 40. As shown in the figure, the counter drive gear 51 is formed in a hollow cylindrical shape, and has a large diameter cylindrical shape including a plurality of external teeth 510 that mesh with corresponding gear teeth of the counter driven gear 53 (see FIG. 1). And a small-diameter cylindrical portion 512 having a smaller diameter than the large-diameter cylindrical portion 511 (bottom circle of the external teeth 510) extending in the axial direction from the large-diameter cylindrical portion 511. A fitting spline 513 is formed on the inner peripheral surface of the small diameter cylindrical portion 512 so as not to overlap the plurality of external teeth 510 and the counter drive gear 51 in the axial direction. In the present embodiment, the fitting spline 513 has an end portion (on the right side in FIG. 2) opposite to the large-diameter cylindrical portion 511 of the small-diameter cylindrical portion 512 so as to be spaced apart from the plurality of external teeth 510 in the axial direction. (End part) is formed on the inner peripheral surface.

  The fitting spline 513 is fitted to a spline 440 formed on the outer peripheral surface of the secondary shaft 44 with a circumferential clearance so that the counter drive gear 51 can rotate integrally with the secondary shaft 44. It functions as a fitting part fitted to the secondary shaft 44. As shown in FIG. 2, the spline 440 is formed at the end of the secondary shaft 44 opposite to the secondary pulley 45. Accordingly, the counter drive gear 51 is arranged such that the fitting spline 513 (and the spline 440) is separated from the primary pulley 43, the secondary pulley 45, and the transmission belt 46 as the torque transmission mechanism in the axial direction rather than the plurality of external teeth 510. The secondary shaft 44 is fitted. On the other hand, a portion of the inner peripheral surface of the counter drive gear 51 that is closer to the larger-diameter cylindrical portion 511 than the fitting spline 513 is inlay fitted to the secondary shaft 44.

  Furthermore, the end surface of the large-diameter cylindrical portion 511 (one end portion) of the counter drive gear 51 fitted to the secondary shaft 44 abuts on a stepped portion (expanded diameter portion) 44 s formed on the secondary shaft 44. In the present embodiment, the counter drive gear 51 is formed with a recess for suppressing interference with a nut 481 for fixing the cylinder member 480 constituting the secondary cylinder 48 to the secondary shaft 44, as shown in FIG. The end surface of the large-diameter cylindrical portion 511 that is in contact with the stepped portion 44s is located in the concave portion. When the counter drive gear 51 is attached to the secondary shaft 44, the plurality of external teeth 510 (large diameter cylindrical portion 511) is more secondary pulley 45 (torque than the small diameter cylindrical portion 512, as shown in FIG. 2. Proximity to the transmission mechanism. Therefore, the counter driven gear 53 is fixed to the counter shaft 52 so as to be closer to the secondary pulley 45 (torque transmission mechanism) in the axial direction than the drive pinion gear 54 (see FIG. 1). Thereby, it becomes possible to shorten the axial length of CVT40 and by extension, the power transmission device 20. FIG.

  As illustrated, the end of the secondary shaft 44 on the secondary pulley 45 side is rotatably supported by a first bearing 91 supported by a rear case 22 c of the transmission case 22. The counter drive gear 51 fitted to the secondary shaft 44 is positioned on the opposite side of the secondary pulley 45 from the first bearing 91 and is rotated by the second bearing 92 supported by the housing 22a of the transmission case 22. It is supported freely. In this way, the secondary shaft 44 and the counter drive gear 51 are supported by the pair of first and second bearings 91 and 92, whereby the secondary pulley side end of the secondary shaft is supported by a single bearing, and the secondary shaft Compared with the case where both ends of the counter drive gear attached to the shaft are supported by two bearings supported by the case, the CVT 40 and thus the entire power transmission device 20 can be made compact.

  In the present embodiment, the first bearing 91 is a ball bearing including an inner race 91i and an outer race 91o. The inner race 91 i of the first bearing 91 is press-fitted into the end of the secondary shaft 44 on the secondary pulley 45 side and is held by a nut 91 n and a fixed sheave 45 a that are screwed into the end of the secondary shaft 44. The outer race 91o is held by the rear case 22c. The second bearing 92 is also a ball bearing including an inner race 92i and an outer race 92o. The inner race 92 i of the second bearing 92 is in contact with the outer teeth 510 at a portion close to the plurality of outer teeth 510 of the small-diameter cylindrical portion 512 so as not to overlap the fitting spline 513 of the counter drive gear 51 in the axial direction. Arranged not to. The outer race 92o has the same axial length as the inner race 92i and is press-fitted into a recess formed in the housing 22a. That is, the second bearing 92 does not come into contact with the plurality of external teeth 510 and does not overlap with the fitting spline 513 in the axial direction from the secondary pulley 45 rather than the plurality of external teeth 510 of the small diameter cylindrical portion 512. Support the spaced apart part. Note that at least one of the first and second bearings 91 and 92 may be a tapered roller bearing or a cylindrical roller bearing.

  As described above, in the CVT 40, the counter drive gear 51 is configured such that the large-diameter cylindrical portion 511 (one end portion) abuts against the step portion 44 s of the secondary shaft 44 and rotates integrally with the secondary shaft 44. Fitted. The first bearing 91 is supported by the rear case 22 c of the transmission case 22 and supports the end of the secondary shaft 44 on the secondary pulley 45 side. Furthermore, the second bearing 92 is supported by the housing 22 a of the transmission case 22 and supports the counter drive gear 51 fitted to the secondary shaft 44 on the opposite side of the secondary pulley 45 from the first bearing 91. . Therefore, if the axial displacement of either the secondary shaft 44 or the counter drive gear 51 is restricted between the first bearing 91 and the second bearing 92, the other axial displacement can also be restricted. It becomes.

  In view of this, in the CVT 40, the inner race 92i of the second bearing 92 and the counter are prevented so that the single shim member (selective shim) 100 formed in an annular shape by a thin metal plate does not contact the plurality of external teeth 510. It arrange | positions between the large diameter cylindrical parts 511 of the drive gear 51. FIG. In the present embodiment, the end on the small diameter cylindrical portion 512 side of the large diameter cylindrical portion 511 of the counter drive gear 51 is smaller in diameter than the root circle of the external tooth 510 and larger in diameter than the small diameter cylindrical portion 512. An abutting portion 511s is formed, and the shim member 100 is disposed between the abutting portion 511s and the end surface of the inner race 92i so as to abut against each other.

  Thus, in the CVT 40, the axial displacement of the secondary shaft 44 and the counter drive gear 51 with respect to the transmission case 22 is restricted by the single shim member 100 disposed around the secondary shaft 44, and thereby the inclination of the transmission belt 46 While suppressing (the axial displacement of the transmission belt 46), the axial displacement of the counter drive gear 51 can be restricted. As a result, it is possible to suppress the torque transmission efficiency via the transmission belt 46 and the counter drive gear 51 and the deterioration of both durability. Further, in the CVT 40, since the axial displacement of the transmission belt 46 and the counter drive gear 51 can be restricted only by the single shim member 100, the assembly process and the number of parts of the CVT 40 can be reduced to suppress the cost increase. Is possible.

  In the CVT 40 configured as described above, torque is transmitted from the primary shaft 42 to the secondary shaft 44 via the primary pulley 43, the transmission belt 46, and the secondary pulley 45 as a torque transmission mechanism. The torque transmitted to the secondary shaft 44 is transmitted from the secondary shaft 44 to the fitting spline 513 of the counter drive gear 51 via the spline 440, as indicated by a broken line in FIG. Further, the torque transmitted to the counter drive gear 51 is transmitted from the inner peripheral side fitting spline 513 to a plurality of external teeth 510 spaced apart in the axial direction.

  Thereby, while suppressing an increase in the axial length of the secondary shaft 44, the torque transmission path from the secondary pulley 45 (torque transmission mechanism) to the external teeth 510 of the counter drive gear 51 is extended, so that the counter drive from the secondary pulley 45 is performed. The rigidity (torsional rigidity) of the members up to the outer teeth 510 of the gear 51 can be substantially reduced. Therefore, it is possible to reduce the dynamic rigidity at the meshing portion of the counter drive gear 51 and the counter driven gear 53 to reduce gear noise generated by the meshing of both, and to suppress the rigidity of the transmission case 22, that is, the increase in weight. You can also. As a result, in the power transmission device 20 including the CVT 40, the gear noise generated by the meshing between the counter drive gear 51 attached to the secondary shaft 44 and the counter driven gear 53 is reduced while reducing the overall size and weight of the device. It becomes possible.

  Furthermore, in the CVT 40, the second bearing 92 is disposed between the plurality of external teeth 510 and the fitting spline 513 so as not to overlap with each other in the axial direction. In addition to supporting the moment by the second bearing 92, the moment is prevented from acting on the fitting spline 513 and the spline 440 side, and thereby the member from the secondary pulley 45 to the external tooth 510 of the counter drive gear 51 is suppressed. It is possible to satisfactorily reduce the rigidity. In addition, the CVT 40 contributes to torque transmission only by being supported by the second bearing 92 as in the case where the second bearing 92 is arranged so as to be separated from the secondary pulley 45 in the axial direction rather than the fitting spline 513. Since it is not necessary to provide the portion to be removed on the secondary shaft 42, the secondary shaft 42 can be shortened and the entire apparatus can be made compact.

  In the above-described embodiment, the fitting portion of the counter drive gear 51 is the fitting spline 513 fitted to the spline 440 formed on the outer peripheral surface of the secondary shaft 44 with a circumferential clearance. Thereby, it is possible to rotate the second shaft and the drive gear integrally while suppressing an increase in the rigidity (torsional rigidity) of the members from the secondary pulley 45 (torque transmission mechanism) to the external teeth of the counter drive gear 51. It becomes. Furthermore, by providing the fitting spline 513 in the small diameter cylindrical portion 512 of the counter drive gear 51, the rigidity of the member from the secondary pulley 45 (torque transmission mechanism) to the external teeth of the counter drive gear 51 can be satisfactorily reduced. it can. Further, by supporting the portion close to the plurality of external teeth 510 of the small diameter cylindrical portion 512 by the second bearing 92, an increase in the interval between the first and second bearings 91 and 92 is suppressed and the counter drive gear 51 It becomes possible to reduce the bending moment applied to the small diameter cylindrical portion 512. Further, the second bearing 92 supports the small-diameter cylindrical portion 512 so as not to contact the plurality of external teeth 510 and to overlap the fitting spline 513 in the axial direction. Even if rattling occurs in the vicinity of the spline 513, the influence of the rattling on the second bearing 92 can be reduced.

  The structure for extending the torque transmission path from the secondary pulley 45 (torque transmission mechanism) to the external tooth 510 of the counter drive gear 51 as described above may be applied to a transmission other than the CVT 40. That is, the above-described structure includes a stepped transmission or a hybrid transmission having first and second shafts arranged in parallel to each other, or a main transmission having a first shaft and a sub-transmission having a second shaft. It may be applied to a transmission including In these cases, the torque transmission mechanism that transmits torque between the first shaft and the second shaft may be a gear mechanism (gear train) or a winding transmission mechanism including a belt or a chain. .

  Next, the procedure for assembling the shim member 100 in the power transmission device 20 will be described. In the present embodiment, when the power transmission device 20 is assembled in the present embodiment, the shim member 100 is mounted on the counter drive after completion of assembly of various parts including the second bearing 92 in the housing 22a and fastening of the transaxle case 22b to the housing 22a. It is assembled to the second bearing 92 together with the gear 51.

  Specifically, the shim member 100 is temporarily fixed near the corresponding contact portion 511s of the counter drive gear 51 via grease, and the small diameter cylindrical portion 512 of the counter drive gear 51 is contacted by the shim member 100. It is inserted into the inner race 92i of the second bearing 92 so as to contact the end surface of the contact portion 511s and the end surface of the inner race 92i. After the counter drive gear 51 and the shim member 100 are assembled to the inner race 92 i of the second bearing 92 in this way, the secondary shaft 44 included in the assembled CVT assembly is fitted to the counter drive gear 51. As a result, the shim member 100 can be easily disposed between the inner race 92 i of the second bearing 92 and the contact portion 511 s of the counter drive gear 51.

  Further, when assembling the power transmission device 20, a plurality of shim members 100 having different thicknesses are prepared, and the distances L1, L2, L3, L4 and L5 in FIG. 2 are measured in a predetermined process. . The distance L1 is the distance between the end surface of the inner race 92i of the second bearing 92 assembled to the housing 22a and the end surface of the transaxle case 22b fastened to the housing 22a. The distance L2 is the distance between the end surface of the transaxle case 22b fastened to the housing 22a and the end surface of the outer race 91o of the first bearing 91 assembled to the secondary shaft 44 assembled in the housing 22a and the transaxle case 22b. It is. The distance L3 is the distance between the end surface of the contact portion 511s of the counter drive gear 51 and the end surface of the counter drive gear 51 that contacts the step portion 44s of the secondary shaft 44. The distance L4 is a distance between the end surface of the step 44s of the secondary shaft 44 and the end surface (end surface on the nut 91n side) of the inner race 91i of the first bearing 91 assembled to the secondary shaft 44. The distance L5 is the difference between the axial length of the inner race 91i of the first bearing 91 and the axial length of the outer race 91o. After measuring these distances L1 to L5, an interval d = L1 + L2− (L3 + L4 + L5) is calculated. Then, the shim member 100 having a thickness that matches or is closest to the distance d is selected, and temporarily fixed to the counter drive gear 51 corresponding thereto via grease. Thereby, the axial displacement of the secondary shaft 44 and the counter drive gear 51 with respect to the transmission case 22 can be kept within a very small predetermined range. When the axial length of the inner race 91i of the first bearing 91 and the axial length of the outer race 91o are the same, the measurement of the distance L5 is not necessary.

  In the power transmission device 20, the shim member 100 is disposed between the inner race 92i of the second bearing 92 and the large-diameter cylindrical portion 511 (the contact portion 511s) of the counter drive gear 51. It is not something that can be done. That is, the shim member 100 may be disposed between the housing 22a of the transmission case 22 and the outer race 91o of the second bearing 92 (A portion in FIG. 2). The shim member 100 may be disposed between the counter drive gear 51 (the end surface of the large-diameter cylindrical portion 511) and the step portion 44s of the secondary shaft (B portion in FIG. 2). Further, the shim member 100 may be disposed between the secondary shaft 44 (the end surface of the fixed sheave 45a) and the inner race 91i of the first bearing 91 (C portion in FIG. 2). The shim member 100 may be disposed between the outer race 91o of the first bearing 91 and the rear case 22c of the transmission case 22 (D portion in FIG. 2).

  As described above, the continuously variable transmission of the present disclosure includes a primary shaft (42) having a primary pulley (43), a secondary shaft (44) having a secondary pulley (45), and the primary pulley (43). A stepless belt including a transmission belt (46) wound around the secondary pulley (45), and a case (22) that houses the primary shaft (42), the secondary shaft (44), and the transmission belt (46). In the transmission (40), a drive fitted to the secondary shaft (44) so that one end abuts against a part (44s) of the secondary shaft (44) and rotates integrally with the secondary shaft (44). The secondary gear is supported by the gear (51) and the case (22, 22c). The first bearing (91) supporting the end of the shaft (44) on the secondary pulley (45) side and the case (22, 22a) are supported by the second pulley (45). A second bearing (92) for supporting the drive gear (51) fitted to the secondary shaft (44) on the side opposite to the one bearing (91), and disposed around the secondary shaft (44); And a single shim member (100) for restricting axial displacement of the secondary shaft (44) and the drive gear (51) relative to the case (22).

  In the continuously variable transmission according to the present disclosure, the drive gear is fitted to the secondary shaft such that one end thereof abuts against a part of the secondary shaft and rotates integrally with the secondary shaft. The first bearing is supported by the case to support the end portion of the secondary shaft on the secondary pulley side, and the second bearing is supported by the case, and on the opposite side of the secondary bearing from the first bearing. A drive gear fitted to the secondary shaft is supported. Thus, if the axial displacement of either the secondary shaft or the drive gear is restricted between the first bearing and the second bearing, the other axial displacement can be restricted. Therefore, in the continuously variable transmission according to the present disclosure, the axial displacement of the secondary shaft and the drive gear with respect to the case is restricted by a single shim member, thereby suppressing the inclination of the transmission belt (the axial displacement of the transmission belt). At the same time, the axial displacement of the drive gear can be restricted. As a result, it is possible to reduce the assembly process and the number of parts of the continuously variable transmission, thereby suppressing an increase in cost.

  The shim member (100) may be disposed between the inner race (92i) of the second bearing (92) and a part (511s) of the drive gear (51). In this case, since the shim member is attached to the drive gear and both are integrally assembled to the second bearing, the secondary shaft can be fitted to the drive gear, so the inner race of the second bearing and the drive gear It is possible to easily arrange the shim member between the part.

  The shim member (100) may be disposed between the case (22, 22a) and the outer race (92o) of the second bearing (92).

  Further, the shim member (100) may be disposed between the drive gear (51) and the part (44s) of the secondary shaft (44).

  The shim member (100) may be disposed between the secondary shaft (44) and the inner race (91i) of the first bearing (91).

  Further, the shim member (100) may be disposed between the outer race (91o) of the first bearing (91) and the case (22, 22c).

  The drive gear (51) includes a large-diameter cylindrical portion (511) including a plurality of external teeth (510), and the large-diameter cylinder extending in the axial direction from the large-diameter cylindrical portion (511). A small-diameter cylindrical portion (512) having a smaller diameter than the cylindrical portion (511), and the drive gear (51) is connected to the secondary shaft (44) on the inner peripheral surface of the small-diameter cylindrical portion (512). A fitting portion (513) fitted to the secondary shaft (44) so as to rotate integrally with the plurality of external teeth (510) may be formed so as not to overlap the axial direction, The fitting portion (513) may be fitted to the secondary shaft (44) so as to be separated from the secondary pulley (45) in the axial direction than the plurality of external teeth (510). The inner race (92i) of the bearing (92) A portion close to the plurality of external teeth (510) of the small-diameter cylindrical portion (512) may be supported so as not to overlap the joint portion (513) in the axial direction, and the shim member (100) Arranged between the inner race (92i) of the second bearing (92) and the large-diameter cylindrical portion (511) of the drive gear (51) so as not to contact the plurality of external teeth (510). May be.

  In such a continuously variable transmission, while suppressing an increase in the shaft length of the secondary shaft, the torque transmission path from the torque transmission mechanism to the external gear of the drive gear is extended, and from the torque transmission mechanism to the external gear of the drive gear. The rigidity of the member can be substantially reduced. Therefore, it is possible to reduce the dynamic rigidity at the meshing portion of the drive gear and the driven gear meshing with it, and to reduce the gear noise generated by the meshing of both, and to suppress the increase in the rigidity of the case of the transmission, that is, the weight. You can also. Further, by providing the fitting portion in the small diameter cylindrical portion of the drive gear, it is possible to satisfactorily reduce the rigidity of the member from the torque transmission mechanism to the external gear of the drive gear. Furthermore, the inner race of the second bearing is arranged so as not to overlap the fitting portion in the axial direction, and the second bearing supports the portions close to the plurality of external teeth of the small-diameter cylindrical portion. To reduce the influence of the rattling generated in the vicinity of the fitting portion of the drive gear with respect to, and to suppress the increase in the distance between the first and second bearings and to reduce the moment applied to the small-diameter cylindrical portion of the drive gear. it can.

  And the invention of this indication is not limited to the above-mentioned embodiment at all, and it cannot be overemphasized that various changes can be made within the range of the extension of this indication. Furthermore, the above-described embodiment is merely a specific form of the invention described in the Summary of Invention column, and does not limit the elements of the invention described in the Summary of Invention column.

  The invention of the present disclosure can be used in the manufacturing industry of continuously variable transmissions.

  20 power transmission device, 21 front cover, 22 transmission case, 22a housing, 22b transaxle case, 22c rear case, 23 starter, 23o one-way clutch, 23p pump impeller, 23s stator, 23t turbine runner, 24 damper mechanism, 25 lock-up Clutch, 30 oil pump, 31 pump body, 32 pump cover, 33 inner rotor, 34 outer rotor, 35 forward / reverse switching mechanism, 36 planetary gear mechanism, 40 continuously variable transmission (CVT), 41 input shaft, 42 primary shaft, 43 primary pulley, 43a fixed sheave, 43b movable sheave, 44 secondary shaft, 44s stepped portion, 440 spline, 45 secondary pulley, 45a solid Sheave, 45b Movable sheave, 46 Transmission belt, 47 Primary cylinder, 48 Secondary cylinder, 480 Cylinder member, 481 Nut, 49 Return spring, 50 Gear mechanism, 51 Counter drive gear, 510 External tooth, 511 Large diameter cylindrical part, 511s Contact portion, 512 Small-diameter cylindrical portion, 513 Fitting spline, 52 Counter shaft, 53 Counter driven gear, 54 Drive pinion gear, 55 Differential ring gear, 57 Differential gear, 59 Drive shaft, 91 First bearing, 91i, 92i Inner race, 91n nut, 91o, 92o outer race, 92 second bearing, 100 shim member, B1 brake, C1 clutch.

Claims (7)

A primary shaft having a primary pulley, a secondary shaft having a secondary pulley, a transmission belt wound around the primary pulley and the secondary pulley, and a case for housing the primary shaft, the secondary shaft and the transmission belt In a continuously variable transmission,
A drive gear fitted to the secondary shaft so that the one end portion abuts against a part of the secondary shaft and rotates integrally with the secondary shaft;
A first bearing supported by the case and supporting an end of the secondary shaft on the secondary pulley side;
A second bearing supported by the case and supporting the drive gear fitted to the secondary shaft on the opposite side of the secondary pulley from the first bearing;
A continuously variable transmission, comprising: a single shim member disposed around the secondary shaft and regulating axial displacement of the secondary shaft and the drive gear with respect to the case. The continuously variable transmission according to claim 1,
The shim member is a continuously variable transmission disposed between an inner race of the second bearing and a part of the drive gear. The continuously variable transmission according to claim 1,
The shim member is a continuously variable transmission disposed between the case and the outer race of the second bearing. The continuously variable transmission according to claim 1,
The shim member is a continuously variable transmission that is disposed between the drive gear and the part of the secondary shaft. The continuously variable transmission according to claim 1,
The shim member is a continuously variable transmission disposed between the secondary shaft and an inner race of the first bearing. The continuously variable transmission according to claim 1,
The shim member is a continuously variable transmission disposed between the outer race of the first bearing and the case. The continuously variable transmission according to claim 2,
The drive gear includes a large-diameter cylindrical portion including a plurality of external teeth, and a small-diameter cylindrical portion having a smaller diameter than the large-diameter cylindrical portion extending in the axial direction from the large-diameter cylindrical portion,
On the inner peripheral surface of the small-diameter cylindrical portion, a fitting portion that is fitted to the secondary shaft so that the drive gear rotates integrally with the secondary shaft overlaps the plurality of external teeth in the axial direction. It is formed so as not to become
The fitting portion is fitted to the secondary shaft so as to be separated from the secondary pulley in the axial direction than the plurality of external teeth,
The inner race of the second bearing supports a portion of the small-diameter cylindrical portion adjacent to the plurality of external teeth so as not to overlap the fitting portion in the axial direction,
The continuously variable transmission is disposed between the inner race of the second bearing and the large-diameter cylindrical portion of the drive gear so that the shim member does not contact the plurality of external teeth.

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