JP2009236294A - Belt-type continuously variable transmission - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To provide a belt-type continuously variable transmission further miniaturized by shortening the axial length of a rotating shaft. <P>SOLUTION: This belt-type continuously variable transmission includes: the rotating shaft 13 having a fixed pulley 15a fixedly provided on a periphery, a groove-like first spline groove 101a formed in an axial direction, and a fixing member mounting portion 102 having a groove portion formed in the substantially middle of the first spline groove 101a; a movable pulley 15b arranged on the periphery of the rotating shaft 13 so that the fixed pulley 15a is opposed to a sheave surface, axially slidably mounted on the rotating shaft 13, and formed with a groove-like second spline groove 101b opposed to the first spline groove 101a; and a substantially cylindrical columnar portion 110 arranged between the first spline groove 101a and the second spline groove 101b. The columnar portion 110 is axially fixed by the fixing member 120 mounted to the fixing member mounting portion 102. <P>COPYRIGHT: (C)2010,JPO&INPIT

Description

  The present invention relates to a belt type continuously variable transmission, and more particularly to a sliding structure between a fixed pulley and a movable pulley.

  The belt type continuously variable transmission transmits power from the input side to the output side via a metal belt. This belt type continuously variable transmission changes the gear ratio by changing the effective radius of the belt by moving the movable pulley in the axial direction with respect to the fixed pulley.

  In such a belt type continuously variable transmission, when the direction of torque is switched, if the movable pulley causes relative rotation with respect to the fixed pulley, the pieces constituting the belt are displaced in the rotation direction, and the metal belt is moved. It may be damaged. Therefore, it is necessary to manage these with high accuracy in order to prevent relative rotation between the fixed pulley and the movable pulley.

  Conventionally, ball spline bearings, roller spline bearings, etc. have been proposed for such a sliding structure between a fixed pulley and a movable pulley, but roller splines with a small number of parts can reduce the size and cost of the transmission. It is advantageous.

  Regarding the sliding structure using this roller spline, Patent Document 1 describes a continuously variable transmission in which the roller spline is configured to be slidable to a position where it abuts against the snap ring and the hydraulic action chamber wall surface.

Patent Document 2 describes a continuously variable transmission that regulates the axial position of a roller spline with an end face of an orthogonal groove and a washer. Furthermore, a continuously variable transmission is described that is regulated by a pair of snap rings on the inner side and the outer side in the axial direction of the roller spline.
JP 2005-127427 A JP 2006-132549 A

  However, in the roller splines described in these patent documents, the roller is in contact with and fixed to the rotating shaft at both ends in the axial direction, so that the length of the roller in the axial direction becomes long and the roller contact surface is machined. It was necessary to increase the strength.

  Further, when both ends of the roller are fixed with snap rings, a plurality of snap rings are required, so that the number of parts increases, the number of assembling steps increases, and the manufacturing cost increases.

  The present invention has been made paying attention to such problems, and is a belt-type device that can be further reduced in size by reducing the axial length of the rotating shaft without increasing the number of components. An object is to provide a step transmission.

  According to one embodiment of the present invention, the fixed pulley 15a provided in a fixed state on the outer periphery, the groove-shaped first spline groove 101a formed in the axial direction, and substantially in the middle of the first spline groove 101a. A rotating shaft 13 having a fixed member mounting groove 102 having a groove formed thereon, and a fixed pulley 15a and a sheave surface are arranged on the outer periphery of the rotating shaft 13 so as to face the rotating shaft 13 and slide in the axial direction. A movable pulley 15b that is movably mounted and has a groove-like second spline groove 101b facing the first spline groove 101a, and between the first spline groove 101a and the second spline groove 101b. A substantially cylindrical column 110 (that is, a roller spline) disposed, and the column 110 is pivoted by a fixing member 120 mounted in a fixing member mounting groove 102. Characterized in that it is fixed in direction.

  Note that the reference numerals are for reference, and are not limited to these.

  According to the present invention, the rotational torque of the fixed pulley provided in a fixed state on the rotating shaft is transmitted to the movable pulley by the cylindrical portions arranged in the first spline groove and the second spline groove, so that the number of parts is increased. In addition, the rotational deviation between the fixed pulley and the movable pulley can be managed with high accuracy, the axial length of the rotary shaft can be reduced, and the belt type continuously variable transmission can be downsized.

  Hereinafter, a belt type continuously variable transmission according to an embodiment of the present invention will be described with reference to the drawings.

<First Embodiment>
FIG. 1 is a front sectional view showing an example of the configuration of a belt type continuously variable transmission (CVT) according to a first embodiment of the present invention.

  The rotation of the output shaft 1 driven by an engine (not shown) is transmitted to a torque converter 2 as a starting device, a forward / reverse switching mechanism 3, and a continuously variable transmission mechanism 4 built in a case 9 of the continuously variable transmission. The

  The torque converter 2 includes a lockup clutch 5 that controls so-called lockup, and the lockup clutch 5 is connected to the turbine shaft 6. One side of the lock-up clutch 5 is formed as a supply chamber (hereinafter, apply chamber) 7a, and the other side is formed as an open chamber (hereinafter, release chamber) 7b. The torque converter 2 is activated by circulating the hydraulic pressure supplied into the release chamber 7b through the apply chamber 7a. On the other hand, by supplying hydraulic pressure to the apply chamber 7a and lowering the hydraulic pressure in the release chamber 7b, the lock-up clutch 5 is engaged with the front cover 8 to be in a lock-up state. By adjusting the pressure in the release chamber 7b, slip pressure control is performed so that the lock-up clutch 5 is slid intentionally.

  The forward / reverse switching mechanism 3 transmits the rotation of the turbine shaft 6 that is the output shaft of the torque converter 2 to the continuously variable transmission mechanism 4 in the forward (forward) direction, and transmits it in the reverse (reverse) direction. And a reverse brake. When hydraulic pressure is supplied to the clutch oil chamber and the forward clutch is engaged, the rotation of the turbine shaft 6 is transmitted to the continuously variable transmission mechanism 4 in the positive direction, and hydraulic pressure is supplied to the brake oil chamber to connect the reverse brake. When it is in a state, it is decelerated in the reverse direction and transmitted.

  The continuously variable transmission mechanism 4 includes an input shaft (primary shaft) 13 connected to the forward / reverse switching mechanism 3 and an output shaft (secondary shaft) 14 arranged in parallel therewith.

  A primary pulley 15 is provided on the primary shaft 13. The primary pulley 15 includes a fixed pulley 15a provided in a fixed state on the outer periphery of the primary shaft 13, and a movable pulley 15b disposed on the outer periphery of the primary shaft 13 and slidably fitted in the axial direction. By sliding the movable pulley 15b with respect to the fixed pulley 15a, the interval between the pulley surfaces with which the pulley belt 17 contacts, that is, the pulley groove width is variably formed.

  The fixed pulley 15a and the movable pulley 15b are provided with a fixed sheave surface 15c and a movable sheave surface 15d, which are formed by a circumferential plane portion, on the surfaces facing each other.

  A secondary pulley 16 is provided on the secondary shaft 14. The secondary pulley 16 includes a fixed pulley 16a provided in a fixed state on the outer periphery of the secondary shaft 14, and a movable pulley 16b that is disposed on the outer periphery of the secondary shaft 14 and is slidably fitted in the axial direction. By sliding the movable pulley 16b with respect to the fixed pulley 16a, the pulley groove width is variably formed.

  The fixed pulley 16a and the movable pulley 16b are provided with a fixed sheave surface 16c and a movable sheave surface 16d formed by circumferential plane portions on the surfaces facing each other.

  The fixed pulley 15a and the movable pulley 15b or the fixed pulley 16a and the movable pulley 16b are configured to be slidable by a sliding structure described later in FIG.

  A belt 17 is stretched between the primary pulley 15 and the secondary pulley 16. By changing the groove width of both the pulleys 15 and 16 and changing the ratio of the winding diameter with respect to each pulley 15 and 16, the rotation of the primary shaft 13 is continuously shifted to the secondary shaft 14 and transmitted. Will be.

  The rotation of the secondary shaft 14 is transmitted to the wheels via a gear train having a reduction gear and a differential device 18. In the case of a front wheel drive vehicle, the wheels are front wheels.

  Next, the configuration around the primary pulley 15 and the secondary pulley 16 will be described in more detail.

  In order to change the groove width of the primary pulley 15, a plunger partition wall 21 having a columnar portion and a disk portion is fixed to the primary shaft 13, and a primary that slidably contacts the outer peripheral side end portion of the plunger partition wall 21. The cylinder 22 is fixed to the rear side in the primary axial direction of the pulley surface of the movable pulley 15b, and a hydraulic oil chamber 23a is formed between the plunger partition wall 21 and the primary cylinder 22 (movable pulley 15b). On the other hand, a disk-shaped plate (partition wall) 24 extending in the primary axial direction is fixed to the inner surface of the primary cylinder 22 at the opening end side, and a balance oil chamber 23 b is formed between the plate 24 and the plunger partition wall 21. ing. Accordingly, the balance oil chamber 23b is provided to face the hydraulic oil chamber 23a with the plunger partition wall 21 interposed therebetween.

  In order to change the groove width of the secondary pulley 16, a plunger partition wall 26 having a tapered cylindrical portion is fixed to the secondary shaft 14, and a secondary cylinder 27 slidably contacting the outer peripheral surface of the plunger partition wall 26 is provided. The movable pulley 16b is fixed to the rear side in the secondary axial direction of the pulley surface, and a hydraulic oil chamber 28a is formed between the plunger partition wall 26 and the secondary cylinder 27 (movable pulley 16b). On the other hand, a disk-shaped plate 29 extending in the secondary axial direction is provided inside the open end of the secondary cylinder 27, and a balance oil chamber 28 b is formed between the plate 29 and the plunger partition wall 26.

  Accordingly, when the hydraulic oil is supplied into the hydraulic oil chamber 23a in the primary cylinder 22 and its volume is increased, the movable pulley 15b moves to the fixed pulley 15a side together with the primary cylinder 22 to reduce the pulley groove width, thereby increasing the volume. If it is made smaller, the pulley groove width becomes wider. Further, the movable pulley 16b, which supplies hydraulic oil into the hydraulic oil chamber 28a in the secondary cylinder 27 to increase its volume, moves to the fixed pulley 16a side together with the secondary cylinder 27, and the pulley groove width becomes narrower. If it is made smaller, the pulley groove width becomes wider.

  The case 9 includes a side cover 9a that rotatably supports one end of the primary shaft 13 via a bearing, and an oil passage 10 through which hydraulic oil flows is disposed in the side cover 9a. Here, the case 9 includes a cylindrical case body 9b that houses the forward / reverse switching mechanism 3 and the continuously variable transmission mechanism 4, a side cover 9a that closes the opening of the case body 9b, and an engine side of the case body 9b. And a converter housing 9c in which the torque converter 2 is housed.

  When the CVT is operating, the hydraulic oil in the hydraulic oil chamber 23a generates a hydraulic pressure due to the centrifugal force due to the rotation of the primary pulley 15, and the centrifugal hydraulic pressure acts in a direction to press the movable pulley 15b against the belt 17. However, centrifugal oil pressure in the direction opposite to this direction is generated in the balance oil chamber 23b. Similarly, centrifugal oil pressure is generated in the hydraulic oil chamber 28a by the rotation of the secondary pulley 16, but centrifugal oil pressure in the direction opposite to this direction is generated in the balance oil chamber 28b. In this manner, the centrifugal hydraulic pressure generated in the hydraulic oil chambers 23a and 28a is offset by the centrifugal hydraulic pressure generated in the balance oil chambers 23b and 28b, and changes in the groove widths of the primary pulley 15 and the secondary pulley 16 due to the centrifugal hydraulic pressure can be suppressed.

  Next, the sliding structure of the fixed pulley 15a and the movable pulley 15b of the first embodiment will be described in more detail.

  Hereinafter, the primary pulley 15 will be described as an example, but the configuration of the secondary pulley 16 is the same.

  FIG. 2 is a cross-sectional view of the fixed pulley 15a and the movable pulley 15b according to the first embodiment. FIG. 3 is a cross-sectional view taken along the line AA in FIG.

  As described above, the fixed pulley 15 a and the movable pulley 15 b are configured to be slidable in the axial direction of the primary shaft 13.

  Here, when the movable pulley 15b rotates relative to the fixed pulley 15a in the circumferential direction, the pieces constituting the belt 17 are displaced in the rotation direction, and the metal belt constituting the belt 17 is damaged. There is a case. Therefore, it is necessary to manage these with high accuracy in order to prevent relative rotation between the fixed pulley and the movable pulley.

  Therefore, the present embodiment has a characteristic configuration as shown in FIG. That is, the cylindrical portion 110 is mounted between the fixed pulley 15a and the movable pulley 15b so that the movable pulley 15b is slidable, and the rotational torque of the fixed pulley 15a is transmitted to the movable pulley 15b by the cylindrical portion 110. Configured.

  A spline groove 101a parallel to the axial direction is formed on the outer peripheral surface of the primary shaft 13 on the fixed pulley 15a side. A spline groove 101b is formed in the axial direction on the movable pulley 15b side so as to face the spline groove 101a. A column portion 110 having a substantially cylindrical shape (roller shape) is slidably mounted between the spline groove 101a and the spline groove 101b.

  In the present embodiment, one spline groove 101a, 101b and cylindrical portion is provided for the primary pulley 15 (or secondary pulley 16), but a plurality (for example, three at equal intervals) may be provided. By providing a plurality, it is possible to cope with a large rotational torque.

  The spline groove 101a on the primary shaft 13 side is formed with a snap ring groove 102 into which the snap ring 120 is inserted substantially in the middle in the axial direction.

  The snap ring 120 has an annular shape with a part opened, and is made of an elastic material. As shown in FIG. 3, the snap ring 120 is configured to have a slightly larger diameter than the outer periphery of the bottom surface of the snap ring groove 102 in a free state.

  The cylindrical part 110 is formed with a cylindrical part groove part 112 having an annular concave shape so as to engage with the snap ring 120 substantially in the middle of the axial direction. The cylindrical part groove 112 is configured to engage with the snap ring 120 when the cylindrical part 110 is attached to the spline grooves 101a and 101b.

  As shown in FIG. 3, the snap ring 120 is exposed from the bottom surface portion of the spline groove 101 a, but the other portion moves in the axial direction by the snap ring groove 102 formed in the circumferential direction on the primary shaft 13. Is regulated. Accordingly, when the cylindrical groove portion 112 and the snap ring 120 are engaged, the cylindrical portion 110 is restricted from moving in the axial direction and is fixed to the primary shaft 13.

  Moreover, as for the cylindrical part 110, the both ends of an axial direction are chamfered or R surface processed in the circumferential direction. In particular, a gentler surface is formed at the end portion on the fixed pulley 15a side in the axial direction.

  Thus, the cylindrical part 110 is fixed to the fixed pulley 15a integrated with the primary shaft 13, whereby the movable pulley 15b is configured to be slidable between the cylindrical part 110 and the spline groove 101b.

  Note that both end sides in the axial direction of the cylindrical portion 110 are not in contact with any of the structures of the primary pulley 15 such as the spline grooves 101 a and 101 b and the plunger partition wall 21. That is, the end of the cylindrical portion 110 on the fixed pulley 15a side in the axial direction is disposed at a predetermined interval without abutting against the back side of the spline grooves 101a and 101b. Similarly, the end of the cylindrical portion 110 on the plunger partition wall 21 side in the axial direction is arranged at a predetermined interval without abutting against the plunger partition wall 21. As a result, it is not necessary to process the back end portions of the spline grooves 101a and 101b, and it is not necessary to increase the required hardness on both end sides in the axial direction of the cylindrical portion 110.

  As described above, the cylindrical portion 110 is formed in the snap ring 120 that is a fixing member, the snap ring groove 102 in which the snap ring 120 that is the fixing member is mounted, and the cylindrical portion 110, and is the snap ring that is the fixing member. A cylindrical portion 112 that is a groove that engages with the cylindrical portion 110, and is fixed in the axial direction by the snap ring 120, the snap ring groove 102, and the cylindrical portion groove 112, and the primary pulley 15 is provided at both axial end surfaces of the cylindrical portion 110. Are arranged at a predetermined interval from the members constituting the.

  Next, a method for assembling the primary pulley 15 of the present embodiment will be described.

  First, the snap ring 120 is attached to the primary shaft 13 and the fixed pulley 15a fixed. The snap ring 120 is configured such that the entire diameter of the snap ring 120 is larger than that of the primary shaft 13 when the opening portion is enlarged by a snap ring pliers or the like.

  Next, the movable pulley 15 b is assembled to the primary shaft 13. The movable pulley 15b is inserted into the primary shaft 13 from the plunger partition wall 21 side. At this time, the spline groove 101a of the primary shaft and the spline groove 101b of the movable pulley 15b are assembled so as to face each other.

  Next, the cylindrical portion 110 is inserted into the spline grooves 101a and 101b. As described above, the cylindrical portion 110 is chamfered at both ends in the axial direction. Therefore, by pressing the snap ring 120 by this chamfered portion and reducing the snap ring 120 in the radial direction, the cylindrical portion 110 is moved in the direction of the fixed pulley 15a while the snap ring 120 is housed in the snap ring groove 102. And when the cylinder part groove part 112 of the cylinder part 110 moves to the position which opposes the snap ring 120, the snap ring 120 expands to radial direction by the elasticity. Thereby, the cylindrical part groove part 112 and the snap ring 120 engage.

  Thereafter, members such as the plunger partition wall 21 are assembled. Thereby, the movable pulley 15b is assembled to the fixed pulley 15a integrated with the primary shaft 13, and the assembly of the primary pulley 15 is completed.

  As described above, the end of the spline grooves 101a and 101b on the fixed pulley 15a side in the axial direction is chamfered larger than the plunger partition wall 21 side, thereby reducing the snap ring 120 in the radial direction. It is configured to be able to be made. When the cylindrical part 110 has such a shape, workability when the cylindrical part 110 is assembled to the primary pulley is improved. In this case, the direction when assembling the cylindrical portion 110 is determined as one direction, but both ends of the cylindrical portion 110 may be chamfered so that the snap ring 120 can be reduced in the radial direction. Good. Thereby, it becomes unnecessary to consider the assembly direction of the cylindrical part 110, and workability | operativity further improves.

  As described above, the cylindrical groove portion 112 is formed in an annular shape in the week direction of the cylindrical portion 110, but it is not necessary to be in an annular shape. You may comprise so that the snap ring 120 may be diameter-fit by the groove-shaped part formed in the circumferential direction part of the cylindrical part 110. FIG. In this case, it is necessary to determine the direction and assemble so that the groove-like portion correctly engages with the snap ring 120.

  Next, effects of the first embodiment of the present invention configured as described above will be described.

  In the embodiment of the present invention, the cylindrical portion 110 having a cylindrical shape is provided in the spline grooves 101a and 101b provided in the primary shaft 13 and the movable pulley 15b. Thereby, generation | occurrence | production of the relative rotation (rotation play) of the movable pulley 15b with respect to the fixed pulley 15a can be suppressed. Then, by managing the processing accuracy of the spline grooves 101a and 101b and the cylindrical portion 110, it becomes possible to manage this rotational play with high accuracy.

  Moreover, since it is not necessary for the cylindrical part 110 to contact | abut the axial direction edge part to the structure which comprises the primary pulley 15, the axial direction length of the primary axis | shaft 13 (or secondary axis | shaft 14) is made small. It becomes possible. As a result, the belt type continuously variable transmission can be downsized in the axial direction.

  Further, since the cylindrical portion 110 is fixed in the axial direction only by the snap ring 120, the number of parts can be reduced. Furthermore, with such a configuration, it is not necessary to abut both ends of the cylindrical portion 110 against, for example, the primary shaft 13 or the plunger partition wall 21, and the required hardness of the cylindrical portion 110 can be reduced. Moreover, it is not necessary to perform processing for abutting the cylindrical portion against the axially inner side end portions of the spline grooves 101a and 101b. As a result, the manufacturing cost can be reduced.

  In addition, since members that are fixed at both ends in the axial direction of the cylindrical portion 110 are not required, these members are not necessary, and it is not necessary to increase the processing accuracy in the axial direction, and the manufacturing cost can be reduced. It becomes.

Second Embodiment
Next, a second embodiment of the present invention will be described.

  In the first embodiment described above, the cylindrical portion is fixed in the axial direction by the snap ring, but in the second embodiment, the cylindrical portion is fixed in the axial direction by a pin. is there. In addition, the same code | symbol is attached | subjected to the structure same as 1st Embodiment, and the description is abbreviate | omitted.

  FIG. 4 is a cross-sectional view of the fixed pulley 15a and the movable pulley 15b according to the second embodiment. FIG. 5 is a top view, a side view, and a cross-sectional view taken along line AA of FIG.

  Hereinafter, the primary pulley 15 will be described as an example, but the configuration of the secondary pulley 16 is the same.

  As in the first embodiment described above, a column portion 210 having a substantially cylindrical shape (roller shape) is mounted between the fixed pulley 15a and the movable pulley 15b, and the movable pulley 15b is configured to be slidable. In addition, the cylindrical portion 110 is configured to transmit the rotational torque of the fixed pulley 15a to the movable pulley 15b.

  Note that one spline groove 101a, 101b and cylindrical portion 110 is provided for the primary pulley 15 (or the secondary pulley 16), but a plurality (for example, three at equal intervals) may be provided. By providing a plurality, it is possible to cope with a large rotational torque.

  In the present embodiment, a pin groove 202 for fixing the pin 220 by fitting the pin 220 is formed in the spline groove 101a on the primary shaft 13 side substantially in the middle of the axial direction.

  The pin 220 has a substantially cylindrical shape, and is a fixing member for fixing the columnar part 210 in the axial direction.

  The cylindrical part 210 is formed with a cylindrical part groove 212 for fixing the pin 220 by fitting the pin 220 approximately in the middle in the axial direction. The cylindrical portion 210 is attached to the spline groove 101a via the pin 220. Therefore, by fitting the pin 220 into the pin groove 202 and the cylindrical groove portion 212, the cylindrical portion 210 is restricted from moving in the axial direction and is fixed to the primary shaft 13.

  In addition, the cylindrical portion 210 has both ends in the axial direction chamfered or rounded to form smooth surfaces with respect to the axial direction at both ends.

  As described above, the cylindrical portion 210 is fixed to the fixed pulley 15a integrated with the primary shaft, so that the movable pulley 15b is configured to be slidable between the cylindrical portion 210 and the spline groove 101b.

  Note that both end sides of the cylindrical portion 210 in the axial direction are not in contact with any of the structures of the primary pulley 15 such as the spline grooves 101a and 101b and the plunger partition wall 21. That is, the end of the cylindrical portion 210 on the fixed pulley 15a side in the axial direction is disposed at a predetermined interval without abutting against the back side of the spline grooves 101a and 101b. Similarly, the end of the cylindrical portion 110 on the plunger partition wall 21 side in the axial direction is arranged at a predetermined interval without abutting against the plunger partition wall 21. As a result, it is not necessary to process the back end portions of the spline grooves 101a and 101b, and it is not necessary to increase the required hardness on both end sides in the axial direction of the cylindrical portion 210.

  As described above, the cylindrical portion 210 is formed in the pin 220 that is a fixing member, the pin groove 202 in which the pin 220 that is the fixing member is mounted, and the cylindrical portion 110 and is fitted to the pin 220 that is the fixing member. A cylindrical portion 212 that is a groove portion to be fixed, and is fixed in the axial direction by the pin 220, the pin groove 202, and the cylindrical portion groove 212, and a member constituting the primary pulley 15 at both axial end surfaces of the cylindrical portion 210 Are arranged at a predetermined interval.

  As shown in FIG. 5, the pin groove 202 of the primary shaft 13 has a substantially long rectangular concave groove. The pin groove 202 has a width in the axial direction substantially the same as the diameter of the pin 220, but a width in the direction perpendicular to the axis is slightly larger than the diameter of the pin 220. On the other hand, the columnar groove portion 212 of the columnar portion 210 has a cylindrical concave groove that is substantially the same as the pin 220. That is, the spline groove 101a is fitted with no gap only in the axial direction, and play is generated in the direction perpendicular to the axis. On the other hand, the pin 220 is fitted to the cylindrical portion 210 without any gap.

  The cylindrical portion 210 transmits the rotational torque of the fixed pulley 15a to the movable pulley 15b. This rotational torque acts between the cylindrical portion 210 and the spline grooves 101a and 101b. Here, in the pin groove 202 of the pin 220, play is generated in the direction perpendicular to the shaft (rotation direction), so that the rotational torque does not directly act on the pin 220.

  By adopting such a configuration, excessive torque does not act on the pin 220, so that damage to the pin 220 can be prevented, and it is not necessary to increase the required hardness of the pin 220, the pin groove 202, and the cylindrical groove portion 212. Manufacturing cost can be reduced.

  Next, a method for assembling the primary pulley 15 of the present embodiment will be described.

  First, the pin 220 is fitted into the pin groove 202 formed in the spline groove 101a of the primary shaft 13 by a method such as press fitting. Thereby, the pin 220 is fixed to the spline groove 101a.

  Next, the cylindrical portion 210 is fitted to the pin 220 fitted in the pin groove 202 by a method such as press fitting. As a result, the pin 220 is fixed to the cylindrical portion 210.

  Next, the movable pulley 15 b is assembled to the primary shaft 13. The movable pulley 15b is inserted into the primary shaft 13 from the plunger partition wall 21 side. The spline groove 101a of the primary shaft and the spline groove 101b of the movable pulley 15b are inserted so as to face each other, and the cylindrical portion 210 is slid in the spline groove 101b and moved to the fixed pulley 15a side. As described above, since the end of the cylindrical portion 220 in the axial direction is chamfered, the working efficiency at the time of assembly is improved.

  Note that the diameter of the primary shaft 13 near the fixed pulley 15a (indicated by X in FIG. 4) is larger than the diameter of the primary shaft 13 near the spline groove 101a (indicated by Y in FIG. 4). When the 15b is inserted into the spline groove, the portion X can be inserted without contacting the cylindrical portion 210 fixed to the spline groove 101a.

  Thereafter, members such as the plunger partition wall 21 are assembled. Thereby, the movable pulley 15b is assembled to the fixed pulley 15a integrated with the primary shaft 13, and the assembly of the primary pulley 15 is completed.

  Next, the effects of the second embodiment of the present invention configured as described above will be described.

  In the present embodiment, similarly to the first embodiment described above, the spline grooves 101a and 101b provided in the primary shaft 13 and the movable pulley 15b are provided with the cylindrical portion 210 having a cylindrical shape. Thereby, generation | occurrence | production of the relative rotation (rotation play) of the movable pulley 15b with respect to the fixed pulley 15a can be suppressed. Then, by managing the processing accuracy of the spline grooves 101a and 101b and the cylindrical portion 110, it becomes possible to manage this rotational play with high accuracy.

  Moreover, since it is not necessary for the cylindrical part 210 to contact | abut the axial direction edge part to the structure which comprises the primary pulley 15, the axial direction length of the primary axis | shaft 13 (or secondary axis | shaft 14) is made small. It becomes possible. As a result, the belt type continuously variable transmission can be downsized in the axial direction.

  Moreover, since the cylindrical part 210 is being fixed to the axial direction only by the pin 220, it becomes possible to reduce a number of parts. Furthermore, with such a configuration, it is not necessary to abut both ends of the cylindrical portion 210 against, for example, the primary shaft 13 or the plunger partition wall 21, and the required hardness of the cylindrical portion 210 can be reduced.

  Moreover, it is not necessary to perform processing for abutting the cylindrical portion to the axially inner end portions of the spline grooves 101a and 101b. As a result, the manufacturing cost can be reduced.

  In addition, since members that are fixed at both ends in the axial direction of the cylindrical portion 210 are not required, these members are not necessary, and it is not necessary to increase the processing accuracy in the axial direction, and the manufacturing cost can be reduced. It becomes.

  It goes without saying that the present invention is not limited to the above-described embodiments, and includes various modifications and improvements that can be made within the scope of the technical idea.

It is front sectional drawing which shows an example of a structure of the belt-type continuously variable transmission (CVT) of this embodiment. It is sectional drawing of the fixed pulley 15a and movable pulley 15b of 1st Embodiment. It is AA sectional drawing of a 1st embodiment. It is sectional drawing of the fixed pulley 15a and movable pulley 15b of 2nd Embodiment. It is the top view of the cylindrical part 210 of 2nd Embodiment, a side view, and AA sectional drawing of FIG.

Explanation of symbols

1 Output shaft 2 Torque converter 13 Input shaft (primary shaft)
14 Output shaft (secondary shaft)
DESCRIPTION OF SYMBOLS 15 Primary pulley 15a Fixed pulley 15b Movable pulley 16 Secondary pulley 16a Fixed pulley 16b Movable pulley 17 Belt 21 Plunger partition wall 26 Plunger partition wall 101a Spline groove 101b Spline groove 102 Snap ring groove 110 Cylinder part 112 Cylinder part groove part 120 Snap ring 202 Pin groove 210 Cylinder part 212 Cylinder part groove part 220 pin

Claims (7)

A rotating shaft provided with a fixed sheave and a first spline on an outer periphery of the shaft, and provided with a fixing member mounting groove formed on an inner diameter of the first spline;
A movable pulley formed with a second spline that is axially slidable and non-rotatable with the first spline;
A cylindrical portion that is provided between the first spline and the second spline and receives torque transmitted to the rotating shaft together with the first spline and the second spline;
With
The belt-type continuously variable transmission is characterized in that the cylindrical portion is fixed in the axial direction by a fixing member mounted in the fixing member mounting groove.   Both end sides in the axial direction of the cylindrical portion are provided at positions that are not in contact with the radial end portions of the first spline and the second spline within the sliding range of the first spline and the second spline. The belt type continuously variable transmission according to claim 1. The fixing member mounting groove has a groove formed in the circumferential direction of the rotary shaft in the approximate middle of the first spline,
The fixing member is an annular elastic body attached to the groove portion,
The cylindrical part has a cylindrical part groove part in which a groove to be engaged with the fixing member is formed,
The belt-type continuously variable transmission according to claim 1 or 2, wherein the cylindrical portion is fixed in an axial direction by engaging the cylindrical portion groove portion when the fixing member is in a free state.   The belt-type continuously variable transmission according to any one of claims 1 to 3, wherein the cylindrical portion is formed with a chamfered portion in the circumferential direction at an end portion in the axial direction.   5. The belt-type continuously variable transmission according to claim 3, wherein the cylindrical part has a cylindrical part groove part in which an annular groove is formed in a circumferential direction substantially in the middle of the axial direction. The fixing member mounting groove has a groove formed substantially in the middle of the second spline,
The fixing member is a substantially cylindrical pin fitted in the groove portion,
The cylindrical part has a cylindrical part groove part in which a groove to be fitted with the fixing member is formed,
The belt-type continuously variable transmission according to claim 1, wherein the cylindrical portion is fixed in the axial direction by fitting the pin into the groove portion and the cylindrical portion groove portion.   6. The belt-type device according to claim 5, wherein the fixing member mounting groove portion has substantially the same width as the pin in the axial direction and a width larger than the pin in the direction perpendicular to the shaft. Step transmission.

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