JP2011122677A - Pulley structure in belt driven continuously variable transmission - Google Patents

Abstract

A driven pulley that is formed of a fixed pulley half and a movable pulley half and is provided on a driven shaft, a drive pulley provided on a drive shaft, and an endless V-belt that is wound around the drive pulley and the driven pulley. In the belt type continuously variable transmission including the above, the coupling strength between the pulley face and the pulley boss in the driven pulley is further increased.
At least one of a fixed pulley half 49 and a movable pulley half is disposed in a circumferential direction with a pulley face 56 formed in a dish shape of aluminum or an aluminum alloy and in contact with a V-belt. A plurality of coupling protrusions 61 are provided on the outer periphery, and the first recesses 62 formed shallower and the second recesses 63 formed deeper than the first recesses 62 are alternately arranged in the circumferential direction. The pulley boss 55 is formed between the portions 61, and the outer periphery of the pulley boss 55 is cast on the inner periphery of the pulley face 56.
[Selection] Figure 4

Description

  The present invention comprises a fixed pulley half that is fixedly arranged at a predetermined position along the axis of the driven shaft, and a movable pulley half that can move toward and away from the fixed pulley half, and is provided on the driven shaft. In particular, a belt-type continuously variable transmission comprising a driven pulley, a driving pulley provided on a driving shaft having an axis parallel to the driven shaft, and an endless V-belt wound around the driving pulley and the driven pulley. The invention relates to the improvement of the structure of the driven pulley.

  In conventional belt type continuously variable transmissions, it is common to form a fixed pulley half and a movable pulley half in a driven pulley by riveting a plurality of locations on the inner periphery of the pulley face to pulley bosses. In such a structure, the thickness of the fixed pulley half and the movable pulley half is increased at the riveting portion, which may increase the weight. Therefore, in the one disclosed in Patent Document 1, the pulley face made of aluminum material and the pulley boss made of iron material are arranged on the outer periphery of the pulley boss provided with a plurality of coupling protrusions arranged at equal intervals. The fixed pulley half and the movable pulley half are configured by casting in the inner periphery of the two and integrally connecting them.

JP 2008-240944 A

  According to the one disclosed in Patent Document 1, it is possible to increase the coupling strength between the pulley face and the pulley boss without causing an increase in wall thickness, but further improvement in the coupling strength is desired.

  The present invention has been made in view of such circumstances, and an object of the present invention is to provide a pulley structure in a belt-type continuously variable transmission that can further increase the coupling strength between a pulley face and a pulley boss.

  In order to achieve the above object, the present invention comprises a fixed pulley half that is fixedly arranged at a predetermined position along the axis of the driven shaft, and a movable pulley half that can move toward and away from the fixed pulley half. And a driven pulley provided on the driven shaft, a driving pulley provided on a driving shaft having an axis parallel to the driven shaft, and an endless V-belt wound around the driving pulley and the driven pulley. In the continuously variable transmission, at least one of the fixed pulley half and the movable pulley half is formed in a dish shape with aluminum or an aluminum alloy and spaced apart from a pulley face contacting the V-belt in the circumferential direction. A plurality of coupling protrusions arranged on the outer periphery are provided on the outer periphery and are formed deeper than the first recess and the first recess formed shallow. And having two pulley recesses arranged alternately in the circumferential direction and an iron pulley boss formed between the coupling protrusions, and the outer periphery of the pulley boss is cast into the inner periphery of the pulley face. It is characterized by.

  In addition to the configuration of the first feature, the present invention has a second feature that a screw hole for attaching an auxiliary machine is provided at a position avoiding the coupling protrusion of the pulley boss.

  According to a third feature of the present invention, in addition to the configuration of the second feature, the screw hole is provided in the pulley boss inward of the inner periphery of the pulley face coupled to the pulley boss. To do.

  According to the present invention, in addition to the configuration of the second or third feature, the accessory is a pulsar ring that is attached to the stationary pulley half of the driven pulley so as to face a sensor that detects the number of rotations. The fourth feature.

  According to the present invention, in addition to the configuration of the fourth feature, reinforcing portions extending in the circumferential direction of the pulley face are provided at a plurality of locations near the outer periphery of the pulley face, and the first recess is provided between the reinforcing portions. A fifth feature is that the pulley boss is formed on the outer periphery of the pulley boss at a position corresponding to.

  According to the present invention, in addition to the configuration of the fifth feature, the reinforcing portion can be subjected to local weight reduction processing for correcting the circumferential balance of the pulley face. The sixth feature is that it is also formed thick.

  According to the present invention, in addition to any of the configurations of the first to sixth features, the pulley boss of the movable pulley half is subjected to heat treatment and plating before being coupled to the pulley face. 7 features.

  In the present invention, in addition to any of the first to seventh features, each coupling protrusion on the outer periphery of the pulley boss is formed in a trapezoidal shape, and the circumferential center of the coupling protrusion on both sides of the first recess is formed. An angle between the passing straight lines is set to be smaller than an angle between straight lines passing through the circumferential center of the coupling protrusions on both sides of the second recess, and a connecting portion between each of the coupling protrusions and the first recess and the second recess is It is an eighth feature that it is formed in a similar curved shape.

  Further, according to the present invention, in addition to any of the configurations of the first to eighth features, the pulley face constituting the fixed pulley half and a part of the movable pulley half are formed in the same shape. Is the ninth feature.

  The crankshaft 26 of the embodiment corresponds to the drive shaft of the present invention, the output shaft 42 of the embodiment corresponds to the driven shaft of the present invention, and the pulsar ring 65 of the embodiment corresponds to the auxiliary machine of the present invention. To do.

  According to a first aspect of the present invention, at least one of the fixed pulley half and the movable pulley half is formed in a dish shape with aluminum or an aluminum alloy and is in a dish shape, and in a circumferential direction A plurality of coupling protrusions arranged at intervals are provided on the outer periphery, and first recesses formed shallower and second recesses formed deeper than the first recesses are alternately arranged in the circumferential direction. A pulley boss made of iron formed between the coupling protrusions, and the outer periphery of the pulley boss is cast on the inner periphery of the pulley face. 1 The coupling force between the coupling protrusions in which the recesses are formed is increased, and the adhesion of the pulley face and the pulley boss can be enhanced to improve the coupling strength. It is possible to reduce the bending strain of the outer periphery of the pulley boss due to such a belt lateral pressure on.

  According to the second feature of the present invention, the pulley boss is provided with a screw hole at a position avoiding the outer peripheral joint protrusion, and the auxiliary machine is attached by the screw hole, so that a plurality of joint protrusions are provided. It is possible to prevent stress concentration due to attachment of the auxiliary machine to the outer periphery of the pulley boss.

  According to the third aspect of the present invention, the screw hole is provided in the pulley boss so as to be located inward of the inner periphery of the pulley face coupled to the pulley boss. A reduction in the bonding strength of the face can be prevented.

  According to the fourth feature of the present invention, even if the diameter of the pulsar ring is increased in order to increase the rotational speed detection accuracy of the driven pulley, the coupling portion of the pulley boss and the pulley face is not affected. The degree of freedom of sensor placement can be increased while maintaining the strength.

  According to the fifth feature of the present invention, the first recess is disposed at a position corresponding to the space between the plurality of reinforcing portions extending in the circumferential direction of the pulley face and provided near the outer periphery of the pulley face. In the part where the first and second recesses are not provided, a shallow first recess is formed between the two, so that the connecting force between the coupling protrusions is increased to reinforce the pulley face. It is possible to equalize the distortion of the pulley face due to the belt side pressure in the circumferential direction while avoiding an increase in weight due to being provided.

  According to the sixth aspect of the present invention, it is possible to perform local weight reduction processing for correcting the circumferential balance of the pulley face by increasing the thickness of the reinforcing portion.

  According to the seventh feature of the present invention, the pulley boss of the movable pulley half is subjected to heat treatment and plating treatment, so that it is possible to improve the strength of the pulley boss and to reinforce the coupling portion with the pulley face. In combination, the strength of the pulley face can be increased.

  According to the eighth feature of the present invention, each coupling protrusion has a trapezoidal shape, and the angle between straight lines passing through the circumferential center of the coupling protrusion on both sides of the first recess is the coupling protrusion on both sides of the second recess. This is smaller than the angle between the straight lines passing through the center in the circumferential direction, and the connecting portion between each coupling protrusion and the first and second recesses is formed in a similar curved shape, so that the hot water area during casting is secured. Thus, the coupling strength between the pulley boss and the pulley face can be further increased.

  Furthermore, according to the ninth feature of the present invention, the fixed pulley half and the movable pulley half have the same pulley face, so that the die when casting the pulley face is fixed while casting the outer periphery of the pulley boss. The production cost can be reduced by sharing the pulley half and the movable pulley half.

It is a left view of a scooter type motorcycle. It is a left view of a power unit and a rear wheel. FIG. 3 is an enlarged view of main parts of FIG. 2. FIG. 4 is a front view of the fixed pulley half viewed from the direction of arrows 4-4 in FIG. 3 with the pulsar ring omitted.

  Hereinafter, embodiments of the present invention will be described with reference to the accompanying drawings.

  First, in FIG. 1, a vehicle body frame F of a scooter type motorcycle having a low floor type floor 11 includes a head pipe 13 that supports a front fork 12 that pivotally supports a front wheel WF, and a front end mounted on the head pipe 13. A pair of left and right side frames 14 to which the portions are joined. The side frame 14 is formed such that a down frame portion 14a hanging downward from the head pipe 13 is connected to a lower end of the down frame portion 14a and extends rearward below the floor 11 and a rear half portion is inclined rearwardly upward. The lower frame portion 14b, the rising frame portion 14c that is connected to the rear end of the lower frame portion 14b and rises upward at the rear of the floor 11, and the rear end of the rising frame portion 14c to support the vehicle seat 15. A single pipe is bent and formed integrally with a seat rail portion 14d extending in the direction.

  Between the rear part of the lower frame part 14b ... in the side frame 14 ... and the front part of the seat rail part 14d ..., it is located below the lower frame part 14b ... in the side frame 14 ... and behind the rising frame part 14c ... The rear sub-frames 16 are provided, and the pivot plates 17 are provided between the side frames 14 and the rear sub-frames 16.

  A power unit P composed of an engine E arranged on the front side of the rear wheel WR and a transmission device M arranged on the left side of the rear wheel WR swings up and down on the pivot plate 17 provided in the body frame F. The rear wheel WR is pivotally supported on the rear portion of the power unit P. The rear wheel WR is supported by the link mechanism 18 so as to be able to move.

  In FIG. 2, an engine body 19 of the engine E, which is a single-cylinder water-cooled four-cycle engine, includes a crankcase 20 formed by connecting left and right crankcase halves 20L and 20R divided into left and right parts, and the crankcase 20 A cylinder block 21 coupled to the cylinder block 21, a cylinder head 22 coupled to the cylinder block 21, and a head cover 23 coupled to the cylinder head 22. A piston 25 is slidably fitted into a cylinder bore 24 provided in the block 21. A crankshaft 26 extending in the width direction of the vehicle body frame F is rotatably supported on the crankcase 20, and the piston 25 is connected to the crankshaft 26 via a connecting rod 27 and a crankpin 28.

  The transmission M includes a belt-type continuously variable transmission 29 and a reduction gear train 30 that decelerates the output of the continuously variable transmission 29 and transmits it to the axle of the rear wheel WR, and is connected to the crankcase 20. And is housed in a transmission case 31 extending to the left side of the rear wheel WR.

  The transmission case 31 is coupled to an inner case 34 that is integrally connected to the left crank case half 20L of the crank case 20 and extends rearward, an outer case 35 that covers the inner case 34 from the outside, and a rear portion of the inner case 34. A transmission chamber 37 for accommodating the belt type continuously variable transmission 29 is formed between the inner case 34 and the outer case 35, and the reduction gear train 30 is accommodated between the inner case 34 and the gear case 36. A gear chamber 38 is formed.

  The belt type continuously variable transmission 29 is wound around a driving pulley 39 provided on the crankshaft 26 as a driving shaft, a driven pulley 40 provided on an output shaft 42 as a driven shaft, and the driving pulley 39 and the driven pulley 40. The drive pulley 39 is provided at one end of the crankshaft 26 that enters the transmission chamber 37 from the crankcase 20 and is parallel to the crankshaft 26. The driven pulley 40 is provided with the output shaft 42 that is rotatably supported by the inner case 34, the outer case 35, and the gear case 36.

  The drive pulley 39 includes a fixed pulley half 43 fixed to the crankshaft 26 and a movable pulley half 44 that can be moved toward and away from the fixed pulley half 43. The movable pulley half 44 includes a crankshaft. It is driven in the axial direction by a centrifugal force acting on a weight 46 disposed between the ramp plate 45 fixed to 26 and the movable pulley half 44.

  Referring also to FIG. 3, the driven pulley 45 enables a fixed pulley half 49 fixedly arranged at a predetermined position along the axis of the output shaft 42, and the proximity and separation of the fixed pulley half 49. The movable pulley half 50 and the fixed pulley half 49 and the movable pulley half 50 are wound around the V belt 41. In addition, a torque cam mechanism 51 that applies a component force in the axial direction between the pulley halves 49 and 50 according to the relative rotational phase difference between the movable pulley half 50 and the fixed pulley half 49 includes the fixed pulley half 49 and The movable pulley half 50 is provided between the movable pulley half 50 and is elastically biased toward the fixed pulley half 49 by the coil spring 52. Between the fixed pulley half 49 and the output shaft 42, the engine A centrifugal clutch 53 is provided that enters a power transmission state as the rotational speed exceeds the set rotational speed.

  At least one of the fixed pulley half 49 and the movable pulley half 50, both in this embodiment, are configured according to the present invention, and the fixed pulley half 49 is capable of relative rotation of the output shaft 42. As shown in the figure, the iron inner cylinder 54 that coaxially surrounds the output shaft 42, a pulley boss 55 that is integrally provided at one end of the inner cylinder 54 and projects outward in the radial direction, and aluminum or an aluminum alloy are formed in a dish shape. The pulley face 56 is in contact with the V belt 41, and the outer periphery of the pulley boss 55 is cast on the inner periphery of the pulley face 56. The movable pulley half 50 includes an iron outer cylinder 57 that allows the inner cylinder 54 to be slidably fitted so as to be capable of relative rotation about the axis and relative movement in the axial direction, and an end of the outer cylinder 57. A pulley boss 58 that is integrally provided and projects outward in the radial direction, and a pulley face 59 that is formed in a dish shape from aluminum or an aluminum alloy and that contacts the V-belt 41. The outer periphery of 58 is cast.

  Referring also to FIG. 4, a plurality of, for example, eight coupling protrusions 61, 61,... Are arranged on the outer periphery of the pulley boss 55 in the fixed pulley half 49 of the driven pulley 40 at intervals in the circumferential direction. The first and second recesses 62, 62,... Formed shallower and the second recesses 63, 63, formed deeper than the first recesses 62, 62,. Are formed alternately in the circumferential direction.

  In addition, each of the coupling protrusions 61, 61... Is formed in a trapezoidal shape, and an angle α1 between straight lines passing through the circumferential centers of the coupling protrusions 61, 61 on both sides of the first recess 62 is the second recess. 63 is set smaller than the angle α2 between the straight lines passing through the circumferential center of the coupling protrusions 61, 61 on both sides of the 63, the coupling protrusions 61, 61..., The first recess 62. Are formed in a similar bent shape.

  The pulley face 56 is formed in a dish shape having a plurality of ribs 56a, 56a,... Which are radially extended by connecting between the outer peripheral portion and the inner peripheral portion and arranged at equal intervals in the circumferential direction. Reinforcing portions 56b, 56b... Extending in the circumferential direction are provided at a plurality of, for example, four locations near the outer periphery of the pulley face 56, and the first recesses 62, 62. Formed on the outer periphery of the pulley boss 55 at positions corresponding to each other.

  Moreover, the reinforcing portions 56b, 56b,... Can be subjected to local weight reduction processing for correcting the circumferential balance of the pulley face 56, for example, perforation processing, and are thicker than the periphery of the reinforcing portions 56b, 56b,. It is formed in meat.

  Further, for example, a pair of screw holes 66, 66 for attaching a pulsar ring 65 as an auxiliary machine is provided at a position where the pulley boss 55 avoids the coupling protrusions 61, 61. Are provided on the pulley boss 55 inward of the inner periphery of the pulley face 56 in a state of being coupled to the pulley boss 55, and the pulsar ring 65 is connected to the pulley boss by bolts 69 screwed into the screw holes 66. 55 is attached.

  As clearly shown in FIG. 3, the sensor 67 for detecting the rotational speed of the driven pulley 40 is attached to the inner surface of the inner case 34 in the transmission case 31 so as to face the outer periphery of the pulsar ring 65.

  The coupling structure of the pulley boss 58 and the pulley face 59 in the movable pulley half 50 is the same as the coupling structure of the pulley boss 55 and the pulley face 56 in the fixed pulley half 49, and detailed description thereof is omitted. The outer cylinder 57 that is integral with the pulley boss 58 is subjected to heat treatment and plating treatment, for example, hard chrome plating for rust prevention, before being coupled to the pulley face 59.

  Moreover, the pulley face 59 of the movable pulley half 50 has a plurality of ribs 59a and a plurality of reinforcing portions 59b, and is formed in the same shape as the pulley face 56 of the fixed pulley half 49 as shown in FIG. Is done.

  Referring to FIG. 3, the torque cam mechanism 51 is provided between the inner cylinder 54 of the fixed pulley half 49 and the outer cylinder 57 of the movable pulley half 50, and the centrifugal clutch 53 is A drive plate 68 provided between the inner cylinder 54 of the pulley half 49 and the output shaft 42, constituting a part of the centrifugal clutch 53 and coaxially coupled to the inner cylinder 54 so as not to be relatively rotatable, and the movable A coil spring 52 surrounding the outer cylinder 57 of the movable pulley half 50 is contracted between the pulley half 50 and the pulley half 50.

  Thus, the axial distance between the fixed pulley half 49 and the movable pulley half 50 in the driven pulley 40 is such that the axial force generated by the torque cam mechanism 51, the axial elastic force generated by the coil spring 52, and the fixed It is determined by the balance with the force from the V-belt 41 acting in the direction of separating the pulley half 49 and the movable pulley half 50, and the movable pulley half 44 is brought close to the fixed pulley half 43 in the drive pulley 39. Thus, when the winding radius of the V belt 41 around the driving pulley 39 is increased, the winding radius of the V belt 41 around the driven pulley 45 is decreased.

  One end portion of the axle 70 of the rear wheel WR penetrates the gear case 36 in an airtight manner and enters the transmission case 31, and one end portion of the axle 70 is rotatably supported by the inner case 34 and the gear case 36. A reduction gear train 30 provided between the output shaft 42 and the axle 70 is housed in the gear chamber 38.

  A swing arm 71 connected to the crankcase 20 of the engine body 19 is disposed on the right side of the rear wheel WR, and the other end portion of the axle 70 is rotatably supported on the rear portion of the swing arm 71. Further, as shown in FIG. 1, a rear cushion unit 72 is provided between the rear portion of the inner case 34 of the transmission case 31 and the rear portion of the left seat rail portion 14 d in the vehicle body frame F.

  Paying attention to FIG. 2, an outer rotor 73 is fixed to the other end portion of the crankshaft 26 rotatably passing through the right crankcase half 20 </ b> R in the crankcase 20, and constitutes a generator 75 together with the outer rotor 73. Thus, the inner stator 74 surrounded by the outer rotor 73 is fixed to the right cover 76 fastened to the right crankcase half 20R so as to cover the generator 75.

  By the way, an intake valve (not shown) for controlling intake air to the combustion chamber 77 formed between the cylinder block 21 and the cylinder head 22 with the top of the piston 25 facing, and exhaust gas from the combustion chamber 77 are controlled. A valve operating device 78 that opens and closes an exhaust valve (not shown) is accommodated between the cylinder head 22 and the head cover 23, and a cam shaft 79 provided in the valve operating device 78 has an axis parallel to the crankshaft 26. It is supported on the cylinder head 22 so as to be able to rotate around. Power from the crankshaft 26 is transmitted to the camshaft 79 through the timing transmission mechanism 65 at a reduction ratio of 1/2.

  An air intake system 81 is connected to the upper side surface of the cylinder head 22 in the engine body 19 and has an air cleaner 82 disposed on the transmission case 31 and supported by the transmission case 31 at the upstream end. The intake system 81 includes the air cleaner 82, an inlet pipe 83 whose upstream end is connected to the air cleaner 82, and a throttle body 84 provided between the downstream end of the inlet pipe 83 and the cylinder head 22. A fuel injection valve 85 for injecting fuel into the air measured in step 1 is attached to the cylinder head 22.

  Further, an exhaust system 86 connected to the lower side surface of the cylinder head 22 is connected to the lower portion of the cylinder head 22 and extends from the lower right side of the engine body 19 to the right side of the rear wheel WR. The exhaust muffler 88 is connected to the exhaust pipe 87 and arranged on the right side of the rear wheel WR.

  Referring to FIG. 2, a cooling air inlet 90 for cooling the belt-type continuously variable transmission 29 with air from the outside is provided in a portion of the transmission case 31 corresponding to the drive pulley 39 of the outer case 35. . A fan 91 for sucking air from the cooling air introduction port 90 into the transmission chamber 37 and diffusing into the transmission chamber 37 is integrated with the outer end surface of the fixed pulley half 43 in the drive pulley 39. Formed.

  Thus, an outside air introduction duct 93 that guides outside air to the air cleaner 82 and leads outside air to the cooling air introduction port 90 is attached to the outer case 35 in the transmission case 31 and corresponds to the cooling air introduction port 90. The outside air introduction duct 93 is divided into a purification chamber 95 formed in the filter element 94 through the cooling air introduction port 90 and a non-purification chamber 96 outside the filter element 94. A transmission case air intake 97 leading to the unpurified chamber 96 is provided at the front of 93 so as to open forward.

  Next, the operation of this embodiment will be described. At least one of the fixed pulley half 49 and the movable pulley half 50 that cooperate with the driven pulley 40 in the continuously variable transmission 29, both in this embodiment, both Are provided on the outer periphery with pulley faces 56 and 59 formed in a dish shape by aluminum or aluminum alloy and contacting the V-belt 41, and a plurality of coupling protrusions 61 arranged at intervals in the circumferential direction. The first recesses 62 formed shallowly and the second recesses 63 formed deeper than the first recesses 62 are alternately arranged in the circumferential direction so that the iron is formed between the coupling protrusions 61. Pulley bosses 55, 58, and the outer circumferences of the pulley bosses 55, 58 are cast on the inner circumferences of the pulley faces 56, 59. Among the plurality of coupling protrusions 61 on the outer periphery of the outer periphery 8, the coupling force between the coupling protrusions 61 in which the shallow first recesses 62 are formed is increased, and the pulley faces 56 and 59 and the pulley bosses 55 and 58 It becomes possible to improve the bonding strength by improving the adhesion, and the amount of bending distortion of the outer periphery of the pulley bosses 55 and 58 due to the belt side pressure applied to the pulley faces 56 and 59 can be reduced.

  By the way, the pulsar ring 65 facing the sensor 67 attached to the inner case 34 of the transmission case 31 so as to detect the rotational speed is attached to the fixed pulley half 49 of the driven pulley 40. Since the screw holes 66 for attaching the pulsar ring 65 are provided at positions avoiding the coupling protrusions 61 of the pulley boss 55, the pulley boss 55 is provided with a plurality of coupling protrusions 61 on the outer periphery of the pulley boss 55 provided with the coupling bosses 61. Stress concentration associated with the attachment of the pulsar ring 65 can be prevented.

  In addition, since the screw holes 66 are provided in the pulley boss 55 so as to be located inward of the inner periphery of the pulley face 56 in a state of being coupled to the pulley boss 55, the pulley boss 55 and the pulley face by attaching the pulsar ring 65 are provided. It is possible to prevent the 56 bond strength from being lowered.

  Further, even if the diameter of the pulsar ring 65 is increased in order to increase the rotational speed detection accuracy of the driven pulley 49, the coupling portion between the pulley boss 55 and the pulley face 56 is not affected, and the sensor is maintained while maintaining the strength of the coupling portion. The degree of freedom of arrangement 67 can be increased.

  Further, reinforcing portions 56b,... 59b,... Extending in the circumferential direction are provided at a plurality of locations near the outer periphery of the pulley faces 56, 59, and the first recesses 62 are provided with a plurality of the reinforcing portions 56b, 56b,. 59b are formed on the outer circumferences of the pulley bosses 55, 58 at positions corresponding to each other. Therefore, in the portions where the reinforcing portions 56b, 56b,... 59b, 59b,. By increasing the connection force between the coupling protrusions 61 and 61 by being formed, the pulley faces 56 and 59 are reinforced, and the weight is increased due to the reinforcements being provided on the entire circumference of the pulley bosses 55 and 58. The distortion of the pulley faces 56 and 59 due to the belt side pressure can be equalized in the circumferential direction.

  Further, the reinforcing portions 56b ... can be subjected to local weight reduction processing for correcting the circumferential balance of the pulley faces 56, 59, and are formed thicker than the periphery of the reinforcing portions 56b ..., 59b ... Therefore, it is possible to perform local weight reduction processing for correcting the circumferential balance of the pulley faces 56 and 59.

  Each of the coupling protrusions 61 is formed in a trapezoidal shape, and an angle α1 between straight lines passing through the circumferential centers of the coupling protrusions 61 on both sides of the first recess 62 is a coupling protrusion on both sides of the second recess 63. 61, 61 is set to be smaller than the angle α2 between the straight lines passing through the center in the circumferential direction, and the connecting portions between the coupling protrusions 61, the first recesses 62, and the second recesses 63 have a similar curved shape. Since it is formed, it is possible to secure a hot water area during casting and to further increase the coupling strength between the pulley bosses 55 and 58 and the pulley faces 56 and 59.

  Further, since the pulley faces 56 and 59 of the fixed pulley half 49 and the movable pulley half 50 have the same shape, the molds for casting the pulley faces 56 and 59 are fixed while casting the outer periphery of the pulley bosses 55 and 58. The production cost can be reduced by using the pulley half 49 and the movable pulley half 50 in common.

  Furthermore, since the heat treatment and the plating treatment are performed on the pulley boss 58 and the outer cylinder 57 of the movable pulley half 50 before the connection with the pulley face 59, the strength of the pulley boss 58 can be improved and the pulley face can be improved. The strength of the pulley face 59 can be increased by combining with the reinforcement of the connecting portion with the 59.

  Although the embodiments of the present invention have been described above, the present invention is not limited to the above-described embodiments, and various design changes can be made without departing from the present invention described in the claims. Is possible.

26 ... Crankshaft 29 as a drive shaft ... Belt type continuously variable transmission 39 ... Driving pulley 40 ... Driving pulley 41 ... V belt 42 ... Output shaft 49 as a driven shaft ..Fixed pulley half 50 ... movable pulley half 55, 58 ... pulley bosses 56, 59 ... pulley face 56b, 59b ... reinforcement part 61 ... coupling protrusion 62 ... first Recess 63 ... Second recess 65 ... Pulsar ring 66 ... Screw hole 67 ... Sensor

Claims (9)

  A fixed pulley half (49) fixedly arranged at a predetermined position along the axis of the driven shaft (42) and a movable pulley half (50) capable of approaching and moving away from the fixed pulley half (49). A driven pulley (40) provided on the driven shaft (42), a drive pulley (39) provided on a drive shaft (26) having an axis parallel to the driven shaft (42), and the drive pulley (39 ) And an endless V-belt (41) wound around the driven pulley (40), at least of the fixed pulley half (49) and the movable pulley half (50) One side is a pulley face (56, 59) formed in a dish shape with aluminum or aluminum alloy and contacting the V belt (41), and a plurality of circumferentially spaced apart composite faces. A plurality of coupling protrusions (61) are provided on the outer periphery, and first recesses (62) formed shallower and second recesses (63) formed deeper than the first recesses (62) are alternately arranged in the circumferential direction. In this way, the pulley bosses (55, 58) made of iron are formed between the coupling protrusions (61), and the pulley bosses (55, 58) are formed on the inner periphery of the pulley faces (56, 59). A pulley structure in a belt type continuously variable transmission, characterized in that the outer periphery is cast.   The belt-type continuously variable screw according to claim 1, wherein a screw hole (66) for attaching an auxiliary machine (65) is provided at a position avoiding the coupling protrusion (61) of the pulley boss (55). Pulley structure in a transmission.   The said screw hole (66) is provided in the said pulley boss | hub (55) inward rather than the inner periphery of the said pulley face (56) in the state couple | bonded with the said pulley boss | hub (55). Pulley structure in the belt type continuously variable transmission.   The said auxiliary machine is a pulsar ring (65) attached to the said fixed pulley half (49) of the said driven pulley (40) facing the sensor (67) which detects rotation speed. 4. A pulley structure in a belt type continuously variable transmission according to 2 or 3.   Reinforcing portions (56b, 59b) extending in the circumferential direction are provided at a plurality of locations near the outer periphery of the pulley face (56, 59), and the first recess (62) is provided between the reinforcing portions (56b, 59b). The pulley structure in the belt-type continuously variable transmission according to any one of claims 1 to 4, wherein the pulley structure is formed on an outer periphery of the pulley boss (55, 58) at a position corresponding to the position.   The reinforcing portion (56b, 59b) can be subjected to local weight reduction processing for correcting the circumferential balance of the pulley face (56, 59), and the periphery of the reinforcing portion (56b, 59b). 6. A pulley structure in a belt-type continuously variable transmission according to claim 5, wherein the pulley structure is formed thicker.   The heat treatment and the plating treatment are performed on the pulley boss (58) of the movable pulley half (50) before the connection with the pulley face (59). A pulley structure in the described belt type continuously variable transmission.   Each coupling protrusion (61) on the outer periphery of the pulley boss (55, 58) is formed in a trapezoidal shape, and the angle between the straight lines passing through the circumferential center of the coupling protrusion (61) on both sides of the first recess (62) is The angle is set smaller than the angle between the straight lines passing through the center in the circumferential direction of the coupling protrusions (61) on both sides of the second recess (63), the coupling protrusions (61), the first recess (62) and the second The pulley structure in the belt type continuously variable transmission according to any one of claims 1 to 7, wherein the connecting portion with the concave portion (63) is formed in a similar curved shape.   The pulley face (56, 59) constituting a part of the stationary pulley half (49) and the movable pulley half (50) is formed in the same shape. A pulley structure in the belt type continuously variable transmission according to any one of the above.

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