JP2005291274A - Cooling device for belt-type continuously variable transmission - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To provide a cooling device for a belt-type continuously variable transmission capable of generating an airflow from an inner diameter portion to an outer diameter portion at a back side of a fixed sheave of a pulley and restraining temperature rise at a back side of the fixed sheave. <P>SOLUTION: An air inlet 63 and an exhaust outlet 65 are arranged on casings 6 and 60 covering a drive pulley 11 and driven pulley 21, air is inhaled from the air inlet 63 in response to rotation of both pulleys 11 and 21, and the air is discharged from the exhaust outlet 65. The exhaust outlet 65 is arranged in the vicinity of an outer periphery of the driven pulley 21, and a fin 21c generating an airflow is arranged on an outer surface of a fixed sheave 21a of the driven pulley 21. A direction board 81 adjacent to the fin is arranged between the fin 21c and a side wall 6c, and a space between the direction board 81 and the side wall 6c is open to an inner diameter side rather than the fin 21c. Thus, air is inhaled from an inner diameter side of the fixed sheave 21a by actions of a centrifugal fan, and an airflow pushing out toward an outer diameter side is generated. <P>COPYRIGHT: (C)2006,JPO&NCIPI

Description

The present invention relates to a cooling device for a belt-type continuously variable transmission, and more particularly to a structure for air-cooling a belt in a continuously variable transmission using a dry belt.

Various types of continuously variable transmissions have been proposed and some of them have been put into practical use. The continuously variable transmission includes a driving pulley, a driven pulley, and a belt wound around both pulleys. By changing the width of the pulley groove of the driving pulley and the driven pulley in the reverse direction, the transmission ratio is continuously variable. Is variable. Therefore, there is an advantage that there is no shift shock and fuel consumption can be improved.

The continuously variable transmission includes a type using a wet belt (metal belt) and a type using a dry belt. The former is driven while lubricating the belt with oil, while the latter is driven by using the frictional force acting between the pulley without lubricating the belt, and transmission efficiency compared to the former. Is good. However, in the latter case, since the belt generates heat due to frictional heat with the pulley and bending of the belt, it is necessary to always air-cool the pulley chamber.

In Patent Document 1, an intake port and an exhaust port are provided in the belt case, fins are provided on the back surfaces of the drive pulley and the driven pulley, an air flow is generated by the fins, and air is sucked from the air intake port and exhausted from the exhaust port. A belt type continuously variable transmission that cools the inside of a belt case is disclosed.

However, even if an air flow is generated by the fins as described above, air stagnation is likely to occur on the back side of the fixed sheaves of the driving pulley and the driven pulley, particularly the inner diameter portion thereof, which causes an increase in the temperature of the belt.
The reason is that the fin has a stirring action that stirs the air, but it does not have the action of a centrifugal pump that generates a radial airflow, and the fixed sheave is not displaced in the axial direction unlike the movable sheave. This is because air is less likely to enter and exit from the inner diameter portion on the back side of the sheave, and air stagnation is likely to occur.
Furthermore, when a gear chamber lubricated with oil is laid out on the back side of the fixed sheave of the driven pulley, the temperature in the belt case also increases as the oil temperature in the gear chamber increases. As described above, since air tends to stagnate on the back side of the fixed sheave, the temperature rise of the partition wall of the gear chamber located on the back side of the fixed sheave cannot be suppressed, leading to an increase in the temperature inside the belt case, and thus the belt temperature. It will be.
JP 2001-158246 A

Accordingly, an object of the present invention is to provide a cooling device for a belt-type continuously variable transmission that can generate an air flow from an inner diameter portion to an outer diameter portion on the back side of a fixed sheave of a pulley and suppress a temperature rise on the back side of the fixed sheave. It is to provide.

In order to achieve the above object, according to the first aspect of the present invention, an intake port and an exhaust port are provided in a casing that covers a drive pulley and a driven pulley, and a V-belt wound between both pulleys. In the belt-type continuously variable transmission that sucks air from the intake port and exhausts air from the exhaust port as the motor rotates, airflow is generated on the back of the stationary sheave of at least one of the drive pulley and the driven pulley. A fin to be generated is provided, a gap is provided between the fin and a side wall of the casing facing the back surface of the fixed sheave, and a guide plate is disposed in the gap in the vicinity of the fin; The space between the guide plate and the side wall is opened to the inner diameter side from the fin, and provides a cooling device for a belt type continuously variable transmission.

As the pulley rotates, the air is stirred by the fins provided on the back surface of the fixed sheave, the outside air enters from the intake port, flows through the casing, and is discharged from the exhaust port. Even if fins are provided on the back surface of the fixed sheave, the fins only stir the air, air stagnation on the back surface side of the fixed sheave is not eliminated, and temperature rise cannot be effectively suppressed. Therefore, when a guide plate is disposed in the vicinity of the fin and the space between the guide plate and the side wall is opened to the inner diameter side from the fin, an air flow from the inner diameter side to the outer diameter side is generated by the action of the centrifugal pump. That is, air enters the space between the guide plate and the side wall, passes through the space, is guided to the inner diameter side of the fin, and further flows from the inner diameter side of the fixed sheave to the outer diameter side. Therefore, air stagnation on the back side of the fixed sheave is eliminated, and temperature rise can be suppressed.
Since only a guide plate is installed in the casing to generate a radial air flow by the action of the centrifugal pump, the cooling efficiency can be increased with a simple structure.

In the present invention, the position where the guide plate is provided may be on the back side of any fixed sheave of the driving pulley and the driven pulley. However, since the driven pulley rotates at high speed when the belt generates the largest amount of heat, the most effective cooling effect is to provide a fin on the fixed sheave of the driven pulley and provide a guide plate near the fin. is there.

As in the second aspect, the present invention is suitable when a gear chamber lubricated with oil is provided on the back side of the side wall.
That is, when the gear chamber is provided on the back side of the fixed sheave via the side wall, the side wall is heated due to the oil temperature rise in the gear chamber, and the temperature of the pulley chamber also increases due to the influence. However, if the guide plate is disposed close to the fin as described above, the side wall is cooled because the air flow is generated on the back side of the fixed sheave by the action of the centrifugal pump. As a result, an increase in the temperature of the pulley chamber can be suppressed, and as a result, an increase in the temperature of the belt can be suppressed.

According to the present invention, the guide plate is arranged in the vicinity of the fin provided on the back surface of the fixed sheave, and the space between the guide plate and the side wall is opened to the inner diameter side from the fin. It is possible to generate an air flow from the inner diameter side to the outer diameter side on the back side. Therefore, air stagnation on the back side of the fixed sheave is eliminated, and the temperature rise of the entire pulley chamber can be suppressed as well as the fixed sheave.

Embodiments of the present invention will be described below with reference to examples.

1 to 6 show a specific structure of an example of a continuously variable transmission according to the present invention, and FIG. 7 shows its skeleton structure.
The continuously variable transmission of this embodiment is an FF horizontal type automobile transmission, which is roughly an input shaft 3 driven via a torsional damper 2 by an engine output shaft 1 and a drive shaft that supports a drive pulley 11. 10, a driven shaft 20 that supports the driven pulley 21, a drive pulley 11 and a dry V belt 15 wound around the driven pulley 21, a first reduction shaft 30, a second reduction shaft 31, and an output shaft 32 connected to the wheels. The transmission motor 40 (see FIG. 7), the tensioner device 50, and the like. The input shaft 3, the drive shaft 10, the driven shaft 20, the first reduction shaft 30, the second reduction shaft 31, and the output shaft 32 are all non-coaxial and arranged in parallel. 1 and 4, the drive pulley 11 is drawn above the driven pulley 21, but actually the drive pulley 11 is arranged below the driven pulley 21 as shown in FIG. 3.
The V-belt 15 used in this embodiment is a well-known composite belt composed of a pair of endless tension bands and a number of blocks locked in the length direction by these tension bands.

The input shaft 3 is rotatably supported by a transmission case 6 via a bearing, and the input shaft 3 is integrally formed with an input gear 3a that meshes with a gear 10a provided at the engine side end of the drive shaft 10. Yes. By appropriately setting the reduction ratio between the input gear 3a and the gear 10a, the drive shaft 10 can be rotated at a reduction ratio suitable for belt driving.

The drive pulley 11 includes a fixed sheave 11a fixed on the drive shaft 10, a movable sheave 11b supported on the drive shaft 10 so as to be movable in the axial direction, and a stroke mechanism 12 provided behind the movable sheave 11b. The movable sheave 11b and the stroke mechanism 12 are disposed closer to the engine than the V belt 15. The stroke mechanism 12 of this embodiment is a ball screw mechanism that moves the movable sheave 11b in the axial direction by rotational input from the speed change motor 40. The female screw member 12b is supported on the movable sheave 11b via a bearing 12a so as to be relatively rotatable. And a male screw member 12c fixed to the case 6, and a transmission gear 13 is fixed to the outer periphery of the female screw member 12b.

The driven pulley 21 includes a fixed sheave 21a fixed on the driven shaft 20, a movable sheave 21b supported on the driven shaft 20 so as to be axially movable, and a stroke mechanism 22 provided behind the movable sheave 21b. The movable sheave 21b and the stroke mechanism 22 are disposed on the opposite side of the engine from the V belt 15. This stroke mechanism 22 is also a ball screw mechanism having the same configuration as the stroke mechanism 12 of the drive pulley 11, and is fixed to the case 6 with a female screw member 22 b supported relative to the movable sheave 21 b through a bearing 22 a so as to be relatively rotatable. The transmission gear 23 is fixed to the outer peripheral portion of the female screw member 22b.

A forward / reverse switching mechanism 24 is provided at a portion of the driven shaft 20 closer to the engine than the driven pulley 21, and a forward gear 25 and a reverse gear 26 are rotatably supported on both sides thereof. When the forward / reverse switching mechanism 24 is shifted to the left in FIG. 7, the forward (D) position is obtained, and when the forward / reverse switching mechanism 24 is shifted to the right, the backward (R) position is obtained. A start clutch 27 is provided at the shaft end of the driven shaft 20 on the engine side. The start clutch 27 connects and disconnects the hub 24 a of the forward / reverse switching mechanism 24 to the driven shaft 20. The forward gear 25 is engaged with the gear 30a of the first reduction shaft 30, the gear 30b of the first reduction shaft 30 is engaged with the gear 31a of the second reduction shaft 31, and the gear 31b of the second reduction shaft 31 is further connected to the differential device 33. Is engaged with the ring gear 33a. Further, the reverse gear 26 meshes with the gear 30 b of the first reduction shaft 30 through the idler gear 28. And the output shaft 32 connected with the wheel via the differential device 33 is driven.

The input gear 3a of the input shaft 3, the gear 10a of the drive shaft 10, the forward / reverse switching mechanism 24, the forward gear 25, the reverse gear 26, the start clutch 27, the first reduction shaft 30 (gears 30a and 30b), the second The reduction shaft 31 (gears 31 a and 31 b) and the differential device 33 are accommodated in a gear chamber 6 a formed on the engine side of the case 6. The gear chamber 6a is lubricated with oil.
On the other hand, the drive pulley 11 and the driven pulley 21 are disposed in a pulley chamber 6b of the case 6 partitioned by the gear chamber 6a and the partition wall 6c. The pulley chamber 6b is a non-lubricated space and is air-cooled.

A speed change motor 40 (see FIG. 7) is attached to the outer side of the case 6. The output gear 41 of the speed change motor 40 is meshed with a reduction gear 45 a provided at one end of the first speed change shaft 45. The first transmission shaft 45 is provided across the pulley chamber 6b. A gear 45 b provided at the other end of the first transmission shaft 45 is a spur gear having a length corresponding to the moving stroke of the movable sheave 21 b of the driven pulley 21, and meshes with the transmission gear 23 provided on the driven pulley 21. Yes. When the gear 45b of the first speed change shaft 45 is rotated, the speed change gear 23 is rotated so that the movable sheave 21b can be moved in the axial direction by the action of the ball screw mechanism 22. That is, the pulley groove width (belt winding diameter) of the driven pulley 21 can be continuously changed by the speed change motor 40.

The transmission gear 23 of the driven pulley 21 is also meshed with a first idler gear 46 a of a second transmission shaft 46 provided over the case 6, and the second idler gear 46 b of the second transmission shaft 46 is also connected to the transmission gear 13 of the drive pulley 11. Are engaged. These idler gears 46a and 46b are also constituted by spur gears having a length corresponding to the moving stroke of the movable sheaves 11b and 21b, similarly to the gear 45b of the first transmission shaft 45. As shown in FIG. 3, the second transmission shaft 46 is disposed between the drive pulley 11 and the driven pulley 21 and in the circumference of the V belt 15. The rotational force of the speed change motor 40 is transmitted to the speed change gear 13 of the drive pulley 11 via the first speed change shaft 45, the speed change gear 23 of the driven pulley 21, and the second speed change shaft 46. Therefore, the movable sheave 11a of the driving pulley 11 and the movable sheave 21a of the driven pulley 21 are synchronized with each other, and can move in the axial direction while changing the pulley groove width (belt winding diameter) in the opposite direction.

Next, a mechanism for applying belt tension to the V-belt 15, that is, the tensioner device 50 will be described.
As described above, the pulley groove width (belt wrapping diameter) of the pulleys 11 and 21 is varied in the opposite direction by the speed change motor 40. However, the slippage between the V belt 15 and the pulleys 11 and 21 is caused by the transmission torque. Will occur. Therefore, a tensioner device 50 as shown in FIG. 3 is provided in order to apply a belt tension that does not cause the V belt 15 to slip. The tensioner device 50 includes a tension roller 51 that presses the loose side of the V-belt 15 inward, and a swingable tensioner arm 53 that supports the tension roller 51 via a link 52. By pressing the V-belt 15 from the outside to the inside in this way, a predetermined belt tension is obtained, and the winding length of the V-belt 15 around the pulleys 11 and 21 is lengthened to increase the transmission efficiency.
Here, the tension roller 51 is attached to the tensioner arm 53 via the link 52, but it goes without saying that the tension roller 51 may be directly attached to the tensioner arm 53.
Further, the tension roller 51 is not limited to the one that presses against the V belt 15 from the outside, and may be the one that presses from the inside.

A base end portion of the tensioner arm 53 is swingably attached to the transmission case 6 via a shaft 53a. A base end portion of a pin 55 is rotatably attached to an intermediate portion of the tensioner arm 53 via a shaft 54. The rod-like tip portion of the pin 55 is inserted into the hollow portion of the piston rod 57 of the hydraulic cylinder 56 provided at the lower portion of the pulley chamber 6b, and is in contact with the bottom portion of the hollow portion. By adjusting the hydraulic pressure of the hydraulic cylinder 56, the rotational biasing force of the tensioner arm 53 can be controlled and adjusted to an optimum belt tension suitable for belt driving. A compression spring 58 is disposed in the hydraulic cylinder 56, and the spring force of the compression spring 58 is a spring force that can provide the minimum belt tension necessary for traveling even if the hydraulic pressure of the hydraulic cylinder 56 fails. Is set.
In this embodiment, the compression spring 58 is disposed in the hydraulic cylinder 56 in order to apply the minimum tension to the belt 15, but a spring for swinging and biasing the tensioner arm 53 may be disposed separately. In this case, a tension spring or a torsion spring may be used as the spring in addition to the compression spring.
In this embodiment, an example in which the tension roller 51 presses the V belt 15 from the outside to the inside has been described. However, the present invention can be applied even when the tension roller 51 presses the V belt 15 from the inside to the outside. is there.

Next, the cooling device for the continuously variable transmission will be described.
As shown in FIGS. 1 and 4, the case bearing 60 that forms the side wall of the case 6 on the side opposite to the engine holds a first bearing 70 that rotatably supports the shaft end on the side opposite to the engine of the drive shaft 10. A holding portion 61 that holds the second bearing 71 that rotatably supports the shaft end portion of the driven shaft 20 on the side opposite to the engine is provided. As shown in FIG. 2, a plurality of air inlets 63 arranged in an annular shape around the drive shaft 10 are provided around the holding portion 61.

Fins 11c and 11d are formed on the outer surface (rear surface) of the fixed sheave 11a and the movable sheave 11b of the drive pulley 11, and the fin 11c on the outer surface of the fixed sheave 11a is formed wide. The air inlet 63 faces the outer surface of the fixed sheave 11a and is arranged on the inner diameter side of the fin 11c. Therefore, the outside air is sucked in from the intake port 63 by the action of the centrifugal pump by the fins 11 c and is sent to the outside of the V-belt 15. Since the fin 11c is close to the inner wall surface of the case cover 60, the gap between the case cover 60 and the fin 11c is narrowed, and the centrifugal pump action due to the rotation of the fin 11c can be exerted effectively.

A resin-made intake duct 64 for uniformly guiding the outside air taken in from the air intake port 64 a to the intake port 63 is fixed to the outer surface of the case cover 60. The air intake 64a of this embodiment is formed in a grid shape in a wide area so that a large amount of air can be taken in, and is open to the side of the transmission case 6.

An exhaust port 65 (see FIGS. 3 and 5) that opens in a substantially tangential direction of the driven pulley 21 is formed in the vicinity of the outer peripheral portion of the driven pulley 21, which is a joint portion between the case 6 and the case cover 60. . A resin exhaust duct 66 (see FIG. 6) is connected to the exhaust port 65. The exhaust duct 66 is formed with a cylindrical fitting portion 66a that is fitted to the exhaust port 65. The fitting portion 66a projects into the case 6 on the downstream side in the pulley rotation direction, and its tip is a driven pulley. The guide part 66b close to the outer peripheral part of 21 is integrally formed. The guiding portion 66b has a role of suppressing the return of the air flowing through the case 6 back to the case 6 and guiding it in the discharge direction. The guiding portion 66b does not interfere with the driven pulley 21 and the V belt 15 even at the maximum gear ratio (Low) and is undercut according to the outer shape so as to be as close as possible to the outer periphery of the pulley 21 and the V belt 15. Has been.

The exhaust duct 66 is integrally formed with a flange 66c that comes into contact with the outer surface of the exhaust port 65, and defines the amount of protrusion of the guide portion 66b into the case 6. Two mounting seats 66 d are provided in the exhaust duct 66, and these mounting seats 66 d are fastened to the outer surface of the case 6 with bolts. At this time, since the flange portion 66 c closes the exhaust port 65, rain water and shower water can be prevented from entering the case 6 from the exhaust port 65. In addition, if a packing or the like is interposed between the flange portion 66c and the outer surface of the exhaust port 65, it is possible to reliably prevent water from entering.

Fins 21c and 21d are also formed on the outer surface (rear surface) of the fixed sheave 21a and the movable sheave 21b of the driven pulley 21. By the rotation of the fins 21c and 21d, the air flowing through the pulley chamber 6b is discharged from the exhaust port 65 to the outside. At this time, a part of the air is not discharged from the exhaust port 65 and tries to return to the pulley chamber 6b along with the fins 21c and 21d, but this air enters the case 6 from the downstream side of the exhaust port 65 in the pulley rotation direction. Since the protruding guide part 66b is dammed and guided in the discharge direction, air can be efficiently discharged from the exhaust port 65.

The exhaust duct 66 is bent in the lateral direction in the vicinity of the connection portion with the exhaust port 65, the intermediate portion extends laterally along the outer surface of the case 6, and an opening 66 e that opens downward is formed at the tip. It is formed (see FIG. 6). Therefore, it is possible to prevent water or the like from flowing into the exhaust port 65 through the exhaust duct 66.

A gear chamber 6a is provided behind the fixed sheave 21a of the driven pulley 21 via a partition wall 6c. Since the lubricating oil is enclosed in the gear chamber 6a, the partition wall 6c also rises in temperature due to the rise in oil temperature. The space between the fixed sheave 21a and the partition wall 6c, particularly in the space near the drive pulley 11, has a small amount of fresh air, so that heat is easily trapped, and the heat increases the room temperature of the pulley chamber 6b. .
Therefore, in this embodiment, as shown in FIGS. 4 and 5, a recess 80 is provided on the side surface of the partition wall 6c facing the fixed sheave 21a of the driven pulley 21, and a guide plate 81 is bridged and fixed to the recess 80. is there. Both ends of the guide plate 81 are fixed to the side surface of the partition wall 6c with bolts 82. The guide plate 81 is fixed at a position substantially opposite to the fins 21c of the fixed sheave 21a, and the gap between the guide plate 81 and the fins 21c is set to a minute gap of about 1 to 3 mm. One opening 80a of the recess 80 partitioned by the guide plate 81 opens to the inner diameter side of the fin 21c, and the other opening 80b opens to the drive pulley side. Therefore, due to the action of the centrifugal pump accompanying the rotation of the fins 21c, as shown by arrows in FIGS. 4 and 5, air enters the recess 80 from the opening 80b on the driving pulley side, and the stationary sheave 21a from the opening 80a on the driven pulley side. Is sucked out to the inner diameter side of the gas and flows toward the outer diameter side of the fixed sheave 21a. Thereafter, the exhaust air is exhausted to the exhaust port 65 as the driven pulley 21 rotates.
In this way, fresh air is introduced into the space between the fixed sheave 21a and the partition wall 6c, and the ventilation flow rate is increased. Therefore, the fixed sheave 21a and the partition wall 6c are cooled, and the lubricating oil sealed in the gear chamber 6a is further cooled. Oil temperature also decreases. Therefore, the cooling effect of the entire pulley chamber 6b can be enhanced.

The position of the opening 80 b on the drive pulley side of the recess 80 is preferably provided in a region between the drive pulley 11 and the driven pulley 21, particularly in a region overlapping with the circumferential region of the belt 15. The reason is that in this region, there is little circulation of fresh air and air stagnation is likely to occur. Therefore, by sucking the air in this region and forcibly sending it to the inner diameter side of the driven pulley 21, it is possible to eliminate air stagnation and to suppress the temperature rise of the belt.

As described above, the cooling device for the continuously variable transmission has a narrow gap between the fin 11c of the drive pulley 11 and the inner wall surface of the case cover 60. Therefore, the centrifugal pump action of the fin 11c causes the inner peripheral side of the drive pulley 11 to move. Only the air flow from the outer peripheral side to the outer peripheral side is generated, and the air can be efficiently sucked from the intake port 63.
The air sucked from the intake port 63 is pushed outward in the radial direction of the drive pulley 11 and is sent to the outside of the V belt 15. Then, it flows in the direction of the driven pulley 21 as the V belt 15 moves.
Furthermore, the air rotates as the fins 21c and 21d rotate due to the stirring action of the fins 21c and 21d of the driven pulley 21, but the amount of air returned back into the pulley chamber 6b by the guide portion 66b provided in the exhaust duct 66 is limited. Therefore, the air heated in the pulley chamber 6b can be efficiently exhausted from the exhaust port 65 to the outside.
As described above, both the intake air amount from the intake port 63 and the exhaust air amount from the exhaust port 65 increase, so that the ventilation flow rate in the pulley chamber 6b increases and the V belt 15 and the pulleys 11 and 21 can be effectively cooled.

The present invention is not limited to the above embodiments.
In the above embodiment, the intake port 63 is provided in the vicinity of the drive pulley 11 and the exhaust port 65 is provided in the vicinity of the driven pulley 21. On the contrary, the intake port 63 is provided in the vicinity of the driven pulley 21 and the exhaust port 65 is exhausted. The port 65 may be provided in the vicinity of the drive pulley 11.
In the above embodiment, the intake port 63 is on the back side of the fixed sheave 11a of the drive pulley 11 and opens to the inner diameter side of the fin 11c of the fixed sheave 11a, and the inner wall surface of the case cover 60 is close to the fin 11c. Therefore, the outside air can be efficiently sucked in by the action of the centrifugal pump, and there is no need to attach a guide plate to the inner surface of the case cover 60, but the intake port 63 is provided in the vicinity of the outer peripheral portion of the drive pulley 11. In this case, a guide plate close to the fin 11c of the fixed sheave 11a may be attached to the inner surface of the case cover 60.
In the above embodiment, a continuously variable transmission is described in which a stroke mechanism and a speed change motor provided in each pulley are combined with a tensioner device that obtains belt tension by pressing a V belt with a tension roller. The present invention is not limited to this, and can be applied to all known dry-type continuously variable transmissions.

It is an expanded sectional view of an example of a continuously variable transmission concerning the present invention. FIG. 2 is a side view of the continuously variable transmission shown in FIG. 1. It is sectional drawing of the pulley chamber of the continuously variable transmission shown in FIG. It is the sectional view on the AA line of FIG. It is an inner side view of a transmission case. It is the perspective view seen from the downward direction of the exhaust duct, and the perspective view seen from the upper part. FIG. 2 is a skeleton diagram of the continuously variable transmission of FIG. 1.

Explanation of symbols

6 Case (casing)
6a Gear chamber 6b Pulley chamber 6c Partition wall (side wall)
11 Drive pulley 15 V belt 21 Driven pulley 21a Fixed sheave 21c Fin 60 Case cover (casing)
63 Intake port 65 Exhaust port 80 Recess (gap)
80a Opening on the driven pulley side 80b Opening on the driving pulley side 81 Guide plate

Claims (2)

The casing that covers the driving pulley and the driven pulley and the V belt wound between the pulleys is provided with an intake port and an exhaust port. Air is sucked from the intake port as the pulleys rotate, In belt type continuously variable transmissions that exhaust air,
On the back surface of the fixed sheave of at least one of the driving pulley and the driven pulley, a fin for generating an airflow is provided,
A gap is provided between the fin and the side wall of the casing facing the back surface of the fixed sheave,
In the gap, a guide plate is arranged close to the fin,
A cooling device for a belt-type continuously variable transmission, wherein a space between the guide plate and the side wall opens toward the inner diameter side of the fin. 2. The cooling device for a belt-type continuously variable transmission according to claim 1, wherein a gear chamber lubricated with oil is provided on the back side of the side wall.

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