JP2010236626A - Cooling device of v-belt type continuously variable transmission - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To provide a cooling device for a V-belt type continuously variable transmission having an enhanced cooling efficiency. <P>SOLUTION: The continuously variable transmission 67 has a primary pulley 51 and a secondary pulley 61, and a V-belt 66 is set over between these pulleys. The transmission 67 is accommodated in an accommodation chamber 70 of a transmission case 25, and the transmission case 25 is furnished with a cooling wind introducing duct 71 and a cooling wind exhaust duct 72. The primary pulley 51 is furnished with a centrifugal fan 73 to produce the cooling wind, and the centrifugal fan 73 is furnished with a partitioning plate 77 to partition a cooling wind intake hole 71a in the cooling wind introducing duct 71 from a blowout part 75b of the centrifugal fan 73. The partitioning plate 77 has a greater outside diameter than the centrifugal fan 73 to prevent the cooling wind from reversely flowing into the cooling wind introducing duct 71. <P>COPYRIGHT: (C)2011,JPO&INPIT

Description

  The present invention relates to a cooling device for a V-belt type continuously variable transmission in a power transmission system for a vehicle.

  As a transmission used in a power transmission system that transmits engine output to driving wheels, there is a continuously variable transmission that continuously controls a gear ratio. The continuously variable transmission includes a V-belt type having an input-side primary pulley, an output-side secondary pulley, and a V-belt that spans between these pulleys, each having a variable groove width. The primary pulley on the input side is provided on the drive side shaft, that is, the primary shaft, and the secondary pulley on the output side is provided on the driven side shaft, that is, the secondary shaft. The V-belt type continuously variable transmission is provided with an introduction duct for introducing cooling air into the transmission case and a discharge duct for discharging cooling air in order to cool each pulley and V-belt. . If a centrifugal fan is provided on the back side of the pulley, it is possible to generate cooling air from the introduction duct to the discharge duct in the accommodation chamber in the transmission case by utilizing the rotation of the pulley.

  As described in Patent Document 1, as a centrifugal fan, there is a radial fan type in which fan blades extend in the radial direction. In this continuously variable transmission, the air introduction port of the introduction duct is a pulley on the input side. It opens to the outer peripheral surface, and the air discharge port of the discharge duct opens to the outer peripheral surface of the pulley on the output side. Further, as described in Patent Document 2, the centrifugal fan includes a multi-blade fan type in which the cross-sectional shape of the fan blade is an arc shape. In this continuously variable transmission, air is introduced into the introduction duct. The opening opens at the end of the input side shaft, and the air discharge opening of the discharge duct opens at the outer peripheral surface of the pulley on the output side.

JP-A 61-262265 JP 2005-291273 A

  In the continuously variable transmission provided with the above-described radial fan type centrifugal fan, a shielding plate is provided between the inner surface of the transmission case on the air inlet side and the belt entrainment side of the centrifugal fan, so that the speed change on the air discharge side. A shielding plate is provided between the inner surface of the machine case and the belt feeding side of the centrifugal fan to prevent backflow of air. However, since the air inlet is disposed radially outward of the fan blade, when the fan blade moves to a position facing the air inlet as the pulley rotates, the space between the blades is radially outward. It faces the air inlet. For this reason, even if it sets as small as possible between a shielding board and a centrifugal fan, there exists a limit in reducing the quantity of the air which flows back into an air inlet. This also has a limit in reducing the amount of air returning from the air outlet side to the inside as well on the air outlet side. Therefore, there is a problem that the cooling efficiency cannot be improved by the cooling fan.

  On the other hand, in the continuously variable transmission provided with the multi-blade fan type centrifugal fan described above, the air inlet of the introduction duct is opened at the end of the input side shaft, so the air inlet is formed. The intake duct, that is, the introduction duct must be arranged on the axial extension of the input side shaft, the axial length of the input side shaft including the introduction duct becomes longer, and the width dimension of the power transmission system is reduced. There is a problem that can not be.

  Further, in this continuously variable transmission, a discharge duct is disposed radially outward of a centrifugal fan provided on the output pulley. In order to guide the air pressurized by the centrifugal fan to the air discharge port, the induction unit is attached to the discharge duct, but the air discharge port of the discharge duct faces the outside of the centrifugal fan in the radial direction. Therefore, like the radial fan type described above, there is a limit to reducing the amount of air returning from the air discharge port side to the inside, and there is a problem that the cooling efficiency cannot be improved by the cooling fan.

  An object of the present invention is to improve the cooling efficiency of a V-belt type continuously variable transmission.

  A cooling device for a V-belt type continuously variable transmission according to the present invention includes a primary pulley having a variable groove width provided on a primary shaft, a secondary pulley having a variable groove width provided on a secondary shaft, and a V-belt stretched over these pulleys. A cooling device for a V-belt type continuously variable transmission for driving a vehicle, comprising a storage chamber for storing the continuously variable transmission, and provided with a cooling air introduction duct and a cooling air discharge duct. A centrifugal fan that is provided on the transmission case, is provided on the pulley, and cools the continuously variable transmission by introducing cooling air from the cooling air introduction duct, and then is discharged to the cooling air discharge duct, and is attached to the centrifugal fan. A partition plate that partitions the cooling air introduction port of the cooling air introduction duct and the blowing portion of the centrifugal fan, and the partition plate that rotates integrally with the centrifugal fan has an outer peripheral portion. Wherein the protruding radially outward from the outer periphery of the centrifugal fan.

  In the cooling device for a V-belt continuously variable transmission according to the present invention, the partition plate has a through hole that guides the cooling air introduced from the cooling air introduction port to the central portion in the radial direction of the centrifugal fan. And In the cooling device for a V-belt type continuously variable transmission according to the present invention, the pulley includes a fixed portion and a movable portion that moves in the axial direction along the rotation axis of the pulley with respect to the fixed portion. The cooling air inlet is formed in the vicinity of the fixed part, and the centrifugal fan is provided in the fixed part.

  According to the present invention, since the partition plate provided in the centrifugal fan protrudes radially outward from the outer periphery of the centrifugal fan, the blowout portion of the centrifugal fan and the cooling air inlet are reliably partitioned. . Thus, the cooling air blown out from the blowing portion is prevented from flowing back from the cooling air introduction port to the cooling air introduction duct, and the cooling efficiency of the continuously variable transmission can be improved.

It is a skeleton figure which shows the cooling device of the V belt type continuously variable transmission which is one embodiment of this invention. It is an expanded sectional view of the cooling device of the V-belt type continuously variable transmission shown in FIG. FIG. 3 is a side view showing a case base portion of the transmission case shown in FIG. 2. FIG. 4 is a perspective view showing a case base and a continuously variable transmission shown in FIG. 3. FIG. 4 is a perspective view showing a primary pulley, a centrifugal fan, and a partition plate shown in FIG. 3.

  Hereinafter, embodiments of the present invention will be described in detail with reference to the drawings. The V-belt type continuously variable transmission of the present invention is used in a power transmission system 10 for a vehicle for transmitting engine output to drive wheels. As shown in FIG. 1, a crankshaft 13 is rotatably mounted by a bearing on a crankcase 12 provided in a transmission case 11 of the power transmission system 10. A cylinder block (not shown) constituting the engine is attached to the crankcase 12, and a piston incorporated in the cylinder block so as to be able to reciprocate is provided on the crankshaft 13 at a position eccentric from the center of rotation. 14 is connected via a connecting rod. FIG. 1 shows a base end 15 connected to the crankpin 14 of the connecting rod. A balancer shaft 16 is rotatably mounted on the crankcase 12 in parallel with the crankshaft 13 via a bearing, and a balancer weight 17 is integrally provided on the balancer shaft 16. A driven gear 18a provided on the balancer shaft 16 meshes with a drive gear 18b provided on the crankshaft 13. When the balancer weight 17 is driven to rotate by the crankshaft 13, the inertial force of the piston causes the balancer weight 17 and the crankshaft to rotate. The axis 13 cancels out.

  A power generator 20 is disposed outside the crankcase 12 so as to be positioned on one end side of the crankshaft 13, and the power generator 20 is covered with a power generator cover 21 attached to the crankcase 12. The power generation body 20 has an outer rotor 22 attached to the crankshaft 13 and a stator 24 provided with a coil 23 and attached to the crankcase 12. When the engine is driven and the crankshaft 13 rotates, the power generation body 20 The generated power is charged in a battery (not shown).

  A transmission case 25 is mounted on the transmission case 11 so as to be positioned on the other end side of the crankshaft 13, and the transmission case 25 is attached to a case base 25 a attached to the outside of the crankcase 12 and a case attached thereto. And a cover 25b. In the transmission case 25, an input side shaft, that is, a primary shaft 26 is rotatably mounted coaxially with the crankshaft 13, and an output shaft, that is, a secondary shaft 27 is rotatably mounted in parallel to the primary shaft 26. One end of the primary shaft 26 is supported by a bearing 28a provided on the case base 25a, and the other end is supported by a bearing 28b provided on the case cover 25b. The secondary shaft 27 extends into the transmission case 11 and is supported by bearings 29 a and 29 b provided in the transmission case 11.

  A centrifugal clutch 30 is disposed outside the crankcase 12 so as to be positioned on the other end side of the crankshaft 13. The centrifugal clutch 30 has a clutch drum 31 attached to the primary shaft 26 and a rotating plate 32 attached to the crankshaft 13. As shown in FIG. 2, a plurality of arc-shaped clutch shoes 34 are rotatably attached to the rotating plate 32 by pins 33, and springs in a direction away from the inner peripheral surface of the clutch drum 31 are attached to the clutch shoes 34. A force is applied by the spring member 35. Therefore, when the rotational speed of the crankshaft 13 becomes equal to or higher than the predetermined rotational speed, the clutch shoe 34 is engaged with the inner peripheral surface of the clutch drum 31 against the spring force, and the crankshaft 13 and the primary shaft 26 are in the engaged state. Become.

  As shown in FIG. 1, a forward / reverse switching shaft 36 is rotatably mounted on the transmission case 11 in parallel with the secondary shaft 27. A low speed drive gear 37a and a high speed drive gear 38a are fixed to the secondary shaft 27, and a reverse drive gear 39a is fixed. On the other hand, the forward / reverse switching shaft 36 is rotatably mounted with a driven gear 37b that meshes with a low-speed drive gear 37a and a driven gear 38b that meshes with a high-speed drive gear 38a, and a reverse drive gear 39a. A driven gear 39b that meshes with an idle gear (not shown) is rotatably mounted.

  As shown in FIG. 1, a speed reduction shaft 41 is rotatably mounted on the transmission case 11 so as to be parallel to the forward / reverse switching shaft 36, and a driving gear mounted on the forward / backward switching shaft 36. A driven gear 42b that meshes with 42a is attached. A first output shaft 43a that extends in a direction perpendicular to the speed reduction shaft 41 is rotatably mounted on the transmission case 11, and the output shaft 43a is a follower that meshes with a drive-side bevel gear 44a attached to the speed reduction shaft 41. A side bevel gear 44b is attached. A second output shaft 43b is connected to the first output shaft 43a, and power is transmitted to the front and rear wheels via these output shafts 43a and 43b. The power transmission system 10 shown in FIG. 1 is mounted on the vehicle body so that the crankshaft 13 faces the vehicle width direction and the output shafts 43a and 43b face the vehicle traveling direction.

  A switching mechanism 45 is splined to the forward / reverse switching shaft 36 between two driven gears 37b and 39b, and the switching mechanism 45 rotates integrally with the forward / reverse switching shaft 36 and is movable in the axial direction. Yes. When this switching mechanism 45 is meshed with the low-speed driven gear 37b, the rotation of the secondary shaft 27 is transmitted to the output shafts 43a and 43b via the low-speed gear pairs 37a and 37b, and via the output shafts 43a and 43b. Forward power is transmitted to the drive wheels. On the other hand, when the switching mechanism 45 is engaged with the reverse driven gear 39b, the rotation of the secondary shaft 27 is transmitted to the output shafts 43a, 43b via the reverse gear pair 39a, 39b and the idle gear, and the output shaft 43a, Power in the reverse direction is transmitted to the drive wheels via 43b. A switching mechanism 46 is splined to the forward / reverse switching shaft 36 so as to face the driven gear 38b. The switching mechanism 46 rotates integrally with the forward / reverse switching shaft 36 and is movable in the axial direction. When this switching mechanism 46 is meshed with the high-speed driven gear 38b, the rotation of the secondary shaft 27 is transmitted to the output shafts 43a and 43b via the high-speed gear pairs 38a and 38b and via the output shafts 43a and 43b. Forward power is transmitted to the drive wheels.

  A primary pulley 51 is attached to the primary shaft 26. As shown in FIG. 2, the primary pulley 51 has a fixed sheave, that is, a fixed portion 52 in which a conical surface is formed on the surface 52a side, and a movable sheave in which a conical surface opposite to the fixed portion 52 is formed on the surface 53a side. And a movable portion 53. The fixed portion 52 is disposed on the inner side of the primary shaft 26, that is, on the centrifugal clutch 30 side, and the movable portion 53 is disposed on the case cover 25 b side outside the fixed portion 52. The fixed portion 52 is provided on a sleeve 54 attached to the primary shaft 26, and the movable portion 53 is mounted on the sleeve 54 so as to be movable in the axial direction. The groove width is variable by the fixed portion 52 and the movable portion 53. A primary pulley 51 is configured.

  As shown in FIG. 2, a cam surface 56 is formed on the back surface of the movable portion 53, and a cam plate 57 is provided on the sleeve 54 so as to face the cam surface 56. A portion inclined in the direction in which the outer portion approaches the movable portion 53 is provided. A columnar centrifugal weight 58 is mounted between the movable portion 53 and the cam plate 57 so as to face the direction perpendicular to the rotation center of the primary shaft 26. Therefore, when the rotation of the crankshaft 13 becomes a predetermined rotation speed or higher and the rotation speed of the primary shaft 26 is increased in a state where the crankshaft 13 and the primary shaft 26 are engaged via the centrifugal clutch 30, The centrifugal weight 58 is moved radially outward by centrifugal force, and the groove width of the primary pulley 51 is narrowed.

  A secondary pulley 61 is attached to the secondary shaft 27. The secondary pulley 61 has a fixed sheave, that is, a fixed portion 62 having a conical surface formed on the surface 62a side, and a movable sheave, that is, a movable portion 63, having a conical surface opposite to the fixed portion 62 formed on the surface 63a side. Yes. The fixed portion 62 is disposed on the outer end side of the secondary shaft 27, that is, the case cover 25 b side, and the movable portion 63 is disposed on the inner side of the fixed portion 62. The fixed portion 62 is provided on a sleeve 64 attached to the secondary shaft 27, and the movable portion 63 is mounted on the sleeve 64 so as to be movable in the axial direction. The groove width is variable by the fixed portion 62 and the movable portion 63. A secondary pulley 61 is configured. A V-belt 66 is stretched between the primary pulley 51 and the secondary pulley 61, and a continuously variable transmission 67 is constituted by the V-belt 66 and both pulleys 51, 61.

  A compression coil spring 69 as a spring member is mounted between the stopper 68 fixed to the sleeve 64 of the secondary shaft 27 and the movable portion 63 in order to apply a tightening force to the V belt 66 to the movable portion 63. Has been. Therefore, when the rotation speed of the primary shaft 26 increases and the centrifugal weight 58 moves radially outward by centrifugal force, the groove width of the primary pulley 51 is reduced, so that the groove width of the secondary pulley 61 is reduced. It is spread against the spring force of the compression coil spring 69. Thereby, the winding diameter of the V belt 66 around the secondary pulley 61 becomes smaller than the winding diameter of the V belt 66 around the primary pulley 51, and the gear ratio of the continuously variable transmission 67 changes to the high speed stage side.

  The continuously variable transmission 67 is accommodated in a waterproof chamber in the transmission case 25, that is, an accommodation chamber 70. A cooling air introduction duct 71 is provided on the primary pulley 51 side of the case base 25a of the transmission case 25, and a cooling air discharge duct 72 is provided on the secondary pulley 61 side. The cooling air introduction duct 71 communicates with the storage chamber 70 via the cooling air introduction port 71a. The cooling air introduction port 71a is shifted to the engine side, that is, the centrifugal clutch 30 side with respect to the primary pulley 51, so that the cooling air introduction is performed. The port 71a protrudes into the housing chamber 70 in the case base 25a and faces the partition wall 25c that houses the centrifugal clutch 30. On the other hand, the cooling air discharge duct 72 communicates with the housing chamber 70 via the cooling air discharge port 72 a, and the cooling air discharge port 72 a is shifted to the transmission case 11 side with respect to the secondary pulley 61.

  As shown in FIG. 3, the cooling air introduction duct 71 is provided at the lower portion of the front end portion of the transmission case 25 when the power transmission system is mounted on the vehicle. The discharge duct 72 is provided in a portion of the rear end portion of the transmission case 25 that is above the cooling air introduction duct 71.

  A centrifugal fan 73 is provided on the fixed portion 52 of the primary pulley 51. The cooling air introduced from the cooling air introduction duct 71 by the centrifugal fan 73 flows along the continuously variable transmission 67 and is then discharged from the cooling air discharge duct 72. As shown in FIG. 5, the centrifugal fan 73 has a plurality of fan blades 74 that protrude in the axial direction from the back surface of the fixed portion 52 and have a circular cross section, and each fan blade 74 is fixed. The unit 52 is integrally provided. Each of the fan blades 74 is provided on the back surface of the fixed portion 52 so that the concave surface faces the rotation direction, is spaced at a constant interval in the circumferential direction, and is generally annular.

  The centrifugal fan 73 has a suction portion 75a of the centrifugal fan 73 at the inside in the radial direction of each fan blade 74 and a blowout portion 75b at the outside in the radial direction, and the cooling air flowing from the suction portion 75a flows into the fan blade 74. Discharged radially outward. As shown in FIGS. 3 and 4, in order to guide the cooling air flowing in from the cooling air introduction duct 71 to the suction portion 75 a, an arcuate guide plate 76 surrounds the secondary pulley 61 side of the fixed portion 52. The guide plate 76 is provided in the case base 25 a and protrudes into the storage chamber 70.

  As shown in FIG. 2, an annular partition plate 77 is attached to the centrifugal fan 73 by bolts 78 so as to be in contact with the axial tips of the respective fan blades 74. Has a through hole 79 for guiding the cooling air introduced from the cooling air introduction port 71 a to the central portion in the radial direction of the centrifugal fan 73. As shown in FIG. 5, a plurality of mounting holes 78 a through which the bolts 78 pass are formed in the partition plate 77, and the partition plate 77 is fastened to the centrifugal fan 73 by the bolts 78.

  As shown in FIG. 2, the partition plate 77 is located inside the cooling air introduction port 71 a of the cooling air introduction duct 71, that is, on the left side in FIG. 2, and the blowing portion of the cooling air introduction port 71 a and the centrifugal fan 73. 75b is partitioned. The outer diameter of the partition plate 77 is set to be larger than the outer diameter of the centrifugal fan 73, and the outer peripheral portion of the partition plate 77 protrudes radially outward from the outer periphery of the centrifugal fan 73 as shown in FIG. Yes. In FIG. 2, the symbol T indicates the length of the partition plate 77 protruding outward from the outer diameter of the centrifugal fan 73. Therefore, the cooling air blown out from the blowing portion 75b is guided toward the inside of the storage chamber 70 as shown by an arrow in FIG. 2, and the cooling air is prevented from flowing back toward the cooling air introduction port 71a. .

  As shown in FIG. 3, the distal end portion of the transmission case 25 is curved in an arc shape along the outer peripheral surface of the centrifugal fan 73 via a cooling air guide gap 81, and the diameter of the centrifugal fan 73 is As shown in FIG. 2, the cooling air discharged into the gap 81 in the outward blowing portion 75 b is guided to the inner surface of the transmission case 25 and guided toward the primary pulley 51. As a result, the cooling air that has flowed into the gap 81 among the cooling air discharged radially outward from the centrifugal fan 73 is blown to the inner peripheral surface of the transmission case 25, but the outer diameter of the partition plate 77. Is larger than the outer diameter of the centrifugal fan 73, that is, the outer diameter of the fixed portion 52, so that the blown cooling air is surely guided toward the primary pulley 51 without flowing back to the cooling air introduction port 71a. Is done. Thus, the cooling air generated by the centrifugal fan 73 efficiently flows along the continuously variable transmission 67, and the cooling efficiency is improved.

  In the power transmission system 10 having the above-described continuously variable transmission 67, when the engine speed reaches a predetermined value or more, the crankshaft 13 and the primary shaft 26 are fastened by the centrifugal clutch 30 and the primary pulley 51 is rotationally driven. The rotation of the primary pulley 51 is transmitted to the secondary pulley 61 via the V belt 66, and the engine power is transmitted to the drive wheels via the output shafts 43a and 43b. By switching the switching mechanisms 45 and 46, the vehicle is switched to either forward travel or reverse travel, and the forward rotation of the primary shaft 26 is shifted by two stages with respect to the output shafts 43a and 43b to drive wheels. Communicated.

  When the primary pulley 51 rotates, the centrifugal fan 73 provided integrally with the fixed portion 52 is rotationally driven, so that the cooling air discharge duct 72 is supplied from the cooling air introduction duct 71 into the accommodation chamber 70 in the transmission case 25. Cooling air toward is generated. The generated cooling air flows along the primary pulley 51, the secondary pulley 61, and the V belt 66 constituting the continuously variable transmission 67, and cools them.

  When the centrifugal fan 73 is rotated, the cooling air flowing into the accommodation chamber 70 in the transmission case 25 from the cooling air introduction port 71a of the cooling air introduction duct 71 passes through the central portion of the partition plate 77 formed in the radial direction. It flows into the centrifugal fan 73 from the hole 79 through the suction portion 75a at the center in the radial direction. The cooling air pressurized by the centrifugal fan 73 is blown out to the blowout portion 75 b radially outward of the centrifugal fan 73. Of the blown cooling air, the cooling air blown toward the arc surface on the tip end side of the transmission case 25 hits the inner peripheral surface of the transmission case 25 and travels toward the case cover 25b via the gap 81. Thus, it flows into the inside of the storage chamber 70. Thereby, the cooling air is reliably guided to the movable portion 53 of the primary pulley 51 and the fixed portion 62 of the secondary pulley 61.

  The cooling air that hits the inner peripheral surface of the transmission case 25 is set so that the outer diameter of the partition plate 77 is larger than the outer diameter of the centrifugal fan 73, so that the cooling air introduction duct 71 has a cooling air introduction port 71 a side. It is surely blown out toward the storage chamber 70 without backflow. Thereby, it is possible to prevent the cooling air blown from the blowing portion 75b of the centrifugal fan 73 from flowing back to the cooling air introduction duct 71, and the flow rate of the cooling air flowing through the storage chamber 70 by the centrifugal fan 73 can be increased. The cooling efficiency of the continuously variable transmission 67 can be improved.

  In addition, the cooling air introduction duct 71 is disposed so as to face the connection end portion side of the primary shaft 26 with respect to the primary pulley 51, that is, the centrifugal clutch 30 that connects the crankshaft 13 and the primary shaft 26. A cooling air introduction duct 71 is provided in the transmission case 25 so as to overlap the centrifugal clutch 30. Thus, the cooling air introduction duct 71 can be provided in the transmission case 25 without increasing the width dimension of the transmission case 25, that is, the dimension of the transmission case 25 in the axial direction of the primary shaft 26.

  The present invention is not limited to the above-described embodiment, and various modifications can be made without departing from the scope of the invention. For example, the illustrated continuously variable transmission is provided with a centrifugal fan 73 on the back surface of the fixed portion 52 of the primary pulley 51. In addition, a centrifugal fan is also provided on the back surface of the fixed portion 62 of the secondary pulley 61. You may do it.

12 Crankcase 13 Crankshaft 25 Transmission case 26 Primary shaft 27 Secondary shaft 51 Primary pulley 52 Fixed portion 53 Movable portion 61 Secondary pulley 62 Fixed portion 63 Movable portion 66 V belt 67 Continuously variable transmission 70 Storage chamber 71 Cooling air introduction duct 71a Cooling air introduction port 72 Cooling air discharge duct 72a Cooling air discharge port 73 Centrifugal fan 74 Fan blade 75a Suction part 75b Outlet part 76 Guide plate 77 Partition plate

Claims (3)

V-belt continuously variable transmission for driving a vehicle comprising a primary pulley with variable groove width provided on the primary shaft, a secondary pulley with variable groove width provided on the secondary shaft, and a V-belt stretched over these pulleys A cooling device of
A transmission case having a storage chamber for storing the continuously variable transmission, and provided with a cooling air introduction duct and a cooling air discharge duct;
A centrifugal fan that is provided on the pulley and that cools the continuously variable transmission by introducing cooling air from the cooling air introduction duct and then discharges the cooling air to the cooling air discharge duct;
A partition plate that is attached to the centrifugal fan and partitions the cooling air introduction port of the cooling air introduction duct and the blowout portion of the centrifugal fan;
A cooling device for a V-belt type continuously variable transmission, wherein an outer peripheral portion of the partition plate that rotates integrally with the centrifugal fan protrudes radially outward from an outer periphery of the centrifugal fan.   2. The cooling device for a V-belt type continuously variable transmission according to claim 1, wherein the partition plate has a through hole that guides the cooling air introduced from the cooling air introduction port to a central portion in a radial direction of the centrifugal fan. A cooling device for a V-belt type continuously variable transmission.   3. The cooling device for a V-belt type continuously variable transmission according to claim 1 or 2, wherein the pulley has a fixed portion and a movable portion that moves in the axial direction along the rotation axis of the pulley with respect to the fixed portion. The cooling air inlet is formed in the vicinity of the fixed part, and the centrifugal fan is provided in the fixed part.

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