JP6479609B2 - Continuously variable transmission - Google Patents

Description

  The present invention relates to a continuously variable transmission that changes a gear ratio steplessly.

  Conventionally, a continuously variable transmission is known in which rotational power between pulleys is transmitted by a belt or chain wound around two pulleys.

  In such a continuously variable transmission, the temperature of the belt and other parts that are pressed against the pulleys is likely to increase due to friction, and the inner peripheral part of the pulleys, such as the inner peripheral part of each pulley and the space between the pulleys. It is easy to heat up.

  In particular, in a dry-type continuously variable transmission in which a mechanism for supplying hydraulic oil to a belt or the like is omitted, the cooling effect by the hydraulic oil cannot be obtained, and there is a risk of overheating the above-described portions.

  Therefore, a technique for air-cooling the continuously variable transmission has been proposed.

  For example, an air cooling structure using an air flow accompanying a circular motion of a belt or the like has been studied.

  As such a structure, a structure that promotes air cooling with an airflow generated by blades (fins) provided on the outer peripheral side of the belt or the back surface of the pulley (see Patent Documents 1 and 2), or occurs along the inner periphery of the belt. For example, a structure that promotes air cooling by rectifying the airflow (see Patent Document 3).

Japanese Patent Laid-Open No. 07-12207 JP 2006-29486 A JP 2003-287110 A

  However, in the structure in which the blades or pulleys are provided with the blades as described above, it is difficult to supply the air current to the portion surrounded by the belt or the like, and the air current generated on the inner peripheral side of the belt due to the circular motion is weak in the first place For this reason, a sufficient cooling effect may not be obtained.

  Therefore, there is room for improvement in cooling the continuously variable transmission.

  The present invention has been made in view of the above-described problems, and relates to a continuously variable transmission and an object of the present invention is to reliably cool.

  It is to be noted that the present invention is not limited to the purpose herein, and is an operational effect derived from each configuration shown in [Mode for Carrying Out the Invention] to be described later, and also exhibits an operational effect that cannot be obtained by conventional techniques. It can be positioned as another purpose.

  (1) In order to achieve the above object, the continuously variable transmission according to the present invention is sandwiched between the first pulley and the second pulley to rotate while being sandwiched between the first pulley and the second pulley. A hollow rotor that transmits power to the pulley, and blades that rotate integrally with the rotor to generate a radial airflow.

  (2) It is preferable that the blade sucks airflow from one side of the outer periphery of the rotor and discharges airflow to the other side of the outer periphery of the rotor.

  (3) The continuously variable transmission of the present invention preferably has an intake port for sucking an airflow.

  (4) Further, it is preferable that the intake port is provided in a forward direction of the vehicle.

  (5) The continuously variable transmission of the present invention preferably has an exhaust port for discharging the airflow.

  (6) It is preferable that the said rotor has a side wall part in each axial both ends, and the said side wall parts are connected with the said blade | wing.

  (7) The rotor includes a plurality of protrusions that are provided so as to protrude intermittently side by side on the same circumference on the outer side in the axial direction of the side wall portion, and that are pressed against the first pulley and the second pulley. It is preferable to have.

  (8) Furthermore, it is preferable to have a plurality of communication holes that are formed in the side wall portion and are provided on the inner peripheral side of the projection portion.

  According to the continuously variable transmission of the present invention, when power is transmitted from the first pulley to the second pulley, the air current generated by the blades rotating integrally with the rotor, the portions around the rotor and the rotor itself Therefore, the continuously variable transmission can be reliably cooled.

FIG. 1 is a cross-sectional view showing a main part of a continuously variable transmission according to an embodiment of the present invention. FIG. 2 is a schematic cross-sectional view for explaining the shift in the continuously variable transmission according to the embodiment of the present invention. FIG. 2 (a) shows the one with the lowest gear ratio, and FIG. 2 (b) shows the one with the highest gear ratio. FIG. 3 is a perspective view showing a rotor of a continuously variable transmission according to an embodiment of the present invention.

  Embodiments relating to a continuously variable transmission according to the present invention will be described with reference to the drawings.

  The continuously variable transmission is installed in a power transmission system of a vehicle such as an automobile or a motorcycle.

  In the present embodiment, the radial direction and the circumferential direction are determined based on the axis of each member.

[I. One Embodiment]
[1. Constitution]
Hereinafter, the configuration of a continuously variable transmission according to an embodiment will be described.

  In the present embodiment, a dry type continuously variable transmission will be described as an example.

[1-1. Basics of continuously variable transmission]
First, the basic function and structure of the continuously variable transmission 1 will be described with reference to FIGS. 1 and 2.

  The continuously variable transmission 1 is a mechanism that continuously outputs a rotation input from a drive source such as an engine or an electric motor (both not shown) by a transmission mechanism 9 and outputs the rotation.

  The rotation output from the continuously variable transmission 1 is transmitted to drive wheels (both not shown) via a shaft and a differential mechanism.

  The transmission mechanism 9 is provided in a predetermined closed space S in the transmission case 2.

  The transmission mechanism 9 includes two pulleys 10 and 20 and a rotor 30 that bears power transmission between the pulleys 10 and 20.

The shafts 11, 21, 31 and the shaft centers C ₁ , C ₂ , D of the pulleys 10, 20 and the rotor 30 are arranged in parallel.

Pulleys 10 and 20 and a rotor 30 are disposed along a power transmission axis P (see FIG. 2) orthogonal to a direction along these axial centers C ₁ , C ₂ and D (hereinafter referred to as “axial direction”). ing. The power transmission axis P here is a virtual line extending along the power transmission direction between the pulleys 10 and 20 and passing between the two sheaves 12 and 22 of the pulleys 10 and 20.

  In the following description, the pulleys 10 and 20 and the rotor 30 will be described on one side with respect to the power transmission axis P, and the description on the other side will be omitted.

  Of the two pulleys 10 and 20, rotational power is input to the primary pulley (first pulley) 10 on the upstream side in the power transmission direction, and the speed is changed from the secondary pulley (second pulley) 20 on the downstream side in the power transmission direction. The rotated power is output.

  The rotor 30 is a hollow rotating member that transmits power from the primary pulley 10 to the secondary pulley 20 by being rotated while being sandwiched between the primary pulley 10 and the secondary pulley 20.

  Hereinafter, the primary pulley 10, the secondary pulley 20, and the rotor 30 will be described in this order.

  The primary pulley 10 has a pulley shaft 11, a sheave 12, and a joint 13 that are arranged to face each other.

These pulley shaft 11, the sheave 12, the joint 13 is provided on the axis C ₁ and concentric with the primary pulley 10 in a predetermined state, it rotates integrally.

  The predetermined state is a state in which the sheave 12 is supported by the joint 13 so as to be orthogonal to the pulley shaft 11. Here, the speed change mechanism 9 has a constant speed ratio (rotational speed of the primary pulley 10: secondary pulley). 20 rotation speed = 1: 1).

  The pulley shaft 11 is a shaft member that is connected to a drive source (not shown) and receives rotational power.

  The sheave 12 is a disk-shaped member that is pressed against the rotor 30 in the axial direction.

  The sheave 12 comes into contact with the rotor 30 at a surface (hereinafter referred to as “sheave surface”) 12 a on the side close to the power transmission axis P.

  Here, the radial cross-sectional shape of the sheave surface 12a is curved so as to be separated from the power transmission axis P toward the outer periphery in a predetermined state.

  The sheave 12 is connected to a joint 13 described below on a surface 12b (hereinafter referred to as "sheave back surface") on the back side of the sheave surface 12a.

  The joint 13 is a joint that connects the sheave 12 to the pulley shaft 11 so as to be tiltable.

  Here, a constant velocity joint (so-called CVJ) is used as the joint 13.

  The secondary pulley 20 has a pulley shaft 21, a sheave 22, and a joint 23.

  The pulley shaft 21, sheave 22, and joint 23 are provided in the same manner as the pulley shaft 11, sheave 12, and joint 13 of the primary pulley 10 except that the power transmission direction of the pulley shaft is opposite.

  As shown in FIGS. 2 and 3, the rotor 30 is composed of a rotor shaft 31 and a side wall 32, and further has a protrusion 33 and a blade 34.

  These protrusions 33 and blades 34 rotate integrally with the rotor 30.

  The rotor shaft 31 and the side wall portion 32 are disposed concentrically with the axis D of the rotor 30.

  A plurality of protrusions 33 and blades 34 are provided on the circumference centered on the axis D and arranged at equal intervals or substantially equal intervals (intermittently).

  The rotor shaft 31 is a rotating shaft that supports the rotor 30.

  Further, the rotor shaft 31 is supported so as to be movable along the power transmission direction.

  Therefore, the rotor 30 supported by the rotor shaft 31 is also movable along the power transmission direction.

  For example, the rotor shaft 31 is supported in the long hole 39 (see FIG. 3).

  The long hole 39 is formed in the transmission case 2 (see FIG. 1), a short diameter is set according to the outer diameter of the rotor shaft 31, and a long diameter is set according to the moving range of the rotor 30. The

  The side wall part 32 is a disk-shaped member.

  Two side walls 32 are arranged side by side in a direction orthogonal to the axis D.

  That is, the side wall portions 32 are provided to face each other.

  A plurality of protrusions 33 project from the side surfaces (outside in the axial direction) of the side wall portions 32 facing the respective sheave surfaces 12a.

  Each protrusion 33 is formed in a hemispherical shape.

  These protrusions 33 are pressed against the sheave surface 12a (see FIG. 2).

  The two side wall portions 32 are connected by the rotor shaft 31 and the blades 34.

  That is, the blades 34 are provided as a part of the structure that connects the side wall parts 32, that is, as a part of the rotor 30 as a power transmission member.

  Details of the blade 34 will be described later.

  Further, as shown in FIGS. 1, 2, and 3, a plurality of communication holes 32 a are formed in each side wall portion 32.

  Here, each communication hole 32a has a fan shape as viewed in the axial direction.

  Further, the communication hole 32 a is disposed on the inner peripheral side with respect to the protrusion 33 and the blade 34.

  Details of the communication hole 32a will be described later.

[1-2. Transmission system]
Next, a configuration (transmission system) for changing the transmission ratio in the transmission mechanism 9 will be described.

  In this speed change mechanism 9, the gear ratio is changed by expanding or reducing the contact radius r between each of the sheaves 12 and 22 and the rotor 30.

  Here, a mechanism (hereinafter referred to as “tilting mechanism”) 40 that changes the contact radius r of the sheaves 12 and 22 with respect to the rotor 30 by tilting the sheaves 12 and 22 with respect to the pulley shafts 11 and 21 is illustrated. explain.

  The same tilting mechanism 40 is provided for each of the two pulleys 10 and 20.

  Here, the tilt mechanism 40 of the primary pulley 10 will be described as an example with reference to FIG.

  The tilt mechanism 40 is provided with a fixed portion 41 that is fixed to the transmission case 2 (see FIG. 1) and does not rotate, and a rotating portion 45 that rotates integrally with the pulley shaft 11, the sheave 12, and the joint 13.

  Hereinafter, the fixing unit 41 and the rotating unit 45 will be described in this order.

[1-2-1. Fixed system]
The fixed portion 41 is provided with an oil passage (hereinafter referred to as “fixed oil passage”) 42 through which hydraulic oil is supplied.

  The fixed oil passage 42 is provided extending along the axial direction.

  The fixed oil passage 42 is provided with two types arranged on the same circumference as viewed in the axial direction.

Specifically, one fixed oil passage (hereinafter referred to as “first fixed oil passage”) 42 </ b> A is provided on the side closer to the secondary pulley 20 (right side in FIG. 2) with the axis C ₁ as a reference, and the secondary pulley The other fixed oil passage (hereinafter referred to as “second fixed oil passage”) 42 </ b> B is provided on the side far from 20 (left side in FIG. 2).

  Each of the fixed oil passages 42A and 42B extends in a long hole shape (for example, an arc shape) when viewed in the axial direction.

  Further, one end portion 11 a of the pulley shaft 11 is rotatably supported by the fixed portion 41 via a bearing 49.

[1-2-2. Rotating system]
The rotating portion 45 is provided with an oil passage (hereinafter referred to as “rotating oil passage”) 46 through which hydraulic oil is supplied.

  The rotary oil passage 46 is provided extending along the axial direction.

  The rotary oil passage 46 is aligned with the fixed oil passage 42 in the radial direction, and the rotary oil passage 46 and the fixed oil passage 42 are provided intermittently side by side so as to overlap in the axial direction.

Since the rotating portion 45 rotates, the rotating oil passage 46 is, in a predetermined rotation phase, one rotating oil passage (hereinafter referred to as “first rotating oil passage”) located on the side closer to the secondary pulley 20 with respect to the axis C _1. functions as) 46A that "in certain rotational phase in phase of half a rotation amount corresponding to the advance side or the retard side than the other rotating fluid passage located on the far side from the secondary pulley 20 the axis C ₁ as reference 46B (hereinafter referred to as “second rotating oil passage”).

  A plurality of first rotating oil passages 46A are provided corresponding to the first fixed oil passage 42A, and a plurality of second rotating oil passages 46B are provided corresponding to the second fixed oil passage 42B.

  A piston 47 is inserted into each of the rotating oil passages 46.

  The piston 47 is provided so as to freely reciprocate in the rotating oil passage 46.

  One end 47a of the piston 47 receives the pressure of the hydraulic oil, and the other end 47b contacts the sheave back surface 12b.

  Further, the pulley shaft 11 is supported by the rotating portion 45 so that the end portions 11 a and 11 b protrude from the rotating portion 45 so as not to be relatively rotatable.

  One end portion 11 a protruding to the fixed portion 41 side of the pulley shaft 11 is supported by the fixed portion 41 via a bearing 49.

  A joint 13 is connected to the other end portion 11 b protruding to the sheave 12 side of the pulley shaft 11.

[1-2-3. Shifting operation]
Next, the speed change operation of the speed change mechanism 9 will be described.

  First, the case where the gear ratio is shifted to the Low side will be described with reference to FIG.

  In this case, as shown by the black arrow, the high-pressure hydraulic oil is supplied to the second fixed oil passage 42B rather than the first fixed oil passage 42A.

  Therefore, higher-pressure hydraulic oil is supplied to the second rotating oil passage 46B than to the first rotating oil passage 46A.

  Therefore, the piston (hereinafter referred to as “second piston”) 47B in the second rotational oil passage 46B is closer to the power transmission axis P than the piston (hereinafter referred to as “first piston”) 47A in the first rotational oil passage 46A. It is pushed out so strongly.

And on the side closer to the secondary pulley 20 with respect to the axis C ₁ , the sheave 12 is separated from the power transmission axis P, and the axial distance between the facing sheaves 12 becomes longer.

Further, on the side far from the secondary pulley 20 with respect to the axis C ₁ , the sheave 12 approaches the power transmission axis P, and the axial distance between the facing sheaves 12 is shortened.

At this time, the rotor 30 moves in a direction approaching the axis C ₁ of the primary pulley 10.

Therefore, the contact radius r ₁ between the sheave 12 and the rotor 30 is reduced, and the gear ratio is changed to the Low side.

  On the contrary, the case where the gear ratio is changed to the High side will be described with reference to FIG.

  In this case, as indicated by the black arrow, the high-pressure hydraulic oil is supplied to the first fixed oil passage 42A rather than the second fixed oil passage 42B.

  Therefore, higher-pressure hydraulic oil is supplied to the first rotating oil passage 46A than to the second rotating oil passage 46B.

  Therefore, the first piston 47A is pushed more strongly toward the power transmission axis P than the second piston 47B.

Then, on the side closer to the secondary pulley 20 with respect to the axis C ₁ , the sheave 12 approaches the power transmission axis P, and the axial distance between the sheaves 12 becomes shorter.

Further, on the side far from the secondary pulley 20 with respect to the axis C ₁ , the sheave 12 is separated from the power transmission axis P, and the axial distance between the sheaves 12 becomes longer.

At this time, the rotor 30 moves in a direction away from the axis C ₁ of the primary pulley 10.

Therefore, the contact radius r ₂ between the sheave 12 and the rotor 30 is increased, and the gear ratio is changed to the High side.

[1-3. Cooling system]
Next, a configuration (cooling system) for cooling the transmission mechanism 9 will be described with reference to FIG.

  Here, a structure (air cooling structure) for cooling each member using an air flow (cooling air) inside the transmission case 2 will be described.

  First, the rotor 30 will be described focusing on the blades 34 and the communication holes 32a.

  The blades 34 function as a part of the power transmission member and also have a function as a member for supplying an airflow.

  That is, the blades 34 also function as a blowing member that rotates integrally with the rotor 30 to generate an airflow.

  Therefore, it can be said that the rotor 30 is a power transmission member and a blower fan.

  The blades 34 extend in the radial direction, and generate an air flow in the radial direction when the rotor 30 rotates.

Here, one side of the outer periphery of the rotor 30 (e.g. the upper right side of Fig. 1) air flow to the suction from A _1, the other side of the outer periphery of the rotor 30 (e.g. the lower side in FIG. 1) to A ₂ for ejecting air flow The blade 34 will be described as an example.

  That is, in the rotor 30, when the air flow is sucked and discharged in the radial direction like a so-called cross flow fan (also called a cross flow fan, a cross flow fan, a line flow fan or a tangential fan), A passing airflow (throughflow) is generated.

  Note that the airflow suction direction and the discharge direction can be set by adjusting the shape of the blades 34 based on the rotation direction of the rotor 30.

  The communication hole 32 a not only functions as a hole in the side wall portion 32, but also functions as an air outlet for passing through the hollow interior of the rotor 30.

  That is, the airflow generated by the blades 34 is not only discharged to the other side of the outer periphery of the rotor 30 but also discharged from the communication hole 32a.

  Next, the peripheral structure of the rotor 30 will be described.

  Specifically, the intake port 3 and the intake passage 4 for introducing outside air, and the exhaust port 5 and the exhaust passage 6 for discharging air in the closed space S will be described.

  The intake port 3 is an opening provided in the transmission case 2.

  By this intake port 3, the closed space S of the transmission case 2 communicates with the outside.

  Here, the air inlet 3 is provided in the forward direction of the vehicle.

  The intake passage 4 is a flow path for introducing outside air from the intake port 3 to one side of the outer periphery of the rotor 30.

  The intake passage 4 is formed linearly.

  The exhaust port 5 is an opening provided in the transmission case 2 similarly to the intake port 3.

  However, the exhaust port 5 is disposed on the opposite side of the intake port 3 with the rotor 30 interposed therebetween in the axial direction.

  The exhaust passage 6 is a flow path for discharging the air inside the closed space S to the outside.

  Specifically, the space from the other side of the outer periphery of the rotor 30 to the exhaust port 5 is the exhaust passage 6.

  In addition to the rotor 30, a separation wall 7 connected to the transmission case 2 is provided between the intake passage 4 and the exhaust passage 6.

  The partition wall 7 surrounds a part of the intake passage 4.

  That is, the intake passage 4 and the exhaust passage 6 are separated by the separation partition 7.

  Here, the separation wall 7 is connected so as to move integrally with the rotor 30.

[2. Effect and effect]
Since the continuously variable transmission 1 of the present embodiment is configured as described above, the following operations and effects can be obtained.

[2-1. Action]
Here, the operation will be described by paying attention to the flow of airflow in the closed space S of the continuously variable transmission 1.

  In the transmission mechanism 9 of the continuously variable transmission 1, when power is transmitted from the primary pulley 10 to the secondary pulley 20, the rotor 30 pressed against the sheave surfaces 12 a and 22 a rotates for power transmission, and accordingly. The blades 34 also rotate.

  Therefore, the air in the closed space S is sucked from one side of the outer periphery of the rotor 30 by the blades 34 and discharged from the other side of the outer periphery of the rotor 30 and discharged from the communication hole 32a of the rotor 30 in the axial direction. The

  Since air is sucked and discharged in this way, an air flow is generated by the blades 34 as indicated by white arrows in FIG.

  Speaking in detail from the upstream side regarding the flow of the airflow, the outside air sucked from the intake port 3 flows through the intake passage 4 and is introduced to one side of the outer periphery of the rotor 30, passes through the hollow interior of the rotor 30, and passes through the rotor. It is discharged to the other side of the outer periphery of the 30 communication holes 32 a or the rotor 30, flows through the exhaust passage 6, and is discharged from the exhaust port 5.

[2-2. effect]
Next, the effect of the continuously variable transmission 1 will be described.

  (1) In the continuously variable transmission 1, when power is transmitted from the primary pulley 10 to the secondary pulley 20, radial airflow is generated by the blades 34 that rotate integrally with the rotor 30.

This airflow circulates through the locations exemplified below.
Location 1: Space between primary pulley 10 and secondary pulley 20 Location 2: Inner circumference of pulleys 10 and 20
(Inner peripheries of sheave surfaces 12a, 22a)
Location 3: Pressure contact portion of pulleys 10 and 20 to rotor 30
(Contact portion between sheave surfaces 12a and 22a and protrusion 33)
Location 4: Hollow interior of rotor 30

  In the conventional continuously variable transmission, the above locations 1 and 2 are surrounded by belts and chains that are wound around two pulleys, so that heat is easily trapped.

  However, according to the continuously variable transmission 1 of the present embodiment, the locations 1 and 2 are not surrounded by the rotor 30 that functions as a power transmission member, so that exhaust heat at the locations 1 and 2 can be promoted. .

  Further, the air flow generated by the blades 34 is discharged to the other side of the outer periphery of the rotor 30, so that the places 1 and 2 can be exhausted.

  Further, the temperatures of the above-described portions 3 and 4 are likely to rise due to the pressure contact or friction between the rotor 30 and the pulleys 10 and 20.

  However, according to the continuously variable transmission 1 of the present embodiment, the air flow caused by the blades 34 is discharged from the communication hole 32a of the rotor 30 so that the above-described portion 3 can be cooled. By passing through, the portion 4 can be cooled.

  Therefore, the continuously variable transmission 1 can be reliably cooled.

  (2) The blades 34 suck airflow from one side of the outer periphery of the rotor 30 and discharge the airflow to the other side of the outer periphery of the rotor 30.

  Therefore, the outside air introduced with respect to said location 1 and 2 arrange | positioned on the other side among the outer periphery of the rotor 30 is sprayed, and the exhaust heat property of the location where it is easy to trap heat can be improved.

  (3) Since the air that has been sucked into the intake passage 4 from the intake port 3 is guided to the portion where the air flow is sucked into the rotor 30, that is, one side of the outer periphery of the rotor 30, the outside air is sucked into the rotor 30. The efficiency can be improved, and the cooling efficiency of the transmission mechanism 9 can be increased.

  (4) Furthermore, since the intake port 3 is provided in the forward direction of the vehicle, the suction efficiency of the airflow to the rotor 30 can be further improved, and the cooling efficiency of the transmission mechanism 9 can be reliably increased.

  (5) Since the airflow discharged to the other side of the outer periphery of the rotor 30 flows through the exhaust passage 6 and is discharged from the exhaust port 5, the discharge efficiency of the airflow from the rotor 30 can be improved. The exhaust heat efficiency of the transmission mechanism 9 can be increased.

  (6) Since the two sidewalls 32 are connected to each other by the blades 34 in the rotor 30, the blades 34 are a part (one structure) of the rotor 30 as a power transmission member and a blower member that generates an air flow. is there.

  Therefore, the continuously variable transmission 1 can be cooled by using the blades 34 that are a part of the rotor 30 not only as a power transmission member but also as a blower member.

  Therefore, the cooling performance can be improved while suppressing the complexity of the structure of the power transmission member.

  (7) The plurality of protrusions 33 projecting from the side wall part 32 are likely to rise in temperature due to pressure contact or friction with the sheave surfaces 12a, 22a.

  However, since the protrusions 33 are provided intermittently side by side, a space is secured between the protrusions 33 to ensure heat dissipation, and the protrusion 33 extends to suppress the temperature rise of the rotor 30. it can.

  Further, since a plurality of protrusions 33 provided intermittently at the contact portions of the rotor 30 with the sheave surfaces 12a and 22a of the pulleys 10 and 20 are provided, the pulley 10 is compared with a structure in which the protrusions continuously extend. , 20 is small, the frictional force between the pulleys 10, 20 and the rotor 30 can be secured, and the power transmission efficiency can be improved.

  (8) Since the side wall 32 is hollowed by the communication hole 32a in which the side wall 32 is formed and the interior of the rotor 30 is hollow, the rotor 30 and the continuously variable transmission 1 can be reduced in weight.

  Furthermore, since the airflow is discharged from the communication hole 32a provided on the inner peripheral side with respect to the protrusion 33, the airflow is efficiently blown to the portion 3 and the vicinity thereof, and the transmission mechanism 9 can be efficiently cooled. .

  Since the partition wall 7 is connected so as to move integrally with the rotor 30, the suction and discharge efficiency of the airflow in the rotor 30 can be increased, and the cooling efficiency of the transmission mechanism 9 can be improved.

[II. (Modification)
Although one embodiment has been described above, the present invention is not limited to the above-described embodiment, and various modifications can be made without departing from the spirit of the present invention. Each structure of one Embodiment mentioned above can be selected as needed, and may be combined suitably.

  For example, the direction of the airflow described above may be set in the opposite direction by changing the shape or arrangement of the blades 34.

  In this case, the airflow flows in the direction opposite to the direction indicated by the white arrow in FIG.

  The airflow sucked or discharged to the rotor 30 may be an axial flow.

  That is, the airflow in the rotor 30 may be discharged or sucked in the radial direction while being sucked or discharged in the axial direction, like the airflow of the blower.

  In this case, a hollow shaft is used as the rotor shaft 31, and the space inside the hollow shaft serves as an intake / exhaust passage.

  Moreover, you may use the blade | wing of a structure like what is called a sirocco fan.

  The blades 34 are not limited to a part of the structure of the rotor 30. For example, after providing another structural member that connects the side wall portions 32, blades that generate airflow in the radial direction may be provided.

  A rectifying plate that rectifies the airflow may be provided at any location in the closed space S (for example, around the intake passage 4, the exhaust passage 6, and the rotor 30).

  In this case, the cooling efficiency can be improved by arranging the current plate so that the airflow is blown to the desired cooling location or is sucked out from the desired cooling location.

  The intake port 3 or the exhaust port 5 may be provided with a check valve or a filter for preventing foreign matters such as dust and moisture from entering the closed space S.

  In this case, although the cooling performance is reduced and the cost of parts is increased, the entry of foreign matter into the closed space S is suppressed, and the durability of the continuously variable transmission 1 can be improved.

  The piston 47 of the tilting mechanism 40 may be driven in and out not only with hydraulic oil but also with compressed air (compressed fluid).

  The speed change mechanism 9 is not limited to the tilting mechanism 40, and a mechanism such as a conventional continuously variable transmission that separates and contacts the sheaves that are arranged to face each other in one pulley and form a V groove may be used.

DESCRIPTION OF SYMBOLS 1 Continuously variable transmission 2 Transmission case 3 Intake port 4 Intake passage 5 Outlet 6 Exhaust passage 7 Separation partition 9 Transmission mechanism 10 Primary pulley (first pulley)
11 pulley shaft 11a one end 11b other end 12 sheave 12a sheave surface 12b sheave back surface 13 joint 20 secondary pulley (second pulley)
21 Pulley shaft 22 Sheave 22a Sheave surface 23 Joint 30 Rotor 31 Rotor shaft 32 Side wall portion 32a Communication hole 33 Projection portion 34 Blade 39 Shaft hole 40 Tilt mechanism 41 Fixed portion 42 Fixed oil passage 42A First fixed oil passage 42B Second fixed oil one side a of the outer circumference of the road 45 rotating portion 46 rotates oil passage 46A first rotation oil passage 46B second rotating fluid passage 47 piston 47a one end 47b other end 47A first piston 47B the second piston 49 bearing a ₁ rotor 30 ₂ Outer circumference of the rotor 30 C ₁ axis of the other side C ₁ primary pulley 10 C ₂ axis of the secondary pulley 20 D axis of the rotor 30 P power transmission axis S predetermined closed space r, r ₁ , r ₂ contact radius

Claims (8)

A hollow rotor that transmits power from the first pulley to the second pulley by rotating while being sandwiched between the first pulley and the second pulley;
A continuously variable transmission having blades that rotate integrally with the rotor to generate a radial airflow. In claim 1,
The continuously variable transmission, wherein the blade sucks airflow from one side of the outer periphery of the rotor and discharges airflow to the other side of the outer periphery of the rotor. In claim 1 or 2,
A continuously variable transmission having an intake port for sucking an airflow. In claim 3,
The continuously variable transmission, wherein the intake port is provided in a forward direction of the vehicle. In any one of Claims 1-4,
A continuously variable transmission having an exhaust port for discharging an airflow. In any one of Claims 1-5,
The rotor has side wall portions at both axial end portions,
The continuously variable transmission characterized in that the side wall portions are connected by the blades. In claim 6,
The rotor includes a plurality of protrusions that are provided to protrude intermittently side by side on the same circumference on the outer side in the axial direction of the side wall and that are pressed against the first pulley and the second pulley. A continuously variable transmission. In claim 7,
A continuously variable transmission having a plurality of communication holes provided in the side wall portion and provided on an inner peripheral side of the projection portion.

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