Pulley device, continuously variable transmission and vehicle

Abstract

To provide a technology capable of decreasing a moment of inertia of a movable sheave in a pulley device.SOLUTION: A pulley device disposed on an output shaft of a power source includes a fixed sheave fixed to the output shaft, and a movable sheave movable in an axial direction of the output shaft with respect to the fixed sheave. A wall part having a lateral surface that becomes an outermost end in a radial direction in the movable sheave is disposed so as to extend in the axial direction on an outer peripheral part of the movable sheave. The wall part partially includes a recess dented inward in the radial direction at an end part on a side of the fixed sheave in the lateral surface.SELECTED DRAWING: Figure 4

Description

[Technical Field]

[0001] The present invention relates to a pulley device that can be applied mainly to a continuously variable transmission. [Background technology]

[0002] In recent years, research and development has been conducted into improving fuel efficiency, which contributes to energy efficiency, in order to ensure that more people have access to affordable, reliable, sustainable and advanced energy. [Prior art documents] [Patent documents]

[0003] [Patent Document 1] Patent Publication No. 2021-193315 Summary of the Invention [Problem to be solved by the invention]

[0004] Patent Document 1 describes a structure in which multiple rollers are built into the drive pulley of a continuously variable transmission, and the movable sheave is movable by the centrifugal force generated by each roller. In the case of a movable sheave constituting a pulley device of a continuously variable transmission, if the weight of the outer periphery is large, the moment of inertia increases accordingly, which requires the throttle to be opened widely during acceleration, which may hinder improvements in fuel economy. Furthermore, there is a risk that drivability may deteriorate due to a decrease in responsiveness to throttle operation.

[0005] Therefore, an object of the present invention is to provide a technique capable of reducing the moment of inertia of a movable sheave in a pulley device, which in turn contributes to improving energy efficiency and drivability. [Means for solving the problem]

[0006] In order to achieve the above object, one aspect of the present invention is a pulley device provided on an output rotation shaft of a power source, the pulley device including: a fixed sheave fixed to the output rotation shaft; a movable sheave movable in an axial direction of the output rotation shaft relative to the fixed sheave; a plurality of weight rollers that move radially outward within the movable sheave by centrifugal force caused by rotation of the output rotary shaft, thereby pressing the movable sheave toward the fixed sheave; Equipped with the movable sheave has a contact surface that contacts each weight roller that moves radially outward, a wall portion having an outer surface that is the outermost end of the movable sheave in the radial direction is provided on an outer peripheral portion of the movable sheave and extends in the axial direction; a surface continuous with the abutment surface, the thickness of the portion of the wall portion on the fixed sheave side being thicker than the other portion; The wall portion has a recess partially recessed radially inward at an end portion of the outer surface on the fixed sheave side. The recesses are arranged on the outer surface at positions that overlap the contact surface in the circumferential direction, and the number of the recesses is the same as the number of weight rollers. , characterized by: [Effects of the Invention]

[0007] According to the present invention, it is possible to provide a technique that can reduce the moment of inertia of a movable sheave in a pulley device, and furthermore, it is possible to improve energy efficiency. [Brief explanation of the drawings]

[0008] [Figure 1] 1 is a schematic side view of a vehicle structure according to an embodiment; [Figure 2] 1 is a cross-sectional view showing an example of the structure of a continuously variable transmission (CVT). [Figure 3] FIG. 2 is an enlarged schematic view of the drive pulley and its surrounding area. [Figure 4] FIG. 10 is a perspective view of the drive pulley with the ramp plate removed. [Figure 5] FIG. 2 is a cross-sectional view showing a configuration example of a drive pulley. [Figure 6] FIG. 10 is a side view of the movable sheave as seen from the side (−X direction side). DETAILED DESCRIPTION OF THE INVENTION

[0009] Hereinafter, the embodiments will be described in detail with reference to the accompanying drawings. Note that the following embodiments do not limit the invention according to the claims, and not all combinations of features described in the embodiments are necessarily essential to the invention. Two or more of the features described in the embodiments may be arbitrarily combined. Furthermore, the same reference numerals are used for the same or similar components, and redundant explanations will be omitted.

[0010] <<Vehicle configuration examples>> FIG. 1 is a schematic side view of the structure of a vehicle 1 according to an embodiment. To facilitate understanding of the structure, the figure shows an X-axis, a Y-axis, and a Z-axis that are orthogonal to one another (the same applies to other figures described below). The X-axis corresponds to the front-rear direction, the Y-axis corresponds to the left-right direction, and the Z-axis corresponds to the up-down direction. In this specification, expressions such as front / rear, left / right (side), and up / down indicate relative positional relationships with respect to the vehicle body. For example, expressions such as "front" and "forward" correspond to the +X direction, and expressions such as "rear" and "rearward" correspond to the -X direction.

[0011] The vehicle 1 includes wheels 11, a power unit 12, and a driving operation mechanism 13. In this embodiment, the vehicle 1 is a two-wheeled vehicle that includes front wheels that are steered and rear wheels that are driven as wheels 11, and although the two-wheeled vehicle illustrated here is a scooter type, other examples include a saddle-ride type or a rider type. Furthermore, the number of wheels 11 is not limited to that in this example, and the vehicle 1 may be a four-wheeled vehicle, for example.

[0012] The power unit 12 includes a power source 121 and a power transmission mechanism 122. The power source 121 may be any known configuration capable of generating power, and in this embodiment, an internal combustion engine is used, but in other embodiments, an electric motor may be used. The power (rotation) of the power source 121 is transmitted to the rear wheels, which are drive wheels, via the power transmission mechanism 122. As will be described in detail later, the power transmission mechanism 122 includes a continuously variable transmission (CVT) 2, and power according to the gear ratio is transmitted to the rear wheels (see FIG. 2).

[0013] The driving operation mechanism 13 is mainly provided at a position accessible to the driver (rider) at the front of the vehicle, and is configured, for example, with multiple operators arranged on a handlebar that can change the direction of the front wheels, which are steered. Examples of the operators include an acceleration operator, a braking operator, and a direction indicator operator.

[0014] <<Configuration example of continuously variable transmission>> Fig. 2 is a cross-sectional schematic diagram showing an example of the structure of the CVT 2. In this embodiment, the CVT 2 includes pulley devices 21 and 22 arranged side by side in the X direction, and a belt 23 mounted thereon. Fig. 3 is an enlarged schematic diagram of the pulley device 21 and its surrounding area.

[0015] <About the drive pulley> The pulley device 21 is provided on an output rotation shaft AX1 of the power source 121 and receives power from the power source 121. The pulley device 21 will be referred to as a drive pulley 21 in the following description to distinguish it from the pulley device 22. The output rotation shaft AX1 is a rotation shaft (crankshaft in this embodiment) on the power source 121 side in the power transmission mechanism 122, and will be referred to as a drive shaft AX1 in the following description.

[0016] The drive pulley 21 includes a fixed sheave 21a, a movable sheave 21b, a torque cam mechanism 21c, a ramp plate 21d, and a weight roller 21e.

[0017] The sheaves 21a and 21b are generally conical in shape and are arranged opposite each other (the sheaves 21a and 21b may also be referred to as pulley halves). The fixed sheave 21a is fixed to the drive shaft AX1. The movable sheave 21b is supported by the drive shaft AX1 so as to be movable in the axial direction (the direction of the drive shaft AX1; in this embodiment, the Y direction) relative to the fixed sheave 21a. The diameter of the belt 23 wound around and between the sheaves 21a and 21b is kept small while the movable sheave 21b is separated from the fixed sheave 21a, and increases as the movable sheave 21b approaches the fixed sheave 21a.

[0018] The torque cam mechanism 21c is mounted around the drive shaft AX1 between the drive shaft AX1 and the movable sheave 21b, and in this embodiment includes a cam pin 211, a cam pin fixing structure 212, a cam groove forming structure 213, and a cam pin sealing structure 214. The cam pin fixing structure 212 is cylindrically configured to surround the drive shaft AX1 and is fixed to the drive shaft AX1, and the cam pins 211 are engaged with and fixed to the cam pin fixing structure 212. As a result, the cam pins 211 are arranged to extend radially outward from the drive shaft AX1 (in a direction away from the drive shaft AX1). A head 211h of the cam pin 211 extends radially outward from the cam pin fixing structure 212, and this head 211h can be configured to be rotatable. A plurality of cam pins 211 (for example, three) can be arranged. The cam groove forming structure 213 is fixed to the drive shaft AX1 and is cylindrically configured to surround the cam pin fixing structure 212 that fixes the cam pin 211, and has a cam groove T1, and is arranged so as to be movable in the axial direction relative to the cam pin fixing structure 212. The cam pin 211 fixed to the cam pin fixing structure 212 has a head portion 211h that is slidable relative to the cam groove T1 of the cam groove forming structure 213. A plurality of cam grooves T1 (for example, three) can be provided corresponding to the cam pins 211. The cam pin sealing structure 214 is configured in a cylindrical shape so as to surround the cam groove forming structure 213 , and seals the cam pin 211 so that the cam pin 211 does not come off the cam pin fixing structure 212 .

[0019] Here, the cam groove T1 extends in a direction inclined with respect to the axial direction, and as a result, the cam groove forming structure 213 receives a force (thrusting force) from the cam pin 211 that moves the movable sheave 21b in the axial direction (Y direction) due to the rotation of the drive shaft AX1. In this embodiment, the cam groove forming structure 213 receives a force (thrusting force) from the cam pin 211 in a direction (-Y direction) that moves the movable sheave 21b away from the fixed sheave 21a. With this structure, the cam groove forming structure 213 receives a force in the axial direction from the cam pin 211 due to the rotation of the drive shaft AX1, and the torque cam mechanism 21c generates a force that moves the movable sheave 21b in the axial direction.

[0020] Ramp plate 21d is disposed on the opposite side of fixed sheave 21a with respect to movable sheave 21b, and together with movable sheave 21b, forms a space for accommodating weight roller 21e, which will be described later. Groove portions 216, into which slide portions 215 of movable sheave 21b slidably fit, are partially (for example, in three locations) provided on the outer edge of ramp plate 21d. Slide pieces 21f (which may also be referred to as guide pieces) made of synthetic resin with excellent sliding properties are attached to groove portions 216 of ramp plate 21d, and the slide portions 215 of movable sheave 21b slidably engage with the slide pieces 21f. The slide portions 215 of movable sheave 21b are portions that protrude in the axial direction (-Y direction) from part of the outer periphery of movable sheave 21b, and may be configured, for example, in the shape of a plate having a thickness in the circumferential direction. The groove 216 of the ramp plate 21d and the slide portion 215 of the movable sheave 21b may be understood as a mechanism for guiding the relative movement in the axial direction between the movable sheave 21b and the ramp plate 21d. Here, a wall portion 219 having an outer surface that is the outermost end in the radial direction of the movable sheave 21b is provided on the outer periphery of the movable sheave 21b and extends in the axial direction (-Y direction). In this embodiment, the slide portion 215 is connected to a part of the wall portion 219 and is configured to protrude further in the axial direction (-Y direction) than the wall portion 219.

[0021] The weight roller 21e is disposed on the opposite side of the fixed sheave 21a with respect to the movable sheave 21b, and is housed in a space formed between the movable sheave 21b and the ramp plate 21d so as to be movable radially outward. The contact surface F21b of the movable sheave 21b that contacts the weight roller 21e is inclined with respect to a plane perpendicular to the axial direction (the XZ plane). Therefore, when the drive shaft AX1 rotates, the resulting centrifugal force causes the weight roller 21e to move radially outward within the movable sheave 21b, and generates a force in a direction (+Y direction) that moves the movable sheave 21b closer to the fixed sheave 21a. This causes the movable sheave 21b to be pressed toward the fixed sheave 21a. The movement of the weight roller 21e here is a concept that includes rolling and sliding, and the weight roller 21e rolls and / or slides on the contact surface F21b of the movable sheave 21b. Therefore, the contact surface F21b may be expressed as a rolling surface or a sliding surface. The contact surface F21b may also be understood as a guide surface that guides the movement of the weight roller 21e within the movable sheave 21b.

[0022] <About the driven pulley> Next, the pulley device 22 will be described with reference to Fig. 2. The pulley device 22 receives power from the drive pulley 21 via a belt 23. The pulley device 22 will be referred to as a driven pulley 22 in the following description to distinguish it from the pulley device 21.

[0023] The driven pulley 22 includes a fixed sheave 22a, a movable sheave 22b, a torque cam mechanism 22c, and a biasing unit 22d.

[0024] Like the sheaves 21a and 21b described above, the sheaves 22a and 22b have a generally conical shape and are arranged opposite each other. The fixed sheave 22a is fixed to the driven shaft AX2. The movable sheave 22b is supported by the driven shaft AX2 so as to be movable in the axial direction (the direction of the driven shaft AX2, the Y direction) relative to the fixed sheave 22a. The diameter of the belt 23 wound around and between the sheaves 22a and 22b is maintained large while the movable sheave 22b is close to the fixed sheave 22a, and becomes smaller as the movable sheave 22b moves away from the fixed sheave 22a.

[0025] The torque cam mechanism 22c has the same function as the torque cam mechanism 21c, that is, generates a force that moves the movable sheave 22b in the axial direction due to the rotation of the driven shaft AX2.

[0026] The biasing unit 22d biases the movable sheave 22b toward the fixed sheave 22a so that the movable sheave 22b approaches the fixed sheave 22a. Any known biasing means may be used for the biasing unit 22d, and a coil spring is typically used.

[0027] The rotation of the driven shaft AX2 is transmitted directly or indirectly to the rear wheels, which are the driving wheels. In other words, the driven shaft AX2 may be connected to the rotation axis of the rear wheels via another power transmission mechanism, or may substantially coincide with the rotation axis of the rear wheels.

[0028] <Gear ratio> In the configuration of the CVT 2 described above, the belt 23 is installed between the pulleys 21 and 22. For example, when the distance between the sheaves 21a and 21b of the drive pulley 21 becomes smaller (the diameter of the belt 23 wound around them becomes larger), the distance between the sheaves 22a and 22b of the driven pulley 22 becomes larger (the diameter of the belt 23 wound around them becomes smaller). Similarly, when the distance between the sheaves 21a and 21b of the drive pulley 21 becomes larger (the diameter of the belt 23 wound around them becomes smaller), the distance between the sheaves 22a and 22b of the driven pulley 22 becomes smaller (the diameter of the belt 23 wound around them becomes larger). With this configuration, the power of the power source 121 is transmitted to the rear wheel, which is the drive wheel, at a gear ratio according to the diameter of the belt 23 at the drive pulley 21 and the diameter of the belt 23 at the driven pulley 22. Because the diameter of the belt 23 is continuously variable at both the pulleys 21 and 22, the gear ratio is continuously changed and there are no gear stages (i.e., continuously variable transmission).

[0029] For example, when the vehicle 1 is stopped, the movable sheave 21b of the drive pulley 21 is spaced apart from the fixed sheave 21a (the diameter of the belt 23 of the drive pulley 21 is small), and the movable sheave 22b of the driven pulley 22 is close to the fixed sheave 22a (the diameter of the belt 23 of the driven pulley 22 is large), so the speed ratio of the CVT 2 is large. In other words, the state in which the movable sheave 21b of the drive pulley 21 is farthest from the fixed sheave 21a and the movable sheave 22b of the driven pulley 22 is closest to the fixed sheave 22a is the state in which the speed ratio is largest (low ratio (equivalent to low gear)). Thereafter, as the vehicle 1 accelerates, the movable sheave 21b of the drive pulley 21 approaches the fixed sheave 21a, and the movable sheave 22b of the driven pulley 22 moves away from the fixed sheave 22a, thereby continuously decreasing the speed ratio of the CVT 2. In other words, the state in which the movable sheave 21b of the drive pulley 21 is closest to the fixed sheave 21a, and the movable sheave 22b of the driven pulley 22 is farthest from the fixed sheave 22a, is the state in which the speed ratio is lowest (top ratio (equivalent to top gear)).

[0030] The speed change (i.e., the movement of the movable sheaves 21b and 22b) can be determined by the axial forces generated by the torque cam mechanism 21c and weight roller 21e of the drive pulley 21, and the torque cam mechanism 22c and biasing unit 22d of the driven pulley 22. For ease of understanding, the force generated by the torque cam mechanism 21c of the drive pulley 21 is defined as F1 (-Y direction), and the force generated by the weight roller 21e is defined as F2 (+Y direction). Furthermore, the force generated by the torque cam mechanism 22c of the driven pulley 22 is defined as F3 (-Y direction), and the force generated by the biasing unit 22d is defined as F4 (-Y direction). In this case: If |F1+F2|=|F3+F4|, the gear ratio is maintained; If |F1+F2|>|F3+F4|, the top ratio is approached (continuous upshifts); If |F1+F2|<|F3+F4|, the gear ratio approaches a low ratio (shifts down continuously).

[0031] Furthermore, in the configuration of the CVT2, the direction in which the force F1 of the torque cam mechanism 21c is generated is the -Y direction (the direction in which the movable sheave 21b moves away from the fixed sheave 21a). This allows for gradual upshifting when a high load is applied to the power source 121, for example, when climbing a slope, thereby enabling driving while suppressing a decrease in power performance.

[0032] <Example of movable sheave configuration> Fig. 4 is a perspective view of the drive pulley 21 with the ramp plate 21d removed. Fig. 4 also shows the slide piece 21f and the weight roller 21e, and shows the weight roller 21e moved radially outward due to centrifugal force caused by the rotation of the drive shaft AX1.

[0033] In this embodiment, a plurality of weight rollers 21e (six in FIG. 4) are arranged around the drive shaft AX1 in the space between the movable sheave 21b and the ramp plate 21d. Each weight roller 21e moves radially outward due to centrifugal force caused by the rotation of the drive shaft AX1 and applies force to the contact surface F21b of the movable sheave 21b, thereby pressing the movable sheave 21b toward the fixed sheave 21a.

[0034] However, if the weight of the outer periphery of the movable sheave 21b is large, the moment of inertia increases accordingly, which may hinder improvement in fuel efficiency. Therefore, in order to reduce the size and weight of the movable sheave 21b of the drive pulley 21 of this embodiment, recesses 219c are partially provided on the outer surface 219a of the wall portion 219. An example of the configuration of the movable sheave 21b of this embodiment will be described below with reference to FIGS. 5 and 6. FIG. 5 is a schematic diagram showing the cross-sectional structure of the drive pulley 21 taken along a cutting line (line d1-d1 in FIG. 4) passing through two weight rollers 21e. FIG. 6 is a side view of the movable sheave 21b as viewed from the side (the -X direction side).

[0035] In this embodiment, a wall portion 219 extending in the axial direction (-Y direction) is provided around the outer periphery of the movable sheave 21b. An outer surface 219a (the outer surface in the radial direction) of the wall portion 219 is the surface that is the outermost end of the movable sheave 21b in the radial direction. An inner surface 219b (the inner surface in the radial direction) of the wall portion 219 is the surface opposite the outer surface 219a, and includes a portion that is continuous with the contact surface F21b that contacts the weight roller 21e. By configuring the wall portion 219 in this manner, the movable sheave 21b can be made smaller while ensuring the rigidity of the movable sheave 21b.

[0036] Furthermore, in the movable sheave 21b configured as described above, the thickness of the portion of the wall 219 on the fixed sheave 21a side (+Y direction side) is configured to be thicker than the other portions. Therefore, in this embodiment, as shown in FIG. 5, a recess 219c recessed radially inward is provided at the end of the outer surface 219a of the wall 219 on the fixed sheave 21a side. It is preferable that a plurality of recesses 219c are provided on the outer surface 219a of the wall 219. In this case, it is preferable that the plurality of recesses 219c are arranged so as to be rotationally symmetrical about the drive shaft AX1 in order to reduce rotational wobble of the movable sheave 21b. This reduces the weight of the outer peripheral portion of the movable sheave 21b, thereby reducing the moment of inertia.

[0037] In particular, the thickness of the portion of the movable sheave 21b where the abutment surface F21b is formed is thicker than the other portions. Therefore, it is preferable that the recesses 219c are provided in a position on the outer surface 219a of the wall portion 219 that overlaps with the abutment surface F21b in the circumferential direction. In this case, the same number of recesses 219c as the number of weight rollers 21e (i.e., six) can be arranged on the outer surface 219a of the wall portion 219 in the circumferential direction. This makes it possible to reduce the weight of the outer periphery of the movable sheave 21b, thereby reducing the moment of inertia, and also ensure appropriate rigidity of the movable sheave 21b.

[0038] Here, recess 219c is intended to reduce the thickness of the portion of wall 219 on the fixed sheave 21a side (+Y direction side), and therefore may be provided in region R of 3 / 4 (preferably 2 / 3) of outer surface 219a of wall 219 on the fixed sheave 21a side, as shown in Fig. 6. By providing recess 219c on outer surface 219a in this way, the thickness of wall 219 on the -Y direction side can be ensured, which can be advantageous in terms of the rigidity of movable sheave 21b.

[0039] Furthermore, recess 219c is preferably configured as a portion where a worker performing maintenance on drive pulley 21 grips movable sheave 21b. Specifically, recess 219c is preferably configured with a width and / or depth that allows a worker to hook their fingers into recess 219c and grip movable sheave 21b, thereby improving ease of maintenance.

[0040] As described above, in the drive pulley 21 of this embodiment, the outer surface 219a of the wall portion 219, which is the radially outermost end of the movable sheave 21b, has a recess 219c recessed radially inward at the end on the fixed sheave 21a side. This makes it possible to reduce the weight of the outer periphery of the movable sheave 21b and reduce the moment of inertia while ensuring the rigidity of the movable sheave 21b. As a result, it is also possible to achieve improved fuel efficiency.

[0041] In the above description, for ease of understanding, each element is denoted by a name related to its function. However, each element is not limited to having the content described in the embodiment as its main function, and may have that function auxiliary to the content. Therefore, each element is not strictly limited to the expression, and the expression can be replaced with a similar expression. In the same spirit, the expression "apparatus" may be replaced with "unit," "component," "piece," "member," "structure," "assembly," etc., or may be omitted or added.

[0042] Furthermore, two or more selectable elements exemplified in the embodiments are not strictly limited to the examples and may be arbitrarily combined, for example, each of the two or more selectable elements may be additionally or alternatively selected. For example, when two elements A and B are arbitrarily combined, they may be expressed as "A and / or B" or "at least one of A and B" to indicate either A only, B only, or both A and B.

[0043] Summary of the embodiment (Item 1) A pulley device (e.g., 21) provided on an output rotation shaft (e.g., AX1) of a power source (e.g., 121), a fixed sheave (e.g., 21a) fixed to the output rotary shaft; a movable sheave (e.g., 21b) that is movable in the axial direction of the output rotation shaft relative to the fixed sheave; Equipped with A wall portion (e.g., 219) having an outer surface (e.g., 219a) that is the outermost end of the movable sheave in the radial direction is provided on the outer periphery of the movable sheave and extends in the axial direction, The pulley device, wherein the wall portion partially has a recess (for example, 219c) recessed radially inward at an end of the outer surface on the fixed sheave side. According to this item, the weight of the outer periphery of the movable sheave can be reduced, thereby reducing the moment of inertia, while ensuring the rigidity of the movable sheave.

[0044] (Item 2) 2. The pulley device according to item 1, wherein the recess is provided in a 3 / 4 region of the outer surface on the fixed sheave side. According to this item, the thickness of the wall portion can be ensured, which is further advantageous in terms of the rigidity of the movable sheave.

[0045] (Item 3) a weight roller (e.g., 21e) that moves radially outward within the movable sheave by centrifugal force caused by rotation of the output rotary shaft and presses the movable sheave toward the fixed sheave; The movable sheave has a contact surface (e.g., F21b) that contacts the weight roller that moves radially outward, 3. The pulley device according to item 1 or 2, wherein the recess is provided on the outer surface at a position that overlaps with the contact surface in the circumferential direction. According to this item, the weight of the outer periphery of the movable sheave can be reduced to reduce the moment of inertia, and the rigidity of the movable sheave can also be appropriately ensured.

[0046] (Item 4) The wall portion has an inner surface (e.g., 219b) opposite the outer surface, 4. The pulley device according to item 3, wherein a portion of the inner surface is configured as a surface that is continuous with the contact surface. According to this item, the movable sheave can be made smaller.

[0047] (Item 5) 5. The pulley device according to any one of items 1 to 4, wherein a plurality of the recesses are provided on the outer surface so as to be rotationally symmetrical about the output rotation shaft. According to this item, the weight of the outer periphery of the movable sheave can be reduced to reduce the moment of inertia, and the rotational wobble of the movable sheave can also be appropriately reduced.

[0048] (Item 6) 6. The pulley device according to any one of items 1 to 5, wherein the recess has a width and / or depth that allows an operator to hook their fingers into the recess and grip the movable sheave. According to this item, the maintainability of the pulley device can be improved.

[0049] (Item 7) A drive pulley (e.g., 21) that is the pulley device according to any one of items 1 to 6; a driven pulley (e.g., 22); a belt (e.g., 23) stretched between the driving pulley and the driven pulley; A continuously variable transmission (e.g., 2) characterized by comprising: According to this item, it is possible to provide a continuously variable transmission equipped with a pulley device capable of reducing the moment of inertia.

[0050] (Item 8) A vehicle (for example, 1) comprising the continuously variable transmission according to item 7 and a wheel (for example, 11). According to this item, it is possible to provide a vehicle to which a continuously variable transmission equipped with a pulley device capable of reducing the moment of inertia is applied.

[0051] The invention is not limited to the above-described embodiment, and various modifications and variations are possible within the scope of the gist of the invention. [Explanation of symbols]

[0052] 21: drive pulley (pulley device), 21a: fixed sheave, 21b: movable sheave, 21c: torque cam mechanism, 21e: weight roller, F21b: contact surface, 219: wall portion, 219a: outer surface, 219b: inner surface, 219c: recessed portion

Claims

1. A pulley device provided on an output rotation shaft of a power source, a fixed sheave fixed to the output rotary shaft; a movable sheave that is movable in the axial direction of the output rotary shaft relative to the fixed sheave; a plurality of weight rollers that move radially outward within the movable sheave by centrifugal force caused by rotation of the output rotary shaft, thereby pressing the movable sheave toward the fixed sheave; Equipped with the movable sheave has a contact surface that contacts each weight roller that moves radially outward, a wall portion having an outer surface that is the outermost end of the movable sheave in the radial direction is provided on an outer peripheral portion of the movable sheave and extends in the axial direction; a surface continuous with the abutment surface, the thickness of the portion of the wall portion on the fixed sheave side being thicker than the other portion; The wall portion has a recess partially recessed radially inward at an end portion of the outer surface on the fixed sheave side, The pulley device is characterized in that the recesses are arranged on the outer surface at positions that overlap the contact surface in the circumferential direction, and the number of the recesses is the same as the number of weight rollers.

2. 2. The pulley device according to claim 1, wherein the recess is provided in a three-quarters area of ​​the outer surface on the fixed sheave side.

3. A pulley device as described in claim 1, characterized in that the recess is provided on the opposite side of the movable sheave from the abutment surface.

4. The wall portion has an inner surface opposite the outer surface, The pulley device according to claim 1, wherein a portion of the inner surface is configured as a surface that is continuous with the contact surface.

5. a plurality of the abutment surfaces are provided on the outer surface of the movable sheave so as to be rotationally symmetrical about the output rotation shaft, The pulley device according to claim 1 , wherein the recessed portion is provided on the outer surface at a position overlapping each of the plurality of contact surfaces in the circumferential direction.

6. A pulley device as described in claim 1, characterized in that the recess is configured to have the same width as each weight roller in the circumferential direction.

7. The torque cam mechanism is provided around the output rotating shaft between the output rotating shaft and the movable sheave, and is capable of generating a force that moves the movable sheave in the axial direction; 2. The pulley device according to claim 1, wherein the contact surface is provided around the periphery of the torque cam mechanism.

8. Further comprising a ramp plate arranged on the opposite side of the fixed sheave with respect to the movable sheave, the movable sheave has a slide portion slidably engaged with a groove portion of the ramp plate, The pulley device according to claim 1 , wherein the slide portion is connected to a part of the wall portion and protrudes beyond the wall portion in the axial direction.

9. A drive pulley that is the pulley device according to any one of claims 1 to 8; A driven pulley; a belt stretched between the drive pulley and the driven pulley; A continuously variable transmission comprising:

10. A vehicle comprising the continuously variable transmission according to claim 9 and a wheel.

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