WO2018194003A1

WO2018194003A1 - Continuously variable transmission

Info

Publication number: WO2018194003A1
Application number: PCT/JP2018/015635
Authority: WO
Inventors: 平岩　一美
Original assignee: 株式会社Ｆｉｎｅｍｅｃｈ
Priority date: 2017-04-21
Filing date: 2018-04-16
Publication date: 2018-10-25
Also published as: JPWO2018194003A1

Abstract

The purpose of the present invention is to compact a double roller toroidal type continuously variable transmission, including a control member. The continuously variable transmission according to the present invention includes a plurality of trunnions 36 which is disposed between an input disk 20 and an output disk 22 and each of which rotatably supports a first roller 24 and a second roller 26. The first roller 24 of each trunnion 36 forms a first friction surface 24a which is in contact, at a point A, with a first toroidal surface 20a formed on the input disk 20, and the first roller 24 and the second roller 26 of each trunnion 36 form second friction surfaces 24b which are in contact with each other at a point B. The second roller 26 of each trunnion 36 forms a first friction surface 26a which is in contact, at a point C, with the second toroidal surface 22a formed on the output disk 22. The points A, B and C are arranged substantially on a straight line. Each trunnion 36 is tiltably supported by a stator 40 provided integrally with a fixed shaft 1, such that the point A and the point C change radially about the point B, and each trunnion 36 can be tilted by rotating a control shaft 12 provided within the outer diameter of the input disk 20 and the output disk 22.

Description

Continuously variable transmission

The present invention relates to a toroidal type continuously variable transmission (CVT), and more particularly to a continuously variable transmission using a double roller traction drive.

As this type of continuously variable transmission, two rollers that contact the toroidal curved surfaces of the input disk and output disk that face each other are rotatably supported by a trunnion to form one set. There is known a continuously variable transmission configured to transmit a power between an input disk and an output disk by using a plurality of gears and to obtain a stepless speed ratio by tilting a trunnion (for example, Patent Document 1). .

In order to make such a continuously variable transmission more compact, one of the two rollers contacting the toroidal curved surfaces of the input disk and the output disk that are arranged to face each other is obtained from the other roller. There has been proposed a continuously variable transmission configured such that the rotational shafts of these rollers are supported by force and the rollers are moved to a stationary position in a plane including two points in contact with the disk (for example, Patent Document 2).

U.S. Pat. No. 2,595,367 U.S. Pat. No. 8,827,864

However, since the conventional toroidal type continuously variable transmissions described in

Patent Documents

1 and 2 have control members arranged on the radially outer sides of the input disk and the output disk, the dimensions of the entire continuously variable transmission For example, it has been difficult to apply to a bicycle transmission.

That is, in the conventional toroidal type continuously variable transmission, the control member for changing the transmission ratio is arranged on the outer side in the radial direction of the input disk and the output disk. However, it has a problem that it is limited.

Accordingly, an object of the present invention is to provide a continuously variable transmission in which a control member is disposed within the outer diameter of an input disk and an output disk, the manufacturing cost is low, and the applicability to a vehicle such as a bicycle is improved. There is.

A continuously variable transmission according to the present invention is disposed between an input disk connected to an input shaft, an output disk connected to an output shaft, and an input disk and an output disk, each including a first roller and a second roller. In addition, a plurality of trunnions that rotatably support the first roller and the second roller are provided. The first roller of each trunnion forms a first friction surface that contacts the first toroidal surface formed on the input disk at point A, and the first roller and the second roller of each trunnion contact each other at point B. Two friction surfaces are formed, and the second roller of each trunnion forms a first friction surface that abuts at a point C on a second toroidal surface formed on the output disk. These points A, B and C The points are arranged so as to be aligned substantially in a straight line. A fixed shaft coaxial with the input disk and the output disk is disposed at the center. Each trunnion is supported in a tiltable manner by a stator provided integrally with the fixed shaft, and the control shaft provided within the outer diameter of the input disk and the output disk is rotated coaxially with the fixed shaft, so that point A In addition, the trunnion is tilted by changing the point C and the point B in the radial direction around the point B.

It is preferable that each trunnion is configured to be tiltable by rotating the control shaft and to be twisted about the B point.

The guide sleeve further includes a guide sleeve provided radially inward of each trunnion. The guide sleeve has a guide groove or a guide protrusion on an outer peripheral surface, and the protrusions or holes provided radially inward of the plurality of trunnions. However, it is also preferable to be configured to engage with the guide groove or the guide protrusion.

It is also preferable that the guide groove of the guide sleeve is a helical groove, the guide sleeve is fixed to a fixed shaft so as not to move in the axial direction, and is configured to rotate with the control shaft in the circumferential direction.

The guide sleeve and the control shaft are connected to each other via a helical spline, and the control shaft or an intermediate portion provided between the control shaft and the guide sleeve by the thrust generated in the helical spline by the torque that drives the guide sleeve. It is also preferable that the member is configured to move in the axial direction to twist each trunnion.

Protrusions are provided at positions away from point B in both the radial direction and circumferential direction in each trunnion, and a shifter connected to the control shaft by a helical spline is provided outside the control shaft in the radial direction. It is also preferable that each trunnion is tilted and / or twisted by pressing the protrusion in the axial direction when the shifter moves in the axial direction by rotation.

It is also preferable that a thrust sleeve is provided radially outside the input disk and the output disk, and the thrust sleeve is configured to receive an axial load acting between the input disk and the output disk.

It is also preferable that a hub shell constituting the output shaft is provided, and the hub shell and a cover integrated with the hub shell are arranged so as to surround the input disk and the output disk.

In the continuously variable transmission of the present invention, a control shaft is provided within the outer diameter of the input disk and the output disk, and the trunnion can be tilted by rotating the control shaft.

Therefore, since the continuously variable transmission of the present invention can constitute a compact continuously variable transmission centering on a fixed shaft, it can be applied to a bicycle or the like at a low cost.

FIG. 3 is a cross-sectional view showing a main part of the continuously variable transmission according to the first embodiment of the present invention, and is a cross-sectional view taken along the line EE of FIG. It is the external view which looked at the principal part of the continuously variable transmission which concerns on embodiment of FIG. 1 from the right direction. It is sectional drawing which shows the other operating state of a part of continuously variable transmission which concerns on embodiment of FIG. It is operation | movement explanatory drawing of the continuously variable transmission which concerns on embodiment of FIG. It is sectional drawing which showed the principal part of the continuously variable transmission which concerns on the 2nd Embodiment of this invention. FIG. 10 is a cross-sectional view showing a main part of a continuously variable transmission according to a third embodiment of the present invention, and is a cross-sectional view taken along the line FF of FIG. FIG. 7 is a cross-sectional view of a main part of the continuously variable transmission according to the embodiment of FIG. 6, and is a cross-sectional view along the line GG of FIG. 6. It is sectional drawing which showed the principal part of the continuously variable transmission which concerns on the 4th Embodiment of this invention. It is sectional drawing which showed the principal part of the continuously variable transmission which concerns on the 5th Embodiment of this invention. It is a skeleton figure of the continuously variable transmission which concerns on the 6th Embodiment of this invention.

Hereinafter, the continuously variable transmission according to each embodiment of the present invention will be described with reference to the drawings. In the following description, the expressions “axial direction”, “radial direction”, and “circumferential direction” are the axial direction of the hub shaft, the radial direction of the hub shaft, and the hub shaft unless otherwise specified. Each circumferential direction is shown.

(First embodiment)
FIG. 1 shows a main part of the continuously variable transmission according to the first embodiment of the present invention in a section taken along line EE of FIG. FIG. 2 shows an external view of the main part of the continuously variable transmission of FIG. 1 as viewed from the right. However, FIG. 2 is shown with the input disk 20, the control shaft 12, the guide sleeve 38, the intermediate member 44, and the like to be described later removed. FIG. 3 shows a cross section of a part of the continuously variable transmission of FIG. 1, in which the upper side from the center of the shaft is depicted with the gear ratio changed. FIG. 4 illustrates the operation when changing the gear ratio described later. The first embodiment relates to a small toroidal type automatic transmission provided in a hub shell portion of a driving wheel of a bicycle.

In FIG. 1, a hub shaft 1 constitutes a fixed shaft of the present invention, and both ends thereof are fixed to a frame 2 such as a bicycle. The continuously variable transmission of the present invention is configured around the hub shaft 1. The input shaft 10 is supported by a bearing 10a via a control shaft 12 with respect to the hub shaft 1, and is configured integrally with a sprocket 10b driven by a chain (not shown). The details of the control shaft 12 rotatably supported by the hub shaft 1 will be described later.

The hub shell 14 constitutes an output shaft of the present invention, is integrally formed with the cover 16, is rotatably supported by the hub shaft 1 by a bearing 14a, and is also supported by the input shaft 10 on the bearing 16a. It is supported rotatably by. In addition, flanges 14 d having a plurality of holes 14 c that engage with the spokes 3 are formed on both sides in the axial direction on the outer periphery of the hub shell 14. In addition, the spoke 3 is drawn only in one place of the engaging part in FIG. Although not shown, the spoke 3 constitutes a part of a bicycle wheel (drive wheel). Although description with reference numerals is omitted, an oil seal or the like is provided between the hub shaft 1, the input shaft 10, the control shaft 12, the hub shell 14, and the cover 16 as necessary. The oil-tight member is provided so that hydraulic oil, which will be described later, leaks from the inside of the continuously variable transmission to the outside, and conversely, foreign matter enters from the outside to the inside.

Inside the hub shell 14, a first roller 24 and a second roller 26 are provided between an input disk 20 connected to the input shaft 10 and an output disk 22 disposed opposite to the hub disk 14 and connected to the hub shell 14. It has been. The first roller 24 and the second roller 26 are configured to contact the input disk 20 and the output disk 22, respectively. As shown in FIG. 1, the input disk 20 is connected to the input shaft 10 with a loading mechanism 28 interposed therebetween. The loading mechanism 28 is configured to generate a thrust according to the transmission torque from the input shaft 10 to the input disk 20, and by this thrust, the input disk 20 moves leftward in FIG. 1, that is, the first roller 24. It is pressed in the direction of Further, a spring 30 is provided between the input disk 20 and the input shaft 10, and the input disk 20 is always pressed with a constant thrust in the left direction in FIG. 1.

A first toroidal surface 20 a is formed on the left side surface of the input disk 20 in FIG. 1, and the first toroidal surface 20 a is in contact with the first roller 24. An output disk 22 disposed opposite to the input disk 20 is connected to the hub shell 14 via a one-way clutch 32. The one-way clutch 32 is a so-called free wheel used for a general bicycle. This freewheel transmits drive torque in the direction of advancing the bicycle from the output disk 22 to the hub shell 14, but the reverse is free.

A second toroidal surface 22 a facing the input disc 20 is formed on the right side surface of the output disc 22 in FIG. 1, and the second toroidal surface 22 a is in contact with the second roller 26. The 1st toroidal surface 20a and the 2nd toroidal surface 22a have the cross-sectional shape comprised by the circular arc centering on the B point mentioned later.

The first roller 24 and the second roller 26 have the same shape, and when the hub shaft 1 side is the radially inner side and the opposite side is the radially outer side, the first roller 24 and the second roller 26 The radially inner side constitutes first friction surfaces 24a and 26a having cross-sectional shapes along the arcs of the first toroidal surface 20a and the second toroidal surface 22a, respectively. The radially outer sides of the first roller 24 and the second roller 26 constitute conical second friction surfaces 24b and 26b, respectively, so that the first roller 24 and the second roller 26 are in contact with each other to transmit power. .

Here, the center of contact between the first toroidal surface 20a of the input disk 20 and the first friction surface 24a of the first roller 24 is point A, and the second friction surface 24b of the first roller 24 and the second of the second roller 26 are second. The center of the contact point with the friction surface 26b is defined as point B, and the center of the contact point between the second toroidal surface 22a of the output disk 22 and the first friction surface 26a of the second roller 26 is defined as point C. As shown by the straight line L in FIG. 1, the three points A, B, and C are aligned on a straight line. As will be described later, when the gear ratio is changed, the radial positions of the points A and C change, but the position of the point B is unchanged, and the fact that these three points are aligned is basically unchanged. .

The input disk 20 and the output disk 22 are connected by a thrust sleeve 34. That is, the thrust sleeve 34 is configured to receive the thrust of the input shaft 10 via the bearing 34a on the right side in FIG. 1 and to transmit the thrust to the output disk 22 by the left snap ring 34b in FIG. . For this reason, the thrust corresponding to the transmission torque generated by the loading mechanism 28 is transmitted to the output disk 22 via the first roller 24 and the second roller 26 on the one hand and to the output disk 22 via the thrust sleeve 34 on the other hand. Acting on 22 cancels each other out. The thrust according to the transmission torque basically does not act other than these. Although the bearing 15 is disposed between the output disk 22 and the hub shell 14, the thrust described above does not act on the bearing 15.

The trunnion 36 that rotatably supports the first roller 24 and the second roller 26 is configured such that the second friction surface 24b of the first roller 24 and the second friction surface 26b of the second roller 26 are in contact with each other. The roller 24 and the second roller 26 are supported. The trunnion 36 has a protrusion 36a on the radially inner side, and this protrusion 36a is engaged with a helical groove 38a of a guide sleeve 38 to be described later.

As shown in FIG. 2, the trunnion 36 has a first pin 36b and a second pin 36c extending in the left and right directions in the circumferential direction, and the center lines of the first pin 36b and the second pin 36c are also shown in FIG. It passes the point B shown. The circumferential tip 36d of the first pin 36b and the circumferential tip 36e of the second pin 36c are configured to be a part of a spherical surface centered at point B, and abut against a stator 40 described later. Yes. 2, three sets of the trunnion 36, the first roller 24, and the second roller 26 (FIG. 1) are arranged at equal intervals in the circumferential direction.

1 and 2 are fixed to the hub shaft 1 by a snap ring 40c. The stator 40 supports the first pin 36b and the second pin 36c so that the trunnion 36 can be tilted and twisted as will be described later. That is, a total of six grooves 40a with which the tip portions of the first pin 36b and the second pin 36c are engaged are formed, and the tip 40d and the second pin in the circumferential direction of the first pin 36b are formed in these grooves 40a. A bottom surface 40b is formed on which the circumferential tip 36e of 36c abuts. The stator 40 has three support pins 40d for supporting a control lever 42, which will be described later, and a check groove 40e for positioning the control lever 42.

Here, the straight line L connecting the three points A, B, and C described above “tilts” the posture change of the trunnion 36 when the radial positions of the points A and C change around the point B. It is defined as FIG. 3 shows a state in which the posture of the trunnion 36 is tilted most with respect to the state of FIG. FIG. 4 schematically shows the first roller 24 and the second roller 26 sandwiched between the first toroidal surface 20a and the second toroidal surface 22a as viewed from the outer side in the circumferential direction. In FIG. 4, the solid line shows a state where a straight line L connecting the points A and C is parallel to the center line of the input shaft 10, and the broken line is a slight amount of the straight line L counterclockwise around the B point. Shows the rotated state. Although the trunnion 36 is not shown in FIG. 4, the posture change of the trunnion 36 that moves with the rotation of the straight line L is defined as “twist”. These tilting and twisting may be performed at the same time or independently, but in either case, the first pin 36b and the second pin 36c supported by the stator 40 are formed in the groove 40a with B Rotate around a point.

The control shaft 12 and the guide sleeve 38 provided outside the hub shaft 1 can rotate in the circumferential direction, but cannot move because they are integrated with the hub shaft 1 in the axial direction. That is, the stator 40, the control shaft 12, and the guide sleeve 38 are arranged in the axial direction so as to sandwich the flange portion 1a formed on the hub shaft 1, and these shafts are disposed by the

washers

12a and 38b and the snap rings 12b, 38c, and 40c. Directional movement is restricted.

Three helical grooves 38a are formed on the outer circumferential surface of the guide sleeve 38, and the projections 36a of the trunnion 36 are engaged with the helical grooves 38a as described above. Therefore, the tilt of the trunnion 36 and the rotation of the guide sleeve 38 are basically linked. Note that the shapes of both the helical groove 38a and the protrusion 36a are appropriately formed so that they are in surface contact as much as possible.

Three notches 38d are formed at both ends of the outer circumferential surface of the guide sleeve 38, and these notches 38d are configured to serve as stoppers when the trunnion 36 is tilted to the maximum extent. ing. In FIGS. 1 and 3, the trunnion 36 and the guide sleeve 38 are shown in a slightly separated state. However, as the tilting further proceeds, the trunnion 36 comes into contact with the guide sleeve 38. The guide sleeve 38 also has a function of always aligning the tilt angles of the three trunnions 36.

A control arm 12c is provided integrally with the control shaft 12 at the right end in FIG. 1 of the control shaft 12, and the control shaft 12 can be rotated by manual operation of a cyclist or operation of an actuator (not shown). It is configured as follows. The control arm 12c may be a pulley or a gear. An intermediate member 44 is interposed between the control shaft 12 and the guide sleeve 38 to transmit the rotation of the control shaft 12 to the guide sleeve 38. That is,

helical splines

12d and 44a and

helical splines

44b and 38e are formed between the control shaft 12 and the intermediate member 44, and between the intermediate member 44 and the guide sleeve 38, respectively. One or both of the

helical splines

12d and 44a and the

helical splines

44b and 38e function as a helical spline. For this reason, in the process in which the rotation operation of the control shaft 12 is transmitted to the guide sleeve 38, the thrust (thrust) generated by these helical splines acts to move the intermediate member 44 in the axial direction.

A groove 44c is formed in the intermediate member 44, and the end portion 42a of the control lever 42 described above is engaged with the groove 44c. As shown in FIG. 2, three control levers 42 are arranged, and when these end portions 42a move along with the movement of the intermediate member 44, the control lever 42 slightly swings around the support pin 40d. . On the other hand, a ball 42 c provided in a hole 42 b formed in the control lever 42 is pressed by a spring 42 d and locked in a check groove 40 e of the stator 40. Therefore, when the control lever 42 swings, the ball 42c moves slightly against the tension of the spring 42d.

The control lever 42 is formed with a first cam 42e and a second cam 42f on both sides in the circumferential direction, respectively. The first cam 42e and the second cam 42f are described above by the swinging of the control lever 42. It acts to press one of the first pin 36b and the second pin 36c of the trunnion 36 and to release the other from the pressing. That is, the first cam 42e and the second cam 42f have shapes opposite to each other in the circumferential direction, and are configured to perform actions opposite to each other when the control lever 42 swings. In FIG. 2, when viewed from the center of one trunnion 36, the first pin 36b is configured such that the first cam 42e of the control lever 42 adjacent to the left in the circumferential direction in the drawing is in contact with the second pin 36c. In the figure, the second cam 42f of the control lever 42 adjacent to the right in the circumferential direction is configured to abut. Since the control levers 42 adjacent to each other in the circumferential direction swing in the same direction, the trunnion 36 is twisted between the first pin 36b and the second pin 36c of one trunnion 36 by the first cam 42e or the second cam 42f. Pressed or released from the press. The direction of the torsion is determined depending on whether the axial movement of the intermediate member 44 is the right side or the left side in FIG.

Next, the operation of the continuously variable transmission according to the first embodiment shown in FIGS. 1 and 2 will be described with reference to FIGS. Although not shown, the continuously variable transmission shown in FIG. 1 can include various sensors, a controller, and the like, and the following operations may be automatically performed based on instructions from the controller. The continuously variable transmission according to the first embodiment uses appropriate hydraulic oil that also serves as a lubricant. The rotation direction in the following description indicates a case when viewed from the right side in FIG. 1, that is, when viewed from the input shaft 10 side.

When the input shaft 10 is driven forward by the cyclist pedaling via the sprocket 10b (clockwise), the input disk 20 rotates the first roller 24 clockwise. As a result, the input disk 20 obtains the thrust corresponding to the driving torque of the input shaft 10 together with the urging force of the spring 30 from the loading mechanism 28, so that the first toroidal surface 20 a changes the first friction surface 24 a of the first roller 24. In FIG. 1, the first roller 24 is rotated while being pressed in the left direction. The first roller 24 transmits the thrust received from the input disk 20 from the second friction surface 24b to the second friction surface 26b of the second roller 26, thereby rotating the second roller 26 counterclockwise. The second roller 26 transmits the thrust received from the first roller 24 from the first friction surface 26a to the second toroidal surface 22a of the output disk 22, thereby rotating the output disk 22 clockwise. The output disk 22 drives the hub shell 14, which is also an output shaft, via the one-way clutch 32 to rotate clockwise (forward direction).

The gear ratio at this time (the rotational speed of the input disk 20 / the rotational speed of the output disk 22) is Rc / Ra, where Ra is the radius of point A and Rc is the radius of point C. The state shown in FIG. 1 is the value with the smallest speed ratio, that is, the acceleration state. However, when the trunnion 36 is tilted as shown in FIG. 3, the value with the largest speed ratio, that is, the deceleration state is obtained. It becomes.

Next, the operation when the gear ratio is changed by tilting the trunnion 36 will be described with reference to FIG. To tilt the trunnion 36, the control shaft 12 is rotated by operating the control arm 12c. The rotation of the control shaft 12 causes the guide sleeve 38 to rotate via the intermediate member 44, thereby driving the protrusion 36 a engaged with the helical groove 38 a of the guide sleeve 38, and the trunnion 36 is connected to the first pin 36 b and It tilts around the central axis of the second pin 36c, that is, around the point B. At this time, when the driving torque of the input shaft 10 is small, the trunnion 36 can be easily tilted. However, when the driving torque of the input shaft 10 is large, the point A of the first roller 24 and the C of the second roller 26 Since the pressing force acting on the point increases, a large force is required to tilt the trunnion 36.

As described above, in the process of transmitting the rotation of the control shaft 12 to the guide sleeve 38, a force for moving the intermediate member 44 in the axial direction is generated, and the control lever 42 is swung to move one of the first cam 42e and the second cam 42f. Presses one of the first pin 36b and the second pin 36c (corresponding to the protrusion of the present invention) of the trunnion 36 in the axial direction. The trunnion 36 is twisted by this pressing force.

As in the case of the first roller 24 and the second roller 26 shown by the solid lines in FIG. 4, the straight line L connecting the points A, B, and C is parallel to the center line of the input shaft 10 as described above. The ball 42c pushed by 42d is in a state of being locked in the check groove 40e. Thus, in a state where the straight line L is parallel to the center line of the input shaft 10, the moment that tilts the trunnion 36 with the torque transmission from the input disk 20 to the output disk 22 does not act. However, as shown by the broken line, when the trunnion 36 is twisted against the tension of the spring 42d and the straight line L is inclined, the contact point between the input disk 20 and the first roller 24, and the output disk 22 and the second roller. At the contact point 26, moments for tilting the trunnion 36 act, that is, the trunnion 36 tilts due to the transmission torque from the input disk 20 to the output disk 22.

Although a detailed description is omitted, since the direction of tilting of the trunnion 36 is determined by the direction of twisting of the trunnion 36, the twisting direction of the helical groove 38a of the guide sleeve 38 and the first cam 42e and the second cam 42f of the control lever 42 are determined. The gear ratio is changed in the direction aimed by the rotation operation of the control shaft 12, and when the target gear ratio is reached, twisting is stopped and the change in the gear ratio is stopped. That is, the rotation angle of the control shaft 12 and the gear ratio can be controlled in correspondence. Although the detailed description is also omitted here, a moment that twists the trunnion 36 acts by the torque transmitted from the input disk 20 to the output disk 22, so that the groove of the check groove 40e is also taken into account. It is desirable to set the angle and the tension of the spring 42d appropriately, and to apply a slight operating force to the control shaft 12 at all times.

As described above, according to the continuously variable transmission according to the first embodiment, the control member such as the control shaft 12 can be disposed within the outer diameter range of the input disk and the output disk. It can be applied to a step transmission. Furthermore, the continuously variable transmission according to the first embodiment has a simple structure as a whole, and can reduce the manufacturing cost as well as the weight and size.

Also, the bearing 34a on which thrust for power transmission acts has the basic advantage that the power transmission efficiency is high with little loss due to rotation because the input shaft 10 and the output disk 22 are in the same rotational direction. And according to 1st Embodiment, while being able to change a gear ratio steplessly according to the will of a cyclist, control of a gear ratio and detection of a gear ratio can be performed only by rotation of the control shaft 12. Therefore, it has desirable characteristics as a continuously variable transmission for bicycles.

(Second Embodiment)
FIG. 5 shows a cross section corresponding to FIG. 1 of a continuously variable transmission according to the second embodiment of the present invention. Here, the description will focus on the parts that are different from the configuration of the continuously variable transmission according to the first embodiment, and the components that are substantially the same as the configuration of the continuously variable transmission according to the first embodiment are denoted by the same reference numerals. A description thereof will be omitted.

The difference between the second embodiment and the first embodiment is that in the second embodiment, the control shaft 12 and the intermediate member 44 in the continuously variable transmission of the first embodiment are integrally configured. It is that. That is, the control shaft 12 is formed with a groove 12e for engaging the control lever 42. The control shaft 12 and the guide sleeve 38 are connected by the

helical splines

12d and 38e, and the control shaft 12 itself is axially connected. It is configured to be slightly movable left and right. Other configurations are the same as those in the first embodiment.

The operation and effect of the continuously variable transmission according to the second embodiment are basically the same as those of the first embodiment. However, as described above, when the speed ratio is changed, only the control shaft 12 itself moves slightly in the axial direction. In the second embodiment, in addition to the above-described effects of the first embodiment, an effect that the structure is simpler than that of the first embodiment can be obtained.

(Third embodiment)
FIG. 6 shows a main part of a continuously variable transmission according to the third embodiment of the present invention in a section taken along line FF in FIG. FIG. 7 shows a main part of the continuously variable transmission of FIG. 6 in a section taken along the line GG of FIG. Here, the description will focus on the parts that are different from the configuration of the continuously variable transmission according to the first embodiment, and the components that are substantially the same as the configuration of the continuously variable transmission according to the first embodiment are denoted by the same reference numerals. A description thereof will be omitted.

The first difference between the third embodiment and the first embodiment is that the configuration between the control shaft 12 and the guide sleeve 38 is different. The second difference is that there are four sets of trunnions 36 including the first roller 24 and the second roller 26. In FIG. 6, the trunnion 36 is represented in a tilted state where the straight line L is parallel to the input shaft 10, but the configuration of the other parts is represented in the same manner as in FIG. 1.

First, the relationship between the trunnion 36 and the guide sleeve 38 of the continuously variable transmission according to the third embodiment will be described. The third embodiment differs from the continuously variable transmission according to the first embodiment in that a hole 36g is formed in the trunnion 36 instead of the projection 36a in the first embodiment, and the hole 36g The guide protrusion 38f of the guide sleeve 38 is engaged. The guide sleeve 38 is configured to be freely movable in the axial direction. Therefore, the function of the guide sleeve 38 is to keep the tilt angles of the four trunnions 36 the same.

Next, the relationship between the control shaft 12 and the intermediate member 44 will be described. The control shaft 12 is provided between the hub shaft 1 and the input shaft 10 and is configured to be capable of only rotating operation without moving in the axial direction. The control shaft 12 and the intermediate member 44 (corresponding to the shifter of the present invention) are connected to each other by

helical splines

12d and 44a, and the intermediate member 44 can be moved in the axial direction when the control shaft 12 rotates. It is configured. An operation arm 44d is formed on the radially outer side of the intermediate member 44, and a tip end portion 44e is formed on the radially outer side of the operation arm 44d. As shown in FIG. 7, four tip portions 44e of the operation arm 44d are formed along the circumferential direction. The tip portions 44e engage with the guide grooves 40f of the stator 40, and the intermediate member 44 does not rotate. It is configured as follows. In FIG. 7, all of the tip portions 44e of the four operation arms 44d are engaged with the guide groove 40f, but may be engaged at only one place.

An operation groove 44g is formed in the operation arm 44d, and the operation groove 44g is engaged with an arm 36h (corresponding to the protrusion of the present invention) of the trunnion 36. The contact point between the operation groove 44g and the arm 36h is offset from the point B in both the radial direction and the circumferential direction. Therefore, when the intermediate member 44 moves in the axial direction, both the tilting and twisting forces act on the trunnion 36.

A recess 36f is formed in the tip surface of the second pin 36c of the trunnion 36, and the recess 36f is provided in a hole 40g formed in the bottom surface 40b of the groove 40a of the stator 40 and is pressed by a spring 40h. The ball 40i is engaged. The functions of the recess 36f and the ball 40i are the same as the functions of the check groove 40e and the ball 42c in the continuously variable transmission according to the first embodiment. Other configurations of the continuously variable transmission of the third embodiment are the same as those of the first embodiment.

Next, the operation of the continuously variable transmission according to the third embodiment will be described. As described above, the difference between the third embodiment and the first embodiment is that the control system is different except that there are four sets of trunnions 36 including the first roller 24 and the second roller 26. Hereinafter, only the differences between the control systems will be described.

As described above, when the control shaft 12 rotates, the intermediate member 44 moves in the axial direction and presses the arm 36h of the trunnion 36 in the axial direction, so that the trunnion 36 is tilted and twisted. Since the tilt angles of the four trunnions 36 are aligned by the operation of the guide sleeve 38, the four trunnions 36 inevitably operate with the same twist angle. Therefore, although the configuration is different, the point that the trunnion 36 performs both tilting and twisting operations by the rotation of the control shaft 12 is the same as in the case of the first embodiment. Since other operations in the third embodiment are basically the same as those in the first embodiment, description thereof will be omitted.

The effect of the continuously variable transmission according to the third embodiment is basically the same as that of the first embodiment. However, as described above, since the number of sets of the first roller 24 and the second roller 26 is as many as four, if the transmission torque is the same, the size can be reduced as compared with the case of the first embodiment.

(Fourth embodiment)
FIG. 8 shows a cross section corresponding to FIG. 1 of a continuously variable transmission according to a fourth embodiment of the present invention. Here, parts different from the configuration of the continuously variable transmission according to the first embodiment and the third embodiment will be mainly described, and the substantially same parts as those of the continuously variable transmission are denoted by the same reference numerals. The description is omitted.

The difference between the fourth embodiment and the first and third embodiments is that the configuration between the control shaft 12 and the trunnion 36 is different. That is, in the fourth embodiment, there are three sets of trunnions 36 including the first roller 24 and the second roller 26. In FIG. 8, the straight line L is represented by the tilted state of the trunnion 36 parallel to the input shaft 10, but the configuration of the other parts is represented in the same manner as in FIG. 1.

In the continuously variable transmission according to the fourth embodiment, a gear 12f is coaxially formed on the control shaft 12, and the gear 12f meshes with a gear 46a of a screw 46 provided rotatably on the stator 40. ing. Since the screw 46 is regulated by the stator 40, it does not move in the axial direction. A helical spline 46 b is formed on the screw 46, and this helical spline 46 b is engaged with the helical spline 48 a of the nut 48.

The front end portion 48b of the nut 48 is engaged with the guide groove 40f of the stator 40, and is configured to be movable in the axial direction. Note that three sets of screws 46 and nuts 48 are provided in the same manner as the trunnion 36. The groove 48c formed in the nut 48 is engaged with the arm 36h of the trunnion 36 as in the case of the third embodiment. Accordingly, the screw 46 is rotated together with the rotation of the control shaft 12, the nut 48 is moved in the axial direction by the action of the helical spline 46b and the helical spline 48a, and the trunnion 36 is tilted and twisted as in the case of the third embodiment. To do.

The operation of the continuously variable transmission according to the fourth embodiment is that the difference between the configuration of the fourth embodiment and the configuration of the third embodiment is that the rotation of the control shaft 12 is tilted and twisted. This is basically the same as the operation of the third embodiment because only the configuration of the portion to be transmitted to is different. Therefore, detailed description regarding the operation is omitted. Moreover, since the effect of the continuously variable transmission according to the fourth embodiment is basically the same as that of the first embodiment, description thereof is omitted.

(Fifth embodiment)
FIG. 9 shows a cross section corresponding to FIG. 1 of a continuously variable transmission according to a fifth embodiment of the present invention. Here, the description will focus on parts that are different from the configuration of the continuously variable transmission according to the first embodiment, and parts that are substantially the same as the configuration of the continuously variable transmission are denoted by the same reference numerals and description thereof is omitted. .

The difference between the fifth embodiment and the first embodiment is that the thrust sleeve 34 that connects the input disk 20 and the output disk 22 in the first embodiment is provided in the fifth embodiment. It is not. Accordingly, the thrust generated by the loading mechanism 28 is transmitted to the hub shell 14 via the bearing 34a and the cover 16, and further transmitted from the hub shell 10 to the output disk 22 via the bearing 15, and from the output disk 22 to the second roller 26 and By acting on the input disk 20 via the first roller 24, they cancel each other and cancel each other.

The operation of the continuously variable transmission according to the fifth embodiment is different from the configuration of the fifth embodiment and the configuration of the first embodiment in that the configuration of the circulation path of the thrust generated by the loading mechanism 28 is the same. Since only the difference is made and there is no difference in the operation of the continuously variable transmission, the detailed description regarding the operation is omitted.

The effect of the continuously variable transmission according to the fifth embodiment will be described. In the fifth embodiment, since the thrust described above is transmitted via the bearing 15, the bearing loss is reduced according to the rotational speed difference between the output shaft 1 and the hub shell 14 in the first embodiment. The power transmission efficiency slightly deteriorates except in the vicinity of the gear ratio 1. On the other hand, since there is no thrust sleeve 34 in the first embodiment, the effects of reducing the weight and size and reducing the manufacturing cost can be obtained.

(Sixth embodiment)
FIG. 10 shows the framework of a continuously variable transmission according to the sixth embodiment of the present invention, and only the upper half of the axial center of the main part corresponding to FIG. 1 is shown. Although details of the control system and the like are not shown, they are basically the same as those in the first embodiment. Here, the description will focus on parts that are different from the configuration of the continuously variable transmission according to the first embodiment, and description of substantially the same parts as those of the continuously variable transmission will be omitted.

The major difference between the sixth embodiment and the first embodiment is that the input shaft 10 is arranged on the left side in the drawing and the output shaft 18 is arranged on the right side in the drawing, and the output gear 18a is connected to the output shaft 18. Is formed integrally. The output gear 18a can drive a counter gear (not shown). The output gear 18a may be a pulley or a sprocket. Further, the fixed shaft 4 is fixed to the case 5. The control shaft 12 is disposed between the fixed shaft 4, the output shaft 18 and the output disk 22. Note that the posture of the trunnion 36 in FIG. 10 is shown in a state where the gear ratio is the largest. The illustration and description of other configurations in the sixth embodiment are omitted. The operation in the sixth embodiment is basically the same as that in the first embodiment. Further, the loading mechanism 28 is shown in a mechanical configuration like the loading mechanism 28 in the sixth embodiment, but it can be replaced with a hydraulic type.

The effect of the continuously variable transmission according to the sixth embodiment is the same as that of the first embodiment, in addition to the effects of the first embodiment, such as a vehicle such as an automobile using an engine as a power source, or a general machine using an electric motor as a power source. It exists in the point which can be used as a continuously variable transmission.

As described above in detail, the continuously variable transmissions according to the first to sixth embodiments of the present invention can compactly combine the elements of the operation system that change the gear ratio, so that bicycles, automobiles, and the like It can be used as a transmission for general machinery. In any case, the configuration is simple, and it is possible to reduce the size and weight, and it is possible to provide at low cost.

The embodiments described above are all illustrative of the present invention and are not intended to be limiting, and the present invention can be implemented in other various modifications and changes. In other words, the continuously variable transmission according to the present invention can be implemented in a mode in which improvements and contrivances according to applications are made without being limited by the above-described configuration and shape based on general knowledge of those skilled in the art. The scope of the present invention is defined only by the claims and their equivalents.

The continuously variable transmission of the present invention can be used as a transmission for bicycles, automobiles and general machines that are particularly required to have high power transmission efficiency and a small size.

1 Hub shaft (fixed shaft)
1a collar 2 frame 3 spoke 4 fixed shaft 5 case 10

input shaft

10a, 14a, 15, 16a, 34a bearing 10b sprocket 12

control shaft

12a,

38b washer

12b, 34b, 38c, 40c snap ring

12c control arm

12d, 38e, 44a, 44b, 46b, 48a Helical spline 12f, 46a Gear 14 Hub shell (output shaft)
14c, 36g, 40g, 42b Hole 14d Flange 16 Cover 18 Output shaft 18a Output gear 20 Input disc 20a First toroidal surface 22 Output disc 22a Second toroidal surface 24

First roller

24a, 26a

First friction surface

24b, 26b Second Friction surface 26 Second roller 28

Loading mechanism

30, 40h, 42d Spring 32 One-way clutch 34 Thrust sleeve 36 Trunnion 36a Protrusion 36b First pin 36c

Second pin

36d, 36e Tip 36f Recess 36h Arm 38 Guide sleeve

38a Helical groove 38d Notch

38f Guide projection 40

Stator

40a, 44c Groove

40b Bottom surface

40d Support pin

40e Check groove

40f Guide groove

40i, 42c Ball 42 Control lever 42a End

42e First cam

42f Second cam 44 Intermediate member

44d Operation arm 44e Tip

44g Operation groove 46 Screw 48 Nut 48c Groove

Claims

An input disk coupled to the input shaft, an output disk coupled to the output shaft, and disposed between the input disk and the output disk, each including a first roller and a second roller and the first roller and the A plurality of trunnions that rotatably support the second roller, and the first rollers of each trunnion form a first friction surface that abuts at a point A on a first toroidal surface formed on the input disk. The first roller and the second roller of each trunnion form a second friction surface that abuts each other at point B, and the second roller of each trunnion is formed on the output disk. A continuously variable transmission that forms a first friction surface that contacts the second toroidal surface at a point C, and is configured such that the points A, B, and C are arranged substantially in a straight line;
A fixed shaft coaxial with the input disk and the output disk is disposed at the center, and each trunnion is supported to be tiltable by a stator provided integrally with the fixed shaft, and the input disk and By rotating the control shaft provided in the outer diameter of the output disk coaxially with the fixed shaft, the points A and C are changed in the radial direction around the point B, and each trunnion tilts. A continuously variable transmission that is configured as described above.
The continuously variable transmission according to claim 1, wherein each trunnion is configured to be tiltable by rotating the control shaft and to be twisted about the point B.
The guide sleeve further includes a guide sleeve provided radially inward of each trunnion, the guide sleeve has a guide groove or a guide protrusion on an outer peripheral surface, and the protrusion provided radially inward of the plurality of trunnions The continuously variable transmission according to claim 1, wherein a hole is configured to engage with the guide groove or the guide protrusion.
The guide groove of the guide sleeve is a helical groove, the guide sleeve is fixed to the fixed shaft so as not to move in the axial direction, and is configured to rotate with the control shaft in the circumferential direction. The continuously variable transmission according to claim 3.
The guide sleeve and the control shaft are connected to each other via a helical spline, and the control shaft or the control shaft and the guide are driven by a thrust generated in the helical spline by torque that the control shaft drives the guide sleeve. The continuously variable transmission according to claim 3 or 4, wherein an intermediate member provided between the sleeve and the sleeve is configured to move in the axial direction to twist each trunnion.
A protrusion is provided at a position away from the point B in each radial direction and circumferential direction in each trunnion, and a shifter connected to the control shaft by a helical spline is provided outside the control shaft in the radial direction. When the shifter moves in the axial direction by rotation of the control shaft, the trunnions are tilted and / or twisted by pressing the protrusions in the axial direction. The continuously variable transmission according to any one of claims 1 to 5.
A thrust sleeve is provided radially outside the input disk and the output disk, and the thrust sleeve is configured to receive an axial load acting between the input disk and the output disk. The continuously variable transmission according to any one of claims 1 to 6.
2. A hub shell constituting the output shaft is provided, and the hub shell and a cover integrated with the hub shell are arranged so as to surround the input disk and the output disk. 8. The continuously variable transmission according to any one of 1 to 7.