JP2007327558A - Toroidal continuously variable transmission - Google Patents

Abstract

The output side disk 16 can be reduced in size as a whole, and the output side disk 16 can be formed directly on the outer peripheral edge of the output side disk 16 while ensuring the processing accuracy of the output side disk 16. A structure capable of reducing the size and weight of the disk 16 is realized.
The axial center of the output gear 17 and the axial center of the output side disk 16 are shifted in the axial direction. Then, the output gear 17 and the cylindrical surface portion 18 that smoothly continues over the entire circumference are provided on the outer peripheral edge of the output side disk 16 in a state adjacent to each other in the axial direction. The cylindrical surface portion 18 becomes a portion (shoe receiving range) that comes into contact (sliding contact) with the shoe when the output side disk 16 is ground.
[Selection] Figure 1

Description

  The present invention relates to an improvement in a toroidal-type continuously variable transmission that is used, for example, as a transmission unit constituting an automatic transmission for automobiles or as a transmission for adjusting the operating speed of various industrial machines such as pumps.

  As described in many publications such as Patent Documents 1 to 5 and Non-Patent Documents 1 and 2, the use of a toroidal continuously variable transmission as a transmission unit of an automatic transmission for automobiles has been studied. Some have been implemented. FIG. 4 shows a so-called double-cavity type of such a toroidal-type continuously variable transmission. Patents are made at two positions in the axial direction of the input rotary shaft 1 which is the rotary shaft described in the claims. A pair of input side disks 2a and 2b, which are outer disks described in claims, are supported. Each of these input side disks 2a, 2b is a toroidal curved surface (concave surface having a circular arc cross section) with respect to the input rotation shaft 1, and is in the input side corresponding to one axial side surface recited in the claims. In a state where the side surfaces 3 and 3 are opposed to each other, concentric and synchronized rotation is supported freely.

  Further, an output side disk 4 corresponding to the inner disk described in the claims is provided at an intermediate portion of the input rotary shaft 1 relative to the input rotary shaft 1 by a rolling bearing (not shown) (for example, a radial needle bearing). Is supported freely. In this state, the output side inner surfaces 5 and 5 of the output side disks 4 are toroidal curved surfaces (concave arc-shaped concave surfaces) and correspond to the axially opposite side surfaces recited in the claims. , Opposite to the input side inner surfaces 3, 3. Further, an output gear 6 provided on the outer peripheral surface of the output side disk 4 and corresponding to the gear described in the claims is engaged with another gear fixed to an output rotation shaft (not shown). Power can be transmitted to the output rotation shaft.

  Further, a plurality of (generally two or three) power rollers 7 are provided in the space (cavity) between the input side and output side inner surfaces 3 and 5 around the input rotation shaft 1. 7 are arranged. Each of these power rollers 7 and 7 has a spherical convex surface on the peripheral surfaces 8 and 8 that are in contact (rolling contact) with the inner surfaces 3 and 5 on both the input side and the output side. It is supported on the inner surface of the shaft so as to be freely rotatable and slightly oscillating. Further, each of these support members is provided with a swinging displacement around a pivot that is in a twisted position with respect to the input rotary shaft 1.

  When changing the gear ratio between the input side disks 2a, 2b and the output side disk 4, the support member is displaced in the axial direction of the pivot (front and back direction in FIG. 4). As a result, rolling contact portions (traction portions) between the peripheral surfaces 8 and 8 of the power rollers 7 and 7 and the input side and output side inner surfaces 3 and 5 of the input side and output side disks 2a, 2b and 4 respectively. ), The direction of the tangential force changes (side slip occurs at the rolling contact portion). As the direction of the force changes, the support members swing (tilt) about the pivot, and the peripheral surfaces 8, 8 of the power rollers 7, 7 and the input side and output side The contact positions of the disks 2a, 2b, and 4 with the input and output side inner surfaces 3 and 5 change.

  For example, as shown in the upper half of FIG. 4, the peripheral surfaces 8, 8 of each of the power rollers 7, 7 are arranged radially outwardly on the input side inner surfaces 3, 3 of the input side disks 2a, 2b. If rolling contact is made with the radially inner portions of the output-side inner surfaces 5 and 5 of the output-side disk 4, the gear ratio between the two disks 2a, 2b, and 4 is increased. On the other hand, as shown in the lower half of FIG. 4, the peripheral surfaces 8, 8 of the power rollers 7, 7 are arranged in the radial direction of the input side inner surfaces 3, 3 of the input side disks 2a, 2b. The rolling ratio between the discs 2a, 2b and 4 becomes the deceleration side when it is brought into rolling contact with the offset portion and the radially outer portion of the output side inner surfaces 5 and 5 of the output side disc 4. . In FIG. 4, for convenience of explanation, the inclination directions (shift states) of the power rollers 7 and 7 are different between the upper half and the lower half. However, during actual operation, the power rollers 7 and 7 are inclined in the same direction (the same speed change state) with respect to the radial direction of the input side and output side disks 2a, 2b and 4 in both the upper half and the lower half. To do.

  During operation of the toroidal-type continuously variable transmission as described above, the pair of input side disks 2a, 2b are pressed in the direction approaching each other by the hydraulic pressing device 9, and both of these input side disks 2a, 2b are pressed. The rotation is transmitted to the output side disk 4 through the power rollers 7 and 7. Further, if necessary, a preload spring such as a disc spring is provided in at least one of the pair of hydraulic chambers 10a and 10b constituting the pressing device 9, and both these hydraulic pressures are provided. Even when no hydraulic pressure is introduced into the chambers 10a and 10b, the input side and output side inner side surfaces 3 and 5 of the input side and output side disks 2a and 2b and the peripheral surfaces of the power rollers 7 and 7 are provided. The surface pressure of the rolling contact portion with 8 and 8 should be ensured to a minimum.

  By the way, in the case of the structure shown in FIG. 4 described above, the output side disk 4 is integrally formed in order to reduce (downsize) the axial dimension of the output side disk 4. That is, this output disk 4 is not formed by connecting and fixing a pair of separate output disks 4a and 4b as shown in FIG. 3 described later, for example. A single material having a shape such as bonded and fixed is formed by performing necessary processing such as cutting, grinding (polishing), and heat treatment, and is integrally formed. An output gear 6 is provided concentrically with the output-side disk 4 on the outer peripheral edge of the output-side disk 4 that is integrally formed (configured by a single member). When the output gear 6 is provided on the outer peripheral edge of the output side disk 4 as described above, the output gear 6 is directly formed on the outer peripheral edge of the output side disk 4 as in the structure shown in FIG. As shown in FIG. 5, the output side disk 4c and the output gear 6a which are separate from each other may be coupled and fixed. FIG. 5 shows the structure described in Patent Documents 3 and 4.

  In any case, when the output gears 6 and 6a are provided on the outer peripheral edge of the output side disks 4 and 4c as described above, conventionally, the axial centers of the output side disks 4 and 4c and the output gears 6 and 6a The center in the axial direction was matched with the axial direction. In other words, at the center in the axial direction of the output side disks 4, 4 c, a virtual plane (see FIG. 4) intersecting the central axis X (see FIG. 4) of the output side disks 4, 4 c at right angles, and the output gear The virtual planes B intersecting at right angles to the central axis X of the output gears 6 and 6a at the centers of the axial directions of the output gears 6 and 6a were made to coincide with each other (to be in the same plane). However, such a structure may cause the following problems.

  First, in the case of the structure in which the output gear 6 is directly formed on the outer peripheral edge portion of the output side disk 4 as shown in FIG. 4 described above, it becomes difficult to ensure the processing accuracy of the output side disk 4 (desired surface). (It is difficult to obtain roughness). That is, when the output side inner surfaces 5 and 5 of the output side disk 4 are ground, a shoe is brought into contact with the outer peripheral edge of the output side disk 4 (sliding contact and sliding contact). The output side disk 4 is prevented from being displaced in the radial direction while allowing the rotation of the output side disk 4. Such a shoe is brought into contact with a portion (cylindrical surface portion) formed in a cylindrical surface shape over the entire circumference in the outer peripheral edge portion of the output side disk 4 to rotate the output side disk 4. This is preferable from the viewpoint of ensuring the processing accuracy of the output-side inner side surfaces 5 and 5 (obtaining a desired surface roughness). On the other hand, in order to ensure the strength of the output gear 6, it is necessary to secure a certain amount of the axial dimension of the output gear 6. Therefore, in the case where the output gear 6 is directly formed on the outer peripheral edge of the output side disk 4 as described above, the shoe and the outer peripheral edge of the output side disk 4 are based on the presence of the output gear 6. There is a possibility that the contact portion (shoe receiving range) becomes small. When the contact portion becomes smaller in this way, the support rigidity of the output disk 4 (rigidity against the pressing force of the grindstone) and the rotation accuracy, and eventually the grinding precision (surface roughness) of the output side inner surfaces 5 and 5 will be described. , Size and shape accuracy) may be difficult to ensure. In addition, when the contact portion is extremely small, there is a possibility that the contact portion may be burned (burned), which is not preferable.

  In order to prevent the occurrence of such inconvenience, for example, an axial direction sufficient to bring the shoe into contact with both side portions of the outer peripheral edge portion of the output side disk 4 sandwiching the output gear 6 in the axial direction. It is conceivable to provide cylindrical surface portions having dimensions. However, in such a case, even if the above-described inconvenience can be prevented, the axial dimension of the output side disk 4 as a whole is increased (the axial thickness is increased), and the size and weight are reduced. It is not preferable from the aspect of aiming. Further, like the structure described in Patent Document 5, for example, the shoe is brought into contact with a portion of the axial side surface of the output side disk 4 that is radially removed from the output side inner side surfaces 5 and 5. It is also conceivable to provide a reference surface (reference surface) for the entire circumference while processing. However, in such a case, the radial dimension of the output side disk 4 is increased (the diameter is increased) by the width dimension of the reference surface, so that the size and weight can be reduced in the same manner as described above. Is not preferred.

  On the other hand, in the case of the structure in which the output side disk 4c and the output gear 6a, which are separate from each other, as shown in FIG. Is unlikely to occur. However, an output gear 6a that is separate from the output side disk 4c is externally fitted to the output side disk 4c and further fixed by welding or the like. The outer diameter of the output gear 6a is shown in FIG. It is larger than the ones, and it is disadvantageous in terms of miniaturization and weight reduction. For example, when a toroidal type continuously variable transmission as shown in FIG. 5 is configured as a transmission device for an FF vehicle (front engine front wheel drive vehicle), the output gear 6a and the output gear 6a are taken out. Shifting from the positional relationship with other members (for example, various members (constituent members) for constituting the planetary gear type transmission 11, the clutch devices 12, 12, the final reduction gear 13, etc.) for transmitting the transmitted power. There is a possibility that the device as a whole cannot be sufficiently downsized. That is, for example, in the case of configuring such a transmission, a planetary gear type transmission 11 and a clutch device 12 are provided around a transmission shaft 15 provided in parallel with the input rotary shaft 1 constituting the toroidal continuously variable transmission. 12 and the final reduction gear 13 need to be arranged.

  On the other hand, depending on the assembly position of the toroidal type continuously variable transmission in the transmission, for example, depending on the structure of various vehicles on which the transmission is mounted, for example, the structure of an engine room or a floor tunnel, the above-described apparatuses 11, 12, 13 In some cases, restrictions are imposed on the positional relationship (layout) of the constituent members. For example, with respect to the transmission gear 14 that meshes with the output gear 6a, for example, it is required to arrange a large number of the constituent members of the devices 11, 12, and 13 in the α portion on the left side of FIG. Conversely, there are cases where it is required to arrange a large number of these constituent members in the β portion on the right side of FIG. However, in such a case, depending on the positional relationship between the output gear 6a and the constituent members, the constituent members cannot be efficiently disposed in the portions, and the transmission apparatus as a whole cannot be sufficiently downsized. There is sex. Specifically, since the axial position of the transmission gear 14 needs to be regulated by the axial position of the output gear 6a, the axial dimensions of the α and β portions are limited, and the components of the above components can be efficiently operated. There is a possibility that it cannot be arranged. Such inconvenience also occurs in the case of the structure in which the output gear 6 is directly formed on the outer peripheral edge of the output side disk 4 as shown in FIG.

JP 2003-301908 A JP 2004-197793 A JP 2000-179664 A Japanese Patent Laid-Open No. 10-267106 JP 2003-156112 A Motoo Aoyama, “Bessed Best Car Red Badge Series 245 / A book that understands the latest mechanics of cars”, Sangensha Co., Ltd./Kodansha Co., Ltd., December 20, 2001, p. 92-93 Hirohisa Tanaka, “Toroidal CVT”, Corona Inc., July 13, 2000

  The toroidal-type continuously variable transmission of the present invention can contribute to the miniaturization of the transmission as a whole in view of the above circumstances, and an output gear (gear) on the outer peripheral edge of the output side disk (inner disk). The invention has been invented to realize a structure capable of reducing the size and weight of the output side disk while ensuring the processing accuracy of the output side disk even when directly forming the disk.

The toroidal-type continuously variable transmission of the present invention has a rotating shaft, a pair of outer disks, an inner disk, a plurality of support members, The same number of power rollers as the supporting members are provided.
Among these, the rotating shaft is rotatably supported in the casing, for example.
In addition, the both outer disks are arranged at two positions in the axial direction of the rotating shaft in a state in which the respective one side surfaces in the axial direction, which are concave surfaces (traction surfaces) each having an arcuate cross section, are opposed to each other. Rotation synchronized with is supported as free.
In addition, the inner disk is in a state in which both side surfaces in the axial direction, which are concave surfaces (traction surfaces) each having an arcuate cross section, are opposed to one side surface in the axial direction of the outer disks, respectively, at the intermediate portion of the rotating shaft. The relative rotation with respect to the rotating shaft is supported freely.
Each of the support members has a plurality of pivots in a position twisted with respect to the rotary shaft, each in a position between both axial side surfaces of the inner disk and one axial side surface of the outer disks. Oscillating displacement around the center is freely provided.
Each of the power rollers is rotatably supported by the support member and has a spherical convex surface that is in contact with both axial sides of the inner disk and axial sides of the outer disks. They are in contact (rolling contact).
A power transmission gear is provided concentrically with the inner disk on the outer peripheral edge of the inner disk.

In particular, in the toroidal type continuously variable transmission of the present invention, the axial center of the gear and the axial center of the inner disk are offset from each other in the axial direction.
In this case, preferably, as described in claim 2, the inner disk is constituted by a single member. That is, the both side surfaces in the axial direction, which are concave surfaces having an arcuate cross section constituting the inner disk, are formed on both side surfaces in the axial direction of a single member (material), and the inner disk is integrally formed.
More preferably, as described in claim 3, a gear is directly formed on the outer peripheral edge portion of the inner disk integrally formed as described above, and the inner disk and the gear are integrally formed.

  As described above, in the case of the toroidal type continuously variable transmission according to the present invention, the axial center of the inner disk and the axial center of the gear are shifted in the axial direction. By this, this gear and each member (constituent member) which comprises a transmission can be arranged efficiently. That is, even if there is a restriction on the arrangement (layout) of the inner disk and each component, the axial position of the gear with respect to the inner disk is shifted in an appropriate direction in consideration of the installation position of each component. By this, this gear and each said structural member can be arrange | positioned efficiently, and it can contribute to size reduction as the whole transmission. In other words, the flexibility (degree of freedom, margin) of the positional relationship with respect to the gear can be ensured, and the ease of incorporation of the transmission (ease of incorporation into a restricted space) can be improved.

  Further, as in the structure described in claims 2 and 3, the inner disk is integrally formed (configured by a single member), and a gear is directly formed on the outer peripheral edge of the integrally formed inner disk. In this case, not only can the transmission as described above be reduced in size and increase in ease of incorporation, but the inner disk can be made smaller and lighter while ensuring the processing accuracy of the inner disk. That is, by shifting the axial centers of the inner disk and the gear from each other, the outer peripheral edge of the inner disk has the axial dimension sufficient to ensure the necessary strength, and the grinding process. In this case, the cylindrical surface portions having sufficient axial dimensions for abutting (sliding contact) necessary shoes are provided adjacent to (adjacent to) each other in the axial direction. For this reason, the necessary shoes can be brought into contact with the cylindrical surface portion during the grinding process without increasing the axial dimension of the inner disk. The arc-shaped concave traction surface) can be ground with high precision (desired surface roughness, shape and dimensional accuracy can be obtained).

[First example of embodiment]
FIG. 1 shows a first example of an embodiment of the present invention corresponding to all of claims 1 to 3. The feature of this example is that the positional relationship between the output side disk 16 and the output gear 17 is devised to reduce the size of the transmission as a whole and to improve the assemblability, as well as the processing accuracy of the output side disk 16. This is because the output side disk 16 is configured to be small and light weight while securing the above. Since the structure and operation of other parts are the same as those shown in FIGS. 4 to 5 described above, overlapping illustrations and explanations are omitted or simplified, and the following description will focus on the characteristic parts of this example.

  Also in this example, the output gear 17 for power transmission, which is also equivalent to a gear, is provided on the outer peripheral edge of the output disc 16 corresponding to the inner disc described in the claims. Concentric with. In the case of this example, the output side disk 16 is composed of a single member. That is, the output side inner surfaces 5 and 5 that are concave surfaces having an arc cross section forming the output side disk 16 are formed on both side surfaces in the axial direction of a single member, and the output side disk 16 is integrally formed. Forming. In the case of this example, the output gear 17 is directly formed on the outer peripheral edge portion of the output side disk 16, and the output side disk 16 and the output gear 17 are integrally formed. When such an output side disk 16 is manufactured, necessary processing such as cutting, grinding, heat treatment or the like is applied to a single material having a shape such that a pair of disks are coupled and fixed as shown in FIG. The output side disk 16 is assumed. Incidentally, since the manufacturing method of such an output side disk 16 is described in, for example, Patent Document 1 and the like, detailed description thereof is omitted.

  In the case of this example, the axial center of the output gear 17 and the axial center of the output disk 16 are shifted from each other with respect to the axial direction of the output gear 17 and the output disk 16. In other words, the center of the output gear 17 at the center of the output side disk 16 at the center in the axis direction of the output side disk 16 and perpendicular to the center axis X of the output side disk 16 and the center of the output gear 17 in the axis direction. The virtual planes B intersecting the axis X at right angles are arranged in parallel with each other in a state shifted in the axial direction. And by comprising in this way, the said output gear wheel 17 and the cylindrical surface part 18 which continues smoothly over a perimeter in the outer peripheral part of the said output side disk 16 are the states adjacent to an axial direction. Provided. In the case of this example, this cylindrical surface portion 18 is a portion (shoe receiving range) where the shoe comes into contact (sliding contact) during grinding.

  According to the toroidal type continuously variable transmission of the present example configured as described above, the axial center of the output side disk 16 and the axial center of the output gear 17 are shifted with respect to this axial direction, for example, FIG. 1 can be increased. For this reason, each member (constituent member) which comprises a transmission is made into the space corresponding to this distance A, ie, the space which spreads in the axial direction one side (left side of FIG. 1) of the transmission gear meshed with the said output gear 17. Can be arranged efficiently. That is, the arrangement of the output side disk 16 and each component {for example, various members for constituting the planetary gear type transmission 11, the clutch devices 12, 12 and the final reduction device 13 as shown in FIG. 5}. When restrictions are imposed on (layout), these components can be efficiently arranged in the space corresponding to the distance A, thereby contributing to downsizing of the entire transmission. In other words, the flexibility (degree of freedom, margin) of the positional relationship with respect to the output gear 17 can be ensured, and the ease of incorporation of the transmission (ease of incorporation into a limited space) can be improved.

  In the case of this example, the output gear 17 is directly formed on the outer peripheral edge portion of the integrally formed output side disk 16, but this output side disk 16 is secured while maintaining the processing accuracy. The side disk 16 can be configured to be small and light. That is, by shifting the axial centers of the output side disk 16 and the output gear 17 from each other as described above, an axial dimension sufficient to ensure the necessary strength at the outer peripheral edge of the output side disk 16. The output gear 17 having the above and the cylindrical surface portion 18 having an axial dimension sufficient to abut a shoe necessary for grinding are provided adjacent to each other in the axial direction. Therefore, even if the axial dimension of the output side disk 16 is not increased, the necessary shoe can be brought into contact with the cylindrical surface portion 18 during the grinding process, and the output side of the output side disk 16 can be contacted. The inner side surfaces 5 and 5 (the traction surface which is a concave surface having an arc cross section) can be ground with high accuracy (a desired surface roughness, shape and dimensional accuracy can be obtained).

[Second Example of Embodiment]
FIG. 2 shows a second example of the embodiment of the present invention, which also corresponds to all of claims 1 to 3. In the case of the first example described above, the output gear 17 is provided with a pressing device 9 in the axial half of the outer peripheral edge of the output side disk 16 (the right half in FIG. 1), that is, in the axial direction. The other side (the left side in FIG. 1) is provided on the other side (the right side in FIG. 1) of the input side disk 2b. On the other hand, in the case of this example, the output gear 17a is provided with the pressing device 9 in the other half in the axial direction (the left half in FIG. 2) of the outer peripheral edge of the output side disk 16, that is, in the axial direction. The other half (left side in FIG. 2) is provided in the half of the input side disk 2a. In the case of this example as well, for example, the distance B shown in FIG. 2 can be increased, and the members (components) constituting the transmission can be efficiently arranged in the space corresponding to the distance B. Necessary shoes can be brought into contact with the cylindrical surface portion 18, and the output-side inner surfaces 5, 5 of the output-side disk 16 can be ground with high accuracy.
Other configurations and operations are the same as those in the first example described above, and thus redundant description is omitted.

[Third example of embodiment]
FIG. 3 shows a third example of the embodiment of the present invention corresponding to the first aspect. In the case of the above-described first example and the above-described second example, the output gears 17 and 17a (see FIGS. 1 and 2) are formed on the outer peripheral edge portion of the output-side disk 16 formed integrally (configured by a single member). Forming directly. On the other hand, in the case of this example, a pair of output side disks 4a, 4b are opposed to each other, and the output gear 17c is sandwiched between the backs, welding, shrink fitting, etc. Thus, they are coupled and fixed to each other. That is, the output side disks 4a and 4b and the output gear 17c are coupled and fixed so as to be able to rotate in synchronization with each other. Then, with the output side disks 4a and 4b and the output gear 17c coupled and fixed in this manner, the inner side disk constituted by the axial center of the output gear 17c and the pair of output side disks 4a and 4b. Are axially shifted from each other in the axial direction. In the case of this example, a combination of the output side disks 4a and 4b corresponds to the inner disk described in the claims.

In the case of this example, the output side inner surfaces 5 and 5 of the output side disks 4a and 4b are ground before the output side disks 4a and 4b and the output gear 17c are coupled and fixed. Can do. For this reason, the effect acquired by ensuring the part which contacts (sliding contact) like the above-mentioned 1st and 2nd examples is small. However, the effect that the members (constituent members) constituting the transmission can be efficiently arranged to reduce the size of the transmission and improve the ease of incorporation can be obtained as in the first and second examples.
Other configurations and operations are the same as those in the first and second examples, and thus a duplicate description is omitted.

Sectional drawing which shows the 1st example of embodiment of this invention in the state from which the shifting state of a power roller differs in an upper half part and a lower half part. Sectional drawing similar to FIG. 1, showing the second example. Sectional drawing similar to FIG. 1 showing the third example. Sectional drawing similar to FIG. 1 which shows the 1st example of a conventional structure. Sectional drawing which shows the 2nd example in the state integrated in the transmission.

Explanation of symbols

DESCRIPTION OF SYMBOLS 1 Input rotating shaft 2a, 2b Input side disk 3 Input side inner surface 4, 4a, 4b, 4c Output side disk 5 Output side inner surface 6, 6a Output gear 7 Power roller 8 Peripheral surface 9 Pressing device 10a, 10b Hydraulic chamber 11 Planetary gear type transmission 12 Clutch device 13 Final reduction device 14 Transmission gear 15 Transmission shaft 16 Output side disk 17, 17a, 17c Output gear 18 Cylindrical surface portion

Claims (3)

  With the rotating shaft and each side surface in the axial direction, each of which is a concave surface having an arc-shaped cross section, facing each other in the axial direction of the rotating shaft, the rotation synchronized with the rotating shaft is freely supported. In the state where the axially opposite side surfaces, each of which is a concave surface having a circular arc cross section, are opposed to the axially one side surfaces of the both outer disks, respectively, A plurality of inner disks that are supported to freely rotate relative to the rotating shaft, and a plurality of inner disks in the axial direction between the both axial side surfaces of the inner disk and one axial side surface of the outer disks. A support member that is provided with a swingable displacement centering on the pivot at the twisted position, and a circumferential convex surface that is rotatably supported by each of the support members and has a spherical convex surface. Both directions A toroidal-type stepless motor comprising a power roller abutting on the surface and one axial side surface of both outer disks, and a power transmission gear provided concentrically with the inner disk on the outer peripheral edge of the inner disk. A toroidal continuously variable transmission characterized in that the axial center of the gear and the axial center of the inner disk are shifted in the axial direction.   The toroidal-type continuously variable transmission according to claim 1, wherein the inner disk is constituted by a single member.   The toroidal continuously variable transmission according to claim 2, wherein a gear is directly formed on the outer peripheral edge of the inner disk.

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