JP2006307900A - Toroidal type continuously variable transmission - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To provide a toroidal type continuously variable transmission capable of positioning an axial position of a retainer 7b of a thrust ball bearing 5 supporting a power roller 3 at an axial center between the power roller 3 and an outer wheel and making an axial displacement of the retainer 7b small. <P>SOLUTION: Inner surfaces 17, 17 of pockets 11a, 11b of the retainer 7b consists of a cylindrical surface part 118 and a spherical surface part 19. When pockets having the spherical surface parts 18 provided in one side in an axial direction of the retainer 7b out of the each pockets 11a, 11b are defined as first pockets 20, 20 and ones provided in another side are defined as second pockets 21, 21, the first pockets 20, 20 and the second pockets 21, 21 are alternately arranged in a circumference direction of the retainer 7b. <P>COPYRIGHT: (C)2007,JPO&INPIT

Description

  The toroidal continuously variable transmission according to the present invention is used as an automatic transmission for automobiles or as a transmission for adjusting the operating speed of various industrial machines such as pumps.

  Toroidal-type continuously variable transmissions used as automatic transmissions for automobiles are described in many publications such as Patent Document 1, Non-Patent Documents 1 and 2, and are partly implemented and well known. Such a toroidal-type continuously variable transmission includes, for example, as shown in FIG. 8, input side disks 1 and 1 corresponding to a first disk whose toroidal curved surfaces are opposite to each other in the axial direction, and a second disk. A plurality of power rollers 3 and 3 are sandwiched between output side disks 2 and 2 corresponding to the above. During operation, the rotation of the input side disks 1, 1 is transmitted to the output side disks 2, 2 via these power rollers 3, 3. The power rollers 3 and 3 are rotatably supported by trunnions 4 and 4, respectively. The trunnions 4 and 4 are pivots (twisted with respect to the central axes of the disks 1 and 2). Oscillating displacement centered around (not shown) is supported freely. When changing the gear ratio between the disks 1 and 2, the trunnions 4 and 4 are displaced in the axial direction of the pivot by, for example, a hydraulic actuator (not shown).

  As a result, the direction of the tangential force acting on the rolling contact portion (traction portion) between the peripheral surface of each of the power rollers 3 and 3 and the inner surface of each of the input and output discs 1 and 2 changes ( Side slip occurs at the rolling contact part). As the force changes, the trunnions 4 and 4 swing (tilt) about the pivot, and the peripheral surfaces of the power rollers 3 and 3 and the input and output disks 1 respectively. The position of contact with the inner surface of 2 changes. Rolling contact of the peripheral surfaces of the power rollers 3 and 3 with the radially outward portion of the inner surface of the input side discs 1 and 1 and the radially inward portion of the inner surface of the output side discs 2 and 2 By doing so, the gear ratio between the two disks 1 and 2 is increased. On the other hand, the peripheral surfaces of the power rollers 3 and 3 are arranged radially inwardly on the inner side surfaces of the input side disks 1 and 1 and radially outwardly on the inner side surfaces of the output side disks 2 and 2. If it is brought into rolling contact with the portion, the gear ratio between the two disks 1 and 2 is reduced.

  During the operation of the toroidal type continuously variable transmission as described above, the power rollers 3 and 3 rotate at high speed while receiving a large thrust load from both the input and output disks 1 and 2. For this purpose, thrust ball bearings 5 and 5 are provided between the power rollers 3 and 3 and the trunnions 4 and 4, respectively. It is possible to support the thrust load applied to As shown in detail in FIG. 9, each of these thrust ball bearings 5, 5 includes a plurality of balls 6, 6, a cage 7 for holding these balls 6, 6 so as to roll, and an outer ring. 8 and. Each of these balls 6, 6 is formed in a spherical shape by, for example, bearing steel or ceramic, and is an inner ring raceway which is a raceway surface formed on the outer side surface (upper side surface in FIG. 9) of each power roller 4. 9 and the outer ring raceway 10 which is the same raceway surface formed on the inner surface of the outer ring 8 (lower surface in FIG. 9).

  The cage 7 is formed in a ring shape from metal or synthetic resin, and has a plurality of pockets 11 and 11 at equal intervals in the circumferential direction at the radial intermediate portion. Each of the balls 6 and 6 is held in each of the pockets 11 and 11 so as to roll freely. Further, each outer ring 8 configured in a ring shape with bearing steel or ceramic or the like is abutted against the inner surface of each trunnion 4, 4 (FIG. 8) via a thrust needle bearing 12. In the case of the structure shown in FIG. 9, the outer ring 8 is supported on the support shaft 13 for rotatably supporting the power rollers 3, and the power rollers 3 are connected to the trunnion 4 on the input side. The output side discs 1 and 2 are integrally formed with a pivot shaft 14 for supporting the discs 1 and 2 in a state in which displacement in the axial direction is allowed.

  The thrust ball bearing 5 as described above rotates at high speed while supporting the thrust load applied to each of the power rollers 3 during operation of the toroidal type continuously variable transmission. For this reason, it is necessary to supply a sufficient amount of lubricating oil to each thrust ball bearing 5 during operation. For this reason, conventionally, one or a plurality of oil supply holes 15 (see FIG. 9) are formed in a part of the outer ring 5, and the lubricating oil is forcibly fed into the oil supply holes 15 during operation. . Further, as described in, for example, Patent Document 2 and the like, the thrust ball bearing 5 is used in order to distribute the lubricating oil fed in as described above to a portion requiring the lubricating oil such as a rolling contact portion. It has been conventionally performed to form concave grooves 16 and 16 (see FIG. 9) on both side surfaces in the axial direction of the cage 7 to be configured, and to use these concave grooves 16 and 16 as lubricating oil flow paths. Patent Document 3 and the like describe an invention for devising the cross-sectional shape of the concave grooves 16 and 16 as described above in order to reduce the size while ensuring the durability of the cage 4 as described above. Yes.

  Further, in Patent Document 4, as shown in FIGS. 10 to 11, the inner surfaces 17 and 17 of the pockets 11a and 11a of the cage 7a constituting the thrust ball bearing are represented by a cylindrical surface portion 18 and a spherical surface portion 19 (FIG. 11). The structure comprised by these is described. That is, with respect to the axial direction of the cage 7a, the cylindrical surface portion 18 and the spherical surface portion 19 that open to the opposite side surfaces are smoothly continuous at the intermediate portion, and the inner diameter of the cylindrical surface portion 18 among them. D is made larger than the outer diameter (diameter) d (FIG. 9) of the balls 6 and 6. If such a structure is adopted, the balls 6 and 6 can be assembled to the pockets 11a and 11a from the cylindrical surface portion 18 side, and the durability of the balls 6 and 6 and the cage 7a is improved. Decrease can be prevented. That is, for example, as in the structure described in Patent Document 5 or the like, the inner surface of the pocket is the spherical surface portion and the both end portions are cylindrical surface portions with respect to the axial direction of the cage, and the inner diameter of each cylindrical portion. Is smaller than the outer diameter of each ball, when assembling each ball in each of these pockets, while expanding the opening edge of each pocket radially outward by the rolling surface of each ball, Each of these balls needs to be pushed into each pocket.

  For this reason, when the opening edge of each pocket expands in the radial direction in this way, there is a possibility that damage such as a crack (crack) or the like may occur in each opening edge. May be reduced. For example, when the cage is made of a synthetic resin containing reinforcing fibers such as glass fibers, the reinforcing fibers and the rolling surfaces of the balls rub against each other when the balls are assembled in the pockets. In addition, the rolling surface of each ball may be damaged. Such damage may cause early separation of the rolling surfaces of these balls, and may reduce the durability of these balls. On the other hand, by adopting the structure as shown in FIGS. 10 to 11 described above, the inconveniences as described above can be prevented, and the durability of the cage 7a and the balls 6 and 6 can be secured.

  In the case of the structure shown in FIGS. 10 to 11, the positions where the spherical portions 19 and 19 of the pockets 11a and 11a are provided in the pockets 11a and 11a in the axial direction of the cage 7a. It is the same. That is, the spherical surface portions 19 and 19 are formed on the inner surfaces 17 and 17 of the pockets 11a and 11a on one side (the lower side in FIG. 11) with respect to the axial direction of the cage 7a. Are provided on the other side (upper side in FIG. 11). At the same time, with the balls 6 and 6 inserted into the pockets 11a and 11a, the pockets 11a and 11a on the other axial side surface of the retainer 7a (the upper surface in FIG. 11). The periphery of the opening edge (4 positions in the circumferential direction) is plastically deformed (caulked) toward the inside in the radial direction of the opening edge. And by carrying out plastic deformation in this way, the inner diameter of the opening edge of each pocket 11a, 11a on the side where the cylindrical surface portions 18, 18 are provided is made smaller than the outer diameter d of the balls 6, 6. The balls 6, 6 are prevented from falling off from the respective opening edges.

  However, when the opening edge is plastically deformed in this way, the cross-sectional shape of the inner surface of each of the pockets 11a, 11a with respect to the axial direction of the cage 7a is perpendicular to the central axis α (FIG. 11) of the cage 7a. And a virtual plane (FIG. 11) passing through the center in the axial direction of each of the pockets 11a and 11a is not symmetric. For this reason, in the state where the cage 7a is assembled to the thrust ball bearing 5, the axial position of the cage 7a is from the center between the races (power roller 1, outer ring 5 in FIGS. 8 and 9). There is a possibility of deviation. In other words, of the axial side surfaces of the cage 7a, the distance between the side surface on which the spherical surface portions 19 and 19 are provided and the side surface of the race ring facing this side surface is the same as the side surface on the cylindrical surface portions 18 and 18 side. And may be smaller than the distance between the side surface of the race ring facing this side surface. In such a case, the distance between the side surfaces of the spherical surface portions 19 and 19 and the side surfaces of the races is reduced during operation, and the lubricating oil is less likely to flow between the side surfaces. there is a possibility. When the side surfaces are in sliding contact with each other, not only the transmission efficiency is lowered, but also damage due to rubbing is likely to occur, and it is difficult to ensure the durability of the cage 7a and the race rings 3 and 8. Further, as described above, there is a possibility that the lubrication failure is likely to occur at the rolling contact portion on the side where the lubricating oil is difficult to circulate.

In particular, the power roller constituting the toroidal-type continuously variable transmission rotates at a high speed while receiving not only a thrust load but also a radial load based on the traction force applied to the rolling contact portion during operation. When such a radial load is applied to the cage via the balls constituting the thrust ball bearing, the axial force applied to the cage becomes non-uniform in the circumferential direction of the cage. easy. Specifically, the degree of non-uniformity is likely to be excessive because the axial force is locally applied in the circumferential direction of the cage, and the balance of the cage in the axial direction is likely to be lost. There is sex. When this balance is lost, the side surface of the cage and the side surface of the raceway are in sliding contact with each other, and the inconvenience as described above is likely to occur.
In Patent Document 5, with respect to the axial direction of the cage, a pocket in which the inner diameter of one opening edge is smaller than the inner diameter of the other opening edge, and conversely, the inner diameter of the other opening edge is Describes a structure in which pockets smaller than the inner diameter of the opening edge are alternately arranged one by one in the circumferential direction of the cage. However, in the above-mentioned Patent Document 5, such a structure is applied to a thrust ball bearing that supports a power roller constituting a toroidal continuously variable transmission, including a statement that suggests that. Not listed.

JP 2001-317601 A Utility Model Registration No. 2603559 JP 2000-310308 A Japanese Patent Laid-Open No. 2001-4003 Japanese Patent No. 3532663 Motoo Aoyama, "Bessed Best Car Red Badge Series 245 / A book that understands the latest mechanics of cars", Sanyusha 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 is a thrust ball bearing for supporting a power roller in view of the above-described circumstances, and the distance between the axial side surfaces of the cage and the side surface of the raceway is the same. It can be made (the cage can be positioned at the center in the axial direction between the races), and the invention has been invented to realize a structure that can reduce the axial displacement of the cage.

The toroidal type continuously variable transmission of the present invention includes, for example, the first and second disks, a plurality of power rollers, and a plurality of trunnions, as in the conventional toroidal type continuously variable transmission described in FIG. And a plurality of thrust ball bearings.
Of these, the first and second disks are supported concentrically so as to be freely rotatable relative to each other. The power rollers are sandwiched between the disks.
Further, each trunnion can be freely oscillated and displaced about the pivots concentrically provided at both end portions in a state where the respective power rollers are rotatably supported.
Each thrust ball bearing is provided between each trunnion and each power roller, and supports a load applied to each power roller.
Each of the thrust ball bearings includes a plurality of balls and an annular cage that holds each of the balls so as to roll.
Further, the cage is formed in a state of penetrating both side surfaces in the axial direction, and includes a plurality of pockets that hold the balls one by one so as to roll freely inside each.
The inner surface of each of these pockets is formed by smoothly connecting a cylindrical surface portion and a spherical surface portion, which open on the opposite side surfaces with respect to the axial direction of the cage, at the intermediate portion.
In particular, in the toroidal type continuously variable transmission of the present invention, each of the pockets is provided on the other side as well as the first pocket provided on one side with respect to the axial direction of the cage. Consists of a second pocket. And these 1st pockets and 2nd pockets are alternately arrange | positioned regarding the circumferential direction of the said holder | retainer.

According to the toroidal type continuously variable transmission of the present invention configured as described above, the thrust ball bearing for supporting the power roller can make the distance between the axial side surfaces of the cage and the side surface of the raceway the same. (The cage can be positioned in the center in the axial direction between the races), and the axial displacement of the cage can be reduced.
That is, with respect to the axial direction of the cage, the first pockets and the second pockets whose spherical portions are opposite to each other in the axial direction are alternately arranged in the circumferential direction of the cage. For this reason, the spherical portions of the first and second pockets are symmetric with respect to a virtual plane that intersects the central axis of each of the cages at right angles and passes through the axial center of the first and second pockets. Can be placed. Even if the cage tends to be displaced in the axial direction, the spherical portion provided in each first pocket is in sliding contact with the rolling surface of each ball, so that the cage is further in the other axial direction. While being able to prevent displacement, the spherical portion provided in each second pocket is in sliding contact with the rolling surface of each ball, so that the cage can be prevented from further displacement in one axial direction. For this reason, the distance between each side surface in the axial direction of the cage and the side surface of the raceway can be made the same, and the amount of axial displacement of the cage can be reduced.

  As a result, the side surfaces of these cages and the side surfaces of the bearing rings can be made difficult to slidably contact with each other, and it is also possible to prevent the lubricating oil from flowing between these side surfaces, thereby preventing a reduction in transmission efficiency and poor lubrication. The durability of the cage and the race can be ensured. In addition, since the durability of the cage can be ensured in this way, the cage can be reduced in size. In addition, by reducing the size of the cage and reducing the axial displacement of the cage as described above, the distance between the bearing rings of the thrust ball bearing can also be reduced. It is possible to reduce the size of the power roller unit incorporating the ball bearing, and thus the toroidal type continuously variable transmission as a whole. In addition, since the lubricating oil can be easily distributed as described above, the pump for feeding the lubricating oil can be reduced in size and the amount of the lubricating oil required can be reduced, and the transmission efficiency can also be improved from this aspect. In addition, since the lubrication state can be improved, it is possible to ensure the durability of the entire apparatus, and it is possible to prevent variations in durability due to the durability being easily lowered at the poorly lubricated portion.

When carrying out the present invention, for example, as described in claim 2, one first pocket and one second pocket are alternately arranged in the circumferential direction of the cage. In this case, if the total number of the pockets of the cage is an odd number, one of the first pocket and the second pocket including two consecutive portions is arranged.
If comprised in this way, the effect of the invention mentioned above can be effectively acquired by the thrust ball bearing which supports the power roller which made the total number of pockets about 8-16.

  Alternatively, when carrying out the present invention, for example, as set forth in claim 3, a set of a plurality of first pockets and second pockets is alternately arranged in the circumferential direction of the cage. To do. In this case, when the total number of pockets of the cage is a multiple of 4, two first pockets and two second pockets are alternately arranged. Further, when the total number of the pockets of the cage is not a multiple of 4, each set of two first pockets or second pockets is alternately arranged, and three first pockets or second pockets. Place one to three sets of pockets.

With this configuration, even when the force applied in the axial direction of the cage becomes non-uniform due to local application in the circumferential direction of the cage, the balance in the axial direction of the cage can hardly be lost. .
That is, even when a force is locally applied to the cage, the force applied locally can be supported by a plurality of first pocket groups or second pocket groups arranged in succession. Further, since the cage rotates at high speed during operation, the locally applied force can be supported by either the first pocket group or the second pocket group, and the balance of the entire cage is lost. It can be difficult. Therefore, compared with the case where these first pockets and second pockets are alternately arranged one by one, the allowable amount of force applied locally as described above can be increased, and the axial displacement amount of the cage can be further reduced. .

Further, when the present invention is carried out, preferably, as described in claim 4, the inner surface of each pocket and the rolling surface of each ball in a state where the center of each ball and the center of each pocket coincide with each other. Is set to 0.2 to 0.5 mm.
If comprised in this way, the fall of the durability of a holder | retainer by the revolution speed of each ball | bowl can be prevented. That is, in the case of a thrust ball bearing that supports a power roller, the revolution speed of each ball is likely to vary compared to a general thrust ball bearing. FIG. 12 shows a thrust ball bearing having a pitch circle diameter of about 50 to 60 mm and a diameter of each ball of about 12 to 18 mm. The circumferential position (azimuth angle) of each ball is the reference position (the revolution speed does not vary). The position is assumed to be deviated from the position when it is assumed to be constant. As is apparent from FIG. 12, the revolution speed of the balls constituting the thrust ball bearing increases or decreases depending on the circumferential position. And when the revolution speed of each said ball | bowl changes in this way, the rolling surface of each of these balls will interfere with the inner surface of the pocket of the said holder | retainer, and force will be added to this holder | retainer. Such a force is repeatedly applied to the cage as a bending stress, and damage such as a crack may occur in the cage with use over a long period of time. Therefore, the gap is regulated as described above in order to prevent such damage.

  When the gap is less than 0.2 mm, the repeated bending stress applied to the cage becomes excessive, and the amplitude of this stress tends to increase. Then, the progress of fatigue is accelerated (the fatigue life is shortened), and there is a possibility that the time until the damage such as the crack is reached is shortened. On the other hand, if the gap exceeds 0.5 mm, the variation of the cage may be excessive due to an excessively large gap between the rolling surface of each ball and the inner surface of the pocket. Such fluttering increases the collision force between the inner surfaces of the pockets and the rolling surfaces of the balls, which may easily cause damage such as cracks in the cage.

  1 to 4 show a first embodiment of the present invention corresponding to claims 1, 2, and 4. FIG. The feature of this embodiment is that both sides of the cage 7b in the axial direction of the cage 7b are devised by devising the positions of the spherical portions 19 and 19 constituting the inner surfaces 17 and 17 of the pockets 11a and 11b in the axial direction of the cage 7b. This is to prevent the surface and the side surfaces of the power roller 3 and the outer ring 8 that are raceways from slidingly contacting each other. Since the structure and operation of the other parts are the same as those of the conventional structure shown in FIGS. 8 to 11 and the like, the overlapping description will be omitted or simplified, and the following description will focus on the characteristic parts of this embodiment.

  The balls 6 and 6 constituting the thrust ball bearing 5 for supporting the power roller 3 are held by the cage 7b so as to be freely rollable. In the case of the present embodiment, the inner surfaces 17 and 17 of the pockets 11a and 11b of the cage 7b are constituted by a cylindrical surface portion 18 and a spherical surface portion 19. That is, the inner surface 17, 17 of each of the pockets 11a, 11b is smoothed at the intermediate portion between the cylindrical surface portion 18 and the spherical surface portion 19 that open on the opposite side surfaces with respect to the axial direction of the cage 7b. It is assumed that it consists of a series. And in the case of a present Example, the pocket 11b which provided the said spherical surface part 19 in one side (above FIG.1, 2, 4) regarding the axial direction of the said holder | retainer 7b among each said pocket 11a, 11b. 11b are the first pockets 20 and 20, and the pockets 11a and 11a provided on the other side (lower side in FIGS. 1, 2 and 4) are the second pockets 21 and 21, respectively. 20, 20 and the second pockets 21, 21 are alternately arranged in the circumferential direction of the cage 7b. More specifically, the total number of the pockets 11a and 11b of the cage 7b is eight, which is an even number, and the first pockets 20 and 20 and the second pockets 21 and 21 are alternately arranged one by one. Is arranged. Further, in a state where the centers of the balls 6 and 6 are aligned with the centers of the pockets 11a and 11b, the clearance between the inner surfaces of the pockets 11a and 11b and the rolling surfaces of the balls 6 and 6 is 0. The inner surface dimensions of the pockets 11a and 11b and the outer diameters of the balls 6 and 6 are regulated so as to be 2 to 0.5 mm.

According to this embodiment configured as described above, the distance between the axial side surfaces of the cage 7b and the side surfaces of the power roller 3 and the outer ring 8 can be made the same (the cage 7b is connected to the power roller 3 and the outer ring 8). The axial displacement amount of the cage 7b can be reduced.
That is, with respect to the axial direction of the cage 7b, the first pockets 20 and 20 and the second pockets 21 and 21 having the spherical portion 19 positioned opposite to each other with respect to the axial direction are related to the circumferential direction of the cage 7b. They are arranged alternately. Therefore, the spherical portions 19 of the first and second pockets 20 and 21 intersect with the central axis α (FIG. 2) of the retainers 7b at right angles, and the first and second pockets 20 , 21 can be arranged symmetrically with respect to a virtual plane (FIG. 2) passing through the center in the axial direction. When the cage 7b tends to be displaced in the other axial direction (upward in FIGS. 1, 2, and 4), the spherical portions 19 and 19 provided in the first pockets 20 and 20 The slidable contact with the rolling surfaces 6 and 6 prevents the cage 7b from being displaced further in the other axial direction. On the other hand, when the cage 7b tends to be displaced in one axial direction (downward in FIGS. 1, 2, and 4), the spherical portions 19 and 19 provided in the second pockets 21 and 21, respectively. Is in sliding contact with the rolling surfaces of the balls 6 and 6, thereby preventing the cage 7b from being displaced further in the axial direction. For this reason, the distance between the axial side surfaces of the cage 7b and the side surfaces of the power roller 3 and the outer ring 8 can be made substantially the same, and the axial displacement amount of the cage 7b can be reduced.

  As a result, both side surfaces of the cage 7b and the side surfaces of the power roller 3 and the outer ring 8 can be prevented from sliding, and it is also possible to prevent the lubricating oil from flowing between these side surfaces, thereby reducing transmission efficiency. In addition, it is possible to prevent poor lubrication and ensure the durability of the cage 7b, the power roller 3, and the outer ring 8. In addition, since the durability of the cage 7b can be ensured in this way, the cage 7b can be downsized. In addition, by reducing the size of the cage 7b and reducing the axial displacement of the cage 7b as described above, the distance between the power roller 3 and the outer ring 8 can also be reduced, and the thrust ball bearing 5 The power roller unit incorporating this thrust ball bearing 5 and thus the overall toroidal type continuously variable transmission can be reduced in size. In addition, since the lubricating oil can be easily circulated as described above, it is possible to reduce the size of the pump for feeding this lubricating oil and to reduce the amount of necessary lubricating oil. The transmission efficiency of the toroidal continuously variable transmission can be improved. Further, since the lubrication state can be improved, the durability of the entire apparatus can be ensured.

  Further, as described above, with the centers of the balls 6 and 6 aligned with the centers of the pockets 11a and 11b, between the inner surfaces of the pockets 11a and 11b and the rolling surfaces of the balls 6 and 6, respectively. The gap is regulated to be 0.2 to 0.5 mm. For this reason, it is possible to prevent a decrease in durability of the cage 7b due to variations in the revolution speed of the balls 6 and 6. That is, when the gap is less than 0.2 mm, as described above, the repeated bending stress applied to the cage 7b becomes excessive, and the amplitude of this stress may increase. In addition, the progress of fatigue is accelerated (the fatigue life is shortened), and there is a possibility that the time until damage such as a crack is shortened. On the other hand, when the gap exceeds 0.5 mm, the flutter of the cage 7b is excessive due to an excessively large gap between the rolling surfaces of the balls 6 and 6 and the inner surfaces of the pockets 11a and 11b. There is a possibility. Such fluttering can increase the collision force between the inner surfaces of the pockets 11a and 11b and the rolling surfaces of the balls 6 and 6, and can easily cause damage such as cracks in the cage 7b. There is sex. On the other hand, in the case of the present embodiment, since the gap is restricted to 0.2 to 0.5 mm as described above, such inconvenience is prevented and the durability of the cage 7b is ensured. it can.

FIG. 5 shows Embodiment 2 of the present invention corresponding to claims 1, 2 and 4. In this embodiment, the total number of the pockets 11a and 11b of the cage 4b is nine, which is an odd number. Along with this, one portion where two second pockets 21 and 21 are continuous is included.
Other configurations and operations are the same as those of the first embodiment described above, and thus redundant description is omitted.

FIG. 6 shows Embodiment 3 of the present invention corresponding to claims 1, 3 and 4. In the case of the present embodiment, a plurality of first pockets 20 and 20 and second pockets 21 and 21 are alternately arranged in the circumferential direction of the cage 7b. More specifically, the total number of the pockets 11a and 11b of the cage 7b is 8 which is a multiple of 4, and the first pockets 20 and 20 are connected in series, and the second pocket A set of two consecutive 21 and 21 is alternately arranged.
In the case of this embodiment, even if the force applied in the axial direction of the cage 7b becomes non-uniform due to local application in the circumferential direction of the cage 7b, the shaft of the cage 7b It is possible to prevent the balance of directions from being easily lost, and to prevent the side surfaces in the axial direction of the cage 7b from slidingly contacting the side surfaces of the power roller 3 and the outer ring 8 (see FIG. 1).
That is, even when a force is locally applied to the cage 7b, the force applied locally in this way is a group of a plurality of first pockets 20 and 20 arranged in succession, or a second pocket 21, Can be supported by 21 groups. Therefore, compared to the case where the first pockets 20 and 20 and the second pockets 21 and 21 are alternately arranged one by one, the allowable amount of force applied locally as described above can be increased, and the shaft of the cage 7b can be increased. The amount of directional displacement can be made smaller.
Other configurations and operations are the same as those of the first and second embodiments described above, and thus redundant description is omitted.

  FIG. 7 shows a fourth embodiment of the present invention corresponding to claims 1, 3 and 4. In the case of the present embodiment, the total number of the pockets 11a and 11b of the cage 7b is nine, and the first pockets 20 and 20 and the second pockets 21 and 21 are alternately two by two, and Each of the three parts is arranged including one place. In the case of this embodiment as well, similarly to the third embodiment described above, even when the axial force applied to the cage 7b becomes non-uniform in the circumferential direction of the cage 7b, the cage 7b. Can be prevented from slidingly contacting the side surfaces of the power roller 3 and the outer ring 8 (see FIG. 1).

  In the present embodiment, since the total number of the pockets 11a and 11b is not a multiple of 4, one set including two first pockets 20 and 20 and two second pockets 21 and 21 are combined. 2 sets and 3 sets of the first pockets 20 and 20 (or the second pockets 21 and 21) are provided. That is, the first pockets 20 and 20 and the second pockets 21 and 21 are grouped in a state in which two or three continuous in any part, and the groups are alternately arranged (first pockets 20 and 20 Or a portion where only one second pocket 21, 21 exists. If comprised in this way, the first pockets 20 and 20 or the second pockets 21 and 21 arranged continuously can support the force applied locally in the axial direction of the cage 7b. Other configurations and operations are the same as those of the third embodiment described above, and thus redundant description is omitted.

The fragmentary sectional view which shows Example 1 of this invention. The fragmentary sectional view which takes out and shows a holder | retainer and a ball. The top view of a holder | retainer. AA sectional drawing of FIG. The figure similar to FIG. 3 which shows Example 2 of this invention. The figure similar to FIG. 3 which shows the same Example 3. FIG. The figure similar to FIG. 3 which shows the same Example 4. FIG. Sectional drawing which shows an example of a conventional structure. Sectional drawing which shows another example of a power roller unit. The top view of a holder | retainer. BB sectional drawing of FIG. The diagram for demonstrating the dispersion | variation in the revolution speed of the ball hold | maintained at the holder | retainer.

Explanation of symbols

DESCRIPTION OF SYMBOLS 1 Input side disk 2 Output side disk 3 Power roller 4 Trunnion 5 Thrust ball bearing 6 Ball 7, 7a, 7b Cage 8 Outer ring 9 Inner ring raceway 10 Outer ring raceway 11, 11a Pocket 12 Thrust needle bearing 13 Support shaft 14 Pivot shaft 15 Oil supply hole 16 Concave groove 17 Inner surface 18 Cylindrical surface portion 19 Spherical surface portion 20 First pocket 21 Second pocket

Claims (4)

  Each of the first and second discs supported concentrically so as to be freely rotatable relative to each other, a plurality of power rollers sandwiched between these discs, and each of these power rollers being supported rotatably. Provided between each trunnion and each power roller, each supporting a load applied to each of these power rollers. A plurality of thrust ball bearings, and each of these thrust ball bearings includes a plurality of balls and an annular cage that holds each of these balls in a freely rolling manner. , Formed in a state of penetrating both sides in the axial direction, and provided with a plurality of pockets that hold each of the balls one by one so as to roll freely, and the inner surface of each of these pockets, With respect to the axial direction of the cage, in each of the toroidal type continuously variable transmissions, each of which is formed by smoothly connecting a cylindrical surface portion and a spherical surface portion that open to opposite side surfaces at the intermediate portion. The pocket is composed of a first pocket provided on one side with respect to the axial direction of the cage, and a second pocket provided on the other side, the first pocket and the second pocket, A toroidal continuously variable transmission, characterized in that the cage is alternately arranged in the circumferential direction.   The toroidal continuously variable transmission according to claim 1, wherein one first pocket and one second pocket are alternately arranged in the circumferential direction of the cage.   The toroidal continuously variable transmission according to claim 1, wherein a set of a plurality of first pockets or second pockets is alternately arranged in the circumferential direction of the cage. With the center of each ball and the center of each pocket coinciding, the minimum gap between the inner surface of each pocket and the rolling surface of each ball in the circumferential direction of the cage is 0.2-0. The toroidal continuously variable transmission according to any one of claims 1 to 3, which is set to 0.5 mm.

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