JP4662303B2 - Toroidal continuously variable transmission - Google Patents

Description

  The present invention relates to a toroidal continuously variable transmission that can be used for transmissions of automobiles and various industrial machines.

  As a transmission for an automobile, a toroidal type continuously variable transmission schematically shown in FIGS. 18 and 19 is known. In this toroidal-type continuously variable transmission, an input side disk 2 is supported concentrically with the input shaft 1, and an output side disk 4 is fixed to an end of an output shaft 3 arranged concentrically with the input shaft 1. On the inner side of the casing containing the toroidal-type continuously variable transmission, trunnions 6 and 6 that swing about pivots 5 and 5 that are twisted with respect to the input shaft 1 and the output shaft 3 are provided.

These trunnions 6 and 6 are provided with pivots 5 and 5 on the outer side surfaces of both ends. In addition, the base end portions of the displacement shafts 7 and 7 are supported at the intermediate portions of the trunnions 6 and 6, and by swinging the trunnions 6 and 6 about the pivot shafts 5 and 5, The inclination angle can be adjusted freely. Power rollers 8 and 8 are rotatably supported around the displacement shafts 7 and 7 supported by the trunnions 6 and 6, respectively. The power rollers 8 are sandwiched between the inner surfaces 2a and 4a of both the input and output disks 2 and 4.
Inner side surfaces 2a and 4a of the input side and output side discs 2 and 4 facing each other have a concave surface obtained by rotating a circular arc centered on the pivot 5, respectively. And the peripheral surfaces 8a and 8a of each power roller 8 and 8 formed in the spherical convex surface are made to contact | abut to the said inner surface 2a and 4a.

  A loading cam type pressing device 9 is provided between the input shaft 1 and the input side disc 2, and the input side disc 2 is elastically pressed toward the output side disc 4 by the pressing device 9. ing. The pressing device 9 includes a cam plate 10 that rotates together with the input shaft 1 and a plurality of (for example, four) rollers 12 and 12 held by a cage 11. A cam surface 13 that is a concavo-convex surface extending in the circumferential direction is formed on one side surface (the left side surface in FIGS. 5 to 6) of the cam plate 10, and the outer side surface (the right side surface in FIG. 18) of the input side disk 2. In addition, a similar cam surface 14 is formed. A plurality of rollers 12 and 12 are supported so as to be rotatable about the radial axis with respect to the center of the input shaft 1.

  When the toroidal-type continuously variable transmission configured as described above is used, when the cam plate 10 rotates with the rotation of the input shaft 1, the plurality of rollers 12, 12 are moved by the cam surface 13 to the input side disk 2. It is pressed by the cam surface 14 formed on the outer surface. As a result, the input side disk 2 is pressed against the plurality of power rollers 8 and 8 and at the same time, based on the pressing of the pair of cam surfaces 13 and 14 and the plurality of rollers 12 and 12, the input side disk 2 2 rotates. The rotation of the input side disk 2 is transmitted to the output side disk 4 via the plurality of power rollers 8, 8, and the output shaft 3 fixed to the output side disk 4 rotates.

  In order to change the rotational speed ratio (transmission ratio) between the input shaft 1 and the output shaft 3, first, when decelerating between the input shaft 1 and the output shaft 3, each trunnion is centered on the pivot shafts 5 and 5. 6 and 6 are swung in a predetermined direction. Then, as shown in FIG. 18, the peripheral surfaces 8a and 8a of the power rollers 8 and 8 are respectively formed on a portion near the center of the inner surface 2a of the input side disk 2 and a portion near the outer periphery of the inner surface 4a of the output side disk 4. The displacement shafts 7 and 7 are inclined so as to contact each other.

On the contrary, when the speed is increased, the trunnions 6 and 6 are swung in the opposite directions around the pivot shafts 5 and 5. Then, as shown in FIG. 19, the peripheral surfaces 8a and 8a of the power rollers 8 and 8 are formed on the outer peripheral portion of the inner side surface 2a of the input side disk 2 and the central portion of the inner side surface 4a of the output side disc 4, These displacement shafts 7 and 7 are inclined so as to contact each other. If the inclination angle of each of the displacement shafts 7 and 7 is set intermediate between those shown in FIGS. 18 and 19, an intermediate gear ratio can be obtained between the input shaft 1 and the output shaft 3.
Incidentally, as a structure in which the trunnion 6 rotatably supports the power roller 8, for example, a structure described in Patent Document 1 is known.

  In this structure, as shown in FIG. 20, the displacement shaft 7 is supported in a circular hole 23 formed in the intermediate portion of the trunnion 6. The displacement shaft 7 includes a support shaft portion 21 and a pivot shaft portion 22 that are parallel to each other and eccentric. Of these, the support shaft portion 21 is rotatably supported inside the circular hole 23 via a radial needle bearing 24. Further, the power roller 8 is rotatably supported around the pivot shaft portion 22 via a radial needle bearing 25 that supports the power roller 8.

  Between the outer surface (large end surface) of the power roller 8 and the intermediate inner surface 40 of the trunnion 6, a thrust ball bearing 26 for supporting the power roller 8 and the outer ring in order from the outer surface side of the power roller 8. A thrust needle bearing 27 is provided for supporting a thrust load applied to 30. The thrust ball bearing 26 supports the rotation of the power roller 8 while supporting a load in the thrust direction applied to the power roller 8. The ball 29 and an annular cage that holds the ball 29 in a rollable manner. 28 and an annular outer ring 30 that is a thrust raceway ring. The inner ring raceway of the thrust ball bearing 26 is formed on the outer side surface of the power roller 8, and the outer ring raceway is formed on the inner side surface of the outer ring 30.

  The thrust needle bearing 27 includes a race 31, a cage 32, and a needle 33. The race 31 and the cage 32 are combined so as to be slightly displaceable in the rotational direction. The thrust needle bearing 27 is disposed between the intermediate inner surface 40 and the outer surface of the outer ring 30 with the race 31 in contact with the intermediate inner surface 40 of the trunnion 6. Such a thrust needle bearing 27 allows the pivot shaft 22 and the outer ring 30 to swing around the support shaft 21 while supporting a thrust load applied from the power roller 8 to the outer ring 30.

  A drive rod 36 is coupled to one end of each trunnion 6, and a drive piston (not shown) is fixed to the outer peripheral surface of the intermediate portion of the drive rod 36. The drive piston is oil-tightly fitted in the drive cylinder (not shown).

  FIG. 21 shows the intermediate inner surface 40 of the trunnion 6 with the thrust needle bearing 27 attached to the surface 40 removed. On the intermediate inner side surface 40 of the trunnion 6, an opening of an oil supply passage 39 provided inside the trunnion 6 is opened near the circular hole 23, and the space between the intermediate inner side surface 40 and the race 31 in contact therewith is formed. The oil supply passage 39 is an oil passage for feeding lubricating oil to the radial needle bearing 25 and the thrust ball bearing 26 that support the power roller 8.

  Here, on the outer peripheral side of the intermediate inner surface 40 of the trunnion 6, race grooves 50, 52 and cage grooves 54, 56 are formed in a substantially arc shape on the outer peripheral side of the race grooves 50, 52, respectively. The race grooves 50 and 52 surround and hold the outer peripheral surface of the race 31 of the thrust needle bearing 27, and the cage grooves 54 and 56 surround and hold the outer peripheral surface of the cage 32.

JP 09-317838 A

  By the way, the machining of the race grooves 50 and 52 and the cage grooves 54 and 56 on the intermediate inner surface 40 of the trunnion 6 is usually performed by milling. Therefore, burrs are likely to occur at the corners and corners of each groove by milling. If this burr enters an oil passage provided between the intermediate inner surface 40 and the race 31, the radial needle bearing 25 and the thrust ball bearing 26 may be damaged early. For this reason, deburring must be carefully performed when the race grooves 50 and 52 and the cage grooves 54 and 56 are processed, and the manufacturing cost of the trunnion 6 increases.

  Further, the race grooves 50 and 52 and the cage grooves 54 and 56 are formed so as to have a step in the swing (swinging) direction of the power roller 8, and the step is cracked by the thrust load repeatedly applied. May occur. Therefore, the size of the trunnion must be increased in order to maintain a sufficient strength against the thrust load repeatedly applied, which also hinders the downsizing and increasing the capacity of the toroidal continuously variable transmission.

  The present invention has been made in view of the above circumstances, and it is possible to manufacture a trunnion by providing a structure that does not have a thrust bearing race and a groove for holding a cage on the inner surface of the trunnion on which the thrust bearing is disposed. An object of the present invention is to provide a toroidal type continuously variable transmission capable of reducing cost and improving trunnion strength.

In order to achieve the above object, the toroidal continuously variable transmission according to claim 1 is configured such that the input side disk and the output are supported concentrically and rotatably with the inner surfaces facing each other. A side disc, a trunnion that swings about a pivot that is twisted with respect to the center axis of the input side disc and the output side disc, and a support shaft portion and a pivot shaft portion that are eccentric to each other. A support shaft portion is rotatably supported by the trunnion, and a pivot shaft is protruded from the inner surface of the trunnion, and is rotatably supported around the pivot shaft portion via a rolling bearing. in the state, arranged between the input side disks and a power roller which is sandwiched between the inner faces of the output side disk, the outer surface and the inner surface of the trunnion of the outer ring is a scan last bearing ring Is, while supporting thrust-direction load that applied to the power roller from the outer ring, and a thrust bearing which allows the displacement of the outer ring relative to the trunnion, and an oil supply passage provided inside the trunnion, the oil supply passage in the toroidal type continuously variable transmission that is opened in the inner surface of said trunnion, said inner surface of said trunnion and flat Tanmen shape, between the outer surface of the inner surface the outer ring, held by the outer ring In this state, the thrust bearing is provided.

  In the toroidal type continuously variable transmission according to claim 1, the thrust bearing is not held on the inner side surface of the trunnion but is held by the outer ring, and the race of the thrust bearing and the cage are held on the inner side surface of the trunnion. Since the groove to be formed is not formed, the manufacturing cost of the trunnion can be reduced and the strength of the trunnion can be improved.

  According to a second aspect of the present invention, the toroidal continuously variable transmission according to the first aspect of the present invention is characterized in that the thrust bearing is disposed on the inner surface side of the trunnion and a retainer that rotatably holds a rolling element. The retainer extends from an outer diameter portion to the outer ring side, and a hook portion that is held on the outer peripheral surface of the outer ring, and extends from the outer diameter portion to the race side. And a collar portion that holds the outer peripheral surface of the race.

  In the second aspect of the invention, the flange extending from the outer diameter portion of the cage to the outer ring side is held on the outer peripheral surface of the outer ring, and the flange portion extending from the outer diameter portion of the cage to the race side is provided. Since the outer peripheral surface of the race is held, the cage and the race are held by the outer ring.

  According to a third aspect of the present invention, the toroidal continuously variable transmission according to the second aspect of the present invention is characterized in that the race is rotatably provided on the support shaft portion of the displacement shaft. .

  According to the third aspect of the present invention, the displacement of the race relative to the outer ring when the power roller swings is prevented.

  According to a fourth aspect of the present invention, there is provided the toroidal continuously variable transmission according to the third aspect of the present invention, wherein the cage is rotatably provided on the support shaft portion of the displacement shaft, and the cage An extension line of the rotating shaft of the rolling element that is rotatably held by the rotating member passes through the center of rotation of the support shaft portion.

  According to the fourth aspect of the present invention, no slip occurs between the rolling element and the outer ring when the power roller swings, and the durability of the thrust bearing is improved.

Furthermore, the toroidal type continuously variable transmission according to claim 5 is the invention according to claim 1, wherein the thrust bearing is provided on the inner surface side of the trunnion and a retainer that rotatably holds a rolling element. With an arranged annular race,
The retainer extends from an outer diameter portion to the outer ring side, extends to an outer peripheral side collar portion held on the outer peripheral surface of the outer ring, and extends from an inner diameter portion to the race side, and And an inner flange portion that holds the surface.

  In the fifth aspect of the present invention, the outer peripheral side flange of the cage is held by the outer peripheral surface of the outer ring, and the inner peripheral side flange of the retainer holds the inner peripheral surface of the race. Therefore, the cage and the race are held by the outer ring.

  According to the toroidal continuously variable transmission of the present invention, it is not necessary to form a thrust bearing race and a groove for holding the retainer on the inner surface of the trunnion on which the thrust bearing is disposed. can do. In addition, since the race and cage grooves are not provided on the inner side surface of the trunnion, there is no stepped portion due to the grooves, so that the strength of the trunnion can be improved, thereby reducing the size and capacity of the trunnion. Can be planned.

  Embodiments of a toroidal type continuously variable transmission according to the present invention will be described below with reference to the drawings. The description of the same components as those shown in FIGS. 20 and 21 is omitted or simplified.

1 to 3 show a structure in which the trunnion 6 according to the first embodiment supports the power roller 8 rotatably.
In the present embodiment, the race groove and the cage groove are not formed on the outer peripheral side of the intermediate inner surface 40 of the trunnion 6, and the intermediate inner surface 40 has a flat surface shape. Between the side surfaces, a thrust needle bearing 58 having an outer ring is disposed.
The thrust needle bearing 58 includes a cage 60, a disk-shaped race 62, and a needle 64 that is rotatably held by the cage 60.

The retainer 60 is formed by press-molding a metal plate material. As shown in FIG. 2, the retainer 60 is formed with an annular main body 66 and a predetermined distance from the main body 66, and rotates the needle 64. A plurality of pockets 68 that are freely held, and a collar portion 70 that extends in the axial direction on the entire circumference of the outermost diameter portion of the main body 66 are provided.
The flange portion 70 is formed from the outermost diameter portion of the main body 66 toward one side in the axial direction, and the outer ring side flange portion 72 is formed from the outermost diameter portion of the main body 66 toward the other side in the axial direction. The outer ring side collar part 72 is formed over the entire circumference while expanding the diameter toward one side in the axial direction, and the race side collar part 74 is formed in the axial direction. It is formed over the entire circumference while extending in a cylindrical shape toward the other side.

  In the thrust needle bearing 58, the cage 60 in which the needle 64 is inserted into the pocket 68 is disposed between the intermediate inner surface 40 and the outer surface of the outer ring 30, and the outer ring 30 is supported by the outer ring side flange 72 of the cage 60. The trunnion 6 side outer peripheral surface is surrounded, and the outer peripheral surface of the race 62 arranged in contact with the intermediate inner side surface 40 by the race side flange 74 is surrounded.

  In the present embodiment, since the outer ring side flange 72 of the cage 60 surrounds the outer peripheral surface of the outer ring 30, the cage 60 is held by the outer ring 30. Further, since the race side flange 74 surrounds the outer peripheral surface of the race 62, the race 62 is held by the outer ring 30 via the cage 60. Thus, the retainer 60 and the race 62 of the thrust needle bearing 58 are held with the outer ring.

  Here, when the power roller 8 swings, the thrust needle bearing 58 swings by half of the swing amount of the power roller 8. Therefore, when the power roller 8 swings between the outer ring side flange 72 and the outer peripheral surface of the outer ring 30 and between the race side flange 74 and the outer peripheral surface of the race 62, the outer ring side flange 72 and A clearance is provided so as not to interfere with the outer ring 30 and to prevent the race side flange 74 and the race 62 from interfering with each other.

In the present embodiment, a race groove and a cage groove are not formed on the intermediate inner surface 40 of the trunnion 6, and an outer ring is provided around the outermost diameter portion of the cage 60 of the thrust needle bearing 58. Since the collar part 70 including the side collar part 72 and the race side collar part 74 is provided and the retainer 60 and the race 62 are held with an outer ring, the manufacturing cost of the trunnion can be reduced.
In addition, since the race groove and the cage groove are not formed on the outer peripheral side of the intermediate inner side surface 40 of the trunnion 6 and a step due to these grooves does not occur in the swing direction of the power roller 8, the strength of the trunnion 6 is increased. It is possible to provide a toroidal continuously variable transmission that is sufficiently secured, and therefore has a reduced size and increased capacity.

Next, FIGS. 4 to 7 show a second embodiment according to the present invention.
Also in this embodiment, the groove for race and the groove for cage are not formed on the outer peripheral side of the intermediate inner surface 40 of the trunnion 6, and the intermediate inner surface 40 has a flat surface shape. Between the side surfaces, a thrust needle bearing 58 having an outer ring is disposed.

As shown in FIG. 5, the retainer 80 constituting the thrust needle bearing 58 includes an annular main body 66, a plurality of pockets 68 formed at predetermined intervals in the main body 66, and an outermost body of the main body 66. And a collar portion 82 extending in the axial direction around the entire circumference of the diameter portion.
The flange portion 82 is formed from the outermost diameter portion of the main body 66 toward one side in the axial direction, and the outer ring side flange portion 84 is formed from the outermost diameter portion of the main body 66 toward the other side in the axial direction. The race side flanges 86 are formed while alternately extending in the circumferential direction in a pawl shape.

The cage 80 is also formed by press-molding a metal plate material.
The cage 80 disposed between the intermediate inner side surface 40 and the outer side surface of the outer ring 30 intermittently surrounds the outer peripheral surface of the outer ring 30 on the trunnion 6 side with the outer ring side flange portion 84, and the race inner flange portion 86 with the intermediate inner surface. The outer peripheral surface of the race 62 arranged in contact with the side surface 40 is intermittently surrounded. Since the outer ring side flange 84 of the cage 80 surrounds the outer peripheral surface of the outer ring 30, the cage 80 is held by the outer ring 30. In addition, since the race side flange 86 surrounds the outer peripheral surface of the race 62, the race 62 is held by the outer ring 30 via the cage 80. Thus, the retainer 80 and the race 62 of the thrust needle bearing 58 are held with an outer ring.

  Here, when the power roller 8 swings, the thrust needle bearing 58 swings by half of the swing amount of the power roller 8, so that the race side flange 86 is between the outer ring side flange 84 and the outer peripheral surface of the outer ring 30. When the power roller 8 swings, the outer ring side collar 72 and the outer ring 30 do not interfere with each other and the race side collar 74 and the race 62 do not interfere with each other. The gap is provided.

  Even in the present embodiment, the same effects as those of the first embodiment can be obtained, and the collar portion 82 of the retainer 80 has the outer ring side collar portion 84 and the race side collar portion 86 in the circumferential direction. Since the protrusion amount of the collar portion from the main body 66 is reduced as compared with the cage 60 of the first embodiment, the weight of the cage 80 can be reduced. Can do.

Next, FIGS. 8 and 9 show a third embodiment according to the present invention.
Also in this embodiment, the groove for race and the groove for cage are not formed on the outer peripheral side of the intermediate inner surface 40 of the trunnion 6, and the intermediate inner surface 40 has a flat surface shape. Between the side surfaces, a thrust needle bearing 58 having an outer ring is disposed.

  As shown in FIG. 9, the retainer 90 constituting the thrust needle bearing 58 includes an annular main body 66, a plurality of pockets 68 formed at predetermined intervals in the main body 66, and the outermost body of the main body 66. An outer peripheral side flange 92 formed extending in the axial direction on the entire circumference of the diameter portion, and an inner peripheral side flange formed extending in the axial direction on the entire circumference of the innermost diameter portion of the main body 66 94.

The outer peripheral side flange portion 92 is formed over the entire circumference while increasing the diameter from the outermost diameter portion of the main body 66 toward one side in the axial direction. The inner peripheral side flange 94 is formed over the entire circumference while extending in a cylindrical shape from the innermost diameter portion of the main body 66 toward the other side in the axial direction.
The cage 90 disposed between the intermediate inner surface 40 and the outer surface of the outer ring 30 surrounds the outer peripheral surface of the outer ring 30 on the trunnion 6 side with the outer peripheral side flange 92, and the inner peripheral side flange 94 is the intermediate inner surface 40. Is opposed to the inner peripheral surface of the race 62 arranged in contact with the inner surface. Since the outer peripheral side flange 92 of the retainer 90 surrounds the outer peripheral surface of the outer ring 30, the retainer 90 is retained by the outer ring 30 while restraining radial movement. Further, since the inner peripheral flange 94 faces the inner peripheral surface of the race 62, the race 62 is held while the radial movement is restricted by the outer ring 30 via the retainer 90. Thus, the retainer 90 and the race 62 of the thrust needle bearing 58 are held with an outer ring.

  Here, when the power roller 8 swings, the thrust needle bearing 58 swings by half of the swing amount of the power roller 8, so that the inner peripheral flange is between the outer peripheral flange 92 and the outer peripheral surface of the outer ring 30. 94 and the inner peripheral surface of the race 62, when the power roller 8 swings, the outer peripheral side flange 92 and the outer ring 30 do not interfere with each other, and the inner peripheral side flange 94 and the race 62 are A gap that does not interfere is provided.

  Even in the present embodiment, the race groove and the cage groove are not formed on the outer peripheral side of the intermediate inner surface 40 of the trunnion 6, and the cage 90 of the thrust needle bearing 58 is the outermost diameter of the main body 66. The outer peripheral side collar part 92 formed extending in the axial direction around the entire circumference of the part, and the inner circumferential side collar part 94 formed extending in the axial direction along the entire circumference of the innermost diameter part of the main body 66. Therefore, it is possible to reduce the production time and production cost compared to the conventional production of trunnions, and the strength of the trunnion 6 is sufficiently secured to achieve downsizing and high capacity. A toroidal continuously variable transmission can be provided.

Next, FIG. 10 shows a fourth embodiment according to the present invention.
Also in this embodiment, the groove for race and the groove for cage are not formed on the outer peripheral side of the intermediate inner surface 40 of the trunnion 6, and the intermediate inner surface 40 has a flat surface shape. Between the side surfaces, a thrust needle bearing 58 having an outer ring is disposed.

  The retainer 96 constituting the thrust needle bearing 58 has an outer periphery formed in a pawl shape toward the one side in the axial direction with a predetermined interval from the outermost diameter portion of the main body 66 not shown in FIG. A side flange 98 and an inner periphery side flange 100 formed in a pawl shape toward the other side in the axial direction with a predetermined interval in the circumferential direction from the innermost diameter portion of the main body 66 are provided.

The retainer 96 of the present embodiment also surrounds the outer peripheral surface of the outer ring 30 on the trunnion 6 side with the outer peripheral side flange portion 98, and the inner peripheral surface flange portion 100 is disposed on the inner peripheral surface of the race 62 disposed on the intermediate inner surface 40. opposite. For this reason, the retainer 96 and the race 62 of the present embodiment are also held with an outer ring.
Further, when the power roller 8 swings, the thrust needle bearing 58 swings by half of the swing amount of the power roller 8, so that the inner peripheral flange 100 is between the outer peripheral flange 98 and the outer peripheral surface of the outer ring 30. And the inner peripheral surface of the race 62, when the power roller 8 swings, the outer peripheral side flange portion 98 and the outer ring 30 do not interfere with each other, and the inner peripheral side flange portion 100 and the race 62 interfere with each other. There is a gap that does not.
Therefore, even in the present embodiment, the same effects as those of the third embodiment can be obtained, and the outer peripheral side flange 98 and the inner peripheral side flange 100 of the retainer 96 are arranged around the periphery of the main body 66. Since it is formed at predetermined intervals in the direction, the weight of the cage 96 can be reduced compared to the cage 90 of the third embodiment.

Next, FIG. 11 and FIG. 12 show a fifth embodiment according to the present invention.
A thrust needle bearing 58 according to the present embodiment includes the cage 60 shown in the first embodiment, the needle 64 rotatably held by the cage 60, and a disk-shaped race 102. ing.

  As shown in FIG. 12, the race 102 has an insertion hole 102 a having an inner diameter substantially the same as the outer diameter of the radial needle bearing 24 disposed on the outer periphery of the support shaft portion 21. Reference numeral 102 b denotes an oil hole that communicates with the oil supply passage 39. The race 102 is disposed in contact with the intermediate inner side surface 40 in a state where the radial needle bearing 24 is inserted into the insertion hole 102a. According to such a configuration, the race 102 is rotatably supported by the support shaft portion 21 via the radial needle bearing 24.

  By the way, when the power roller 8 swings between the outer ring side flange 72 and the outer peripheral surface of the outer ring 30, and between the race side flange 74 and the outer peripheral surface of the race 102, the outer ring side flange 72 and Since there is a gap that does not interfere with the outer ring 30 and does not interfere with the race side flange 74 and the race 102, the position of the race 102 may be greatly displaced with respect to the outer ring 30. However, in the present embodiment, since the race 102 is rotatably supported by the support shaft portion 21, it is possible to prevent the displacement of the race 102 with respect to the outer ring 30.

Next, FIG. 13 shows a sixth embodiment according to the present invention.
The thrust needle bearing 58 according to the present embodiment is the cage 80 shown in the second embodiment, the needle 64 rotatably held by the cage 80, and the fifth embodiment. And a race 102.

  In the present embodiment, when the power roller 8 swings between the outer ring side flange portion 84 and the outer peripheral surface of the outer ring 30 and between the race side flange portion 86 and the outer peripheral surface of the race 102. In this embodiment, the race 102 is supported by the support shaft portion so that the outer ring side collar portion 72 and the outer ring 30 do not interfere with each other and the race side collar portion 74 and the race 102 do not interfere with each other. 21, the position of the race 102 relative to the outer ring 30 can be prevented from being displaced.

Next, FIG. 14 and FIG. 15 show a seventh embodiment according to the present invention.
A thrust needle bearing 58 according to the present embodiment includes a cage 104, a needle 64 that is rotatably held by the cage 104, and a race 102 shown in the fifth embodiment.

As shown in FIG. 15, the cage 104 includes a disk-shaped main body 106 and a flange 70 having the same shape as that of the first embodiment on the entire outer periphery of the main body 106. Yes.
That is, the flange portion 70 is formed from the outermost diameter portion of the main body 106 toward one side in the axial direction, and the outer ring side flange portion 72 is formed from the outermost diameter portion of the main body 106 toward the other side in the axial direction. The outer ring side flange 72 is formed over the entire circumference while increasing the diameter toward one side in the axial direction. The race side flange 74 is While extending in a cylindrical shape toward the other side of the direction, it is formed over the entire circumference.
The main body 106 is formed with an insertion hole 108 having an inner diameter substantially the same as the outer diameter of the radial needle bearing 24 disposed on the outer periphery of the support shaft portion 21. A plurality of pockets 110 that rotatably hold the needle 64 are formed around the insertion hole 108 of the main body 106, and a central axis of these pockets 110 (an axis that coincides with the rotation center of the needle 64). The extension line is provided so as to pass through the center of the insertion hole 108. Reference numeral 112 denotes an oil hole that communicates with the oil supply passage 39.

  In the present embodiment, since the cage 104 and the race 102 are rotatably supported by the support shaft portion 21, the race side flange portion 74 is provided between the outer ring side flange portion 72 and the outer peripheral surface of the outer ring 30. And the outer peripheral surface of the race 102, when the power roller 8 swings, the outer ring side collar 72 and the outer ring 30 do not interfere with each other, and the race side collar 74 and the race 102 do not interfere with each other. Even if the gap is provided, the displacement of the race 102 with respect to the outer ring 30 can be prevented.

  Further, since the central axis of the pocket 110 provided in the cage 104 (the axis that coincides with the rotation center of the needle 64) passes through the center of the insertion hole 108, when the power roller 8 swings. Slip does not occur between the needle 64 and the outer ring 30, and the durability of the thrust needle bearing 58 can be improved.

Next, FIGS. 16 and 17 show an eighth embodiment according to the present invention.
The thrust needle bearing 58 according to the present embodiment includes a cage 114, a needle 64 that is rotatably held by the cage 114, and the race 102 shown in the fifth embodiment.

As shown in FIG. 17, the retainer 114 includes a disc-shaped main body 116, and an outer ring side collar portion 84 and a race side collar portion having the same shape as that of the second embodiment at the outermost diameter portion of the main body 116. 86 is formed.
That is, the outer ring side flange portion 84 is formed from the outermost diameter portion of the main body 116 toward one side in the axial direction, and the race side flange portion 86 is formed from the outermost diameter portion of the main body 116 in the other axial direction. The outer ring side flanges 84 and the race side flanges 86 are formed while alternately extending in the form of pawls in the circumferential direction.

  The main body 116 is formed with an insertion hole 118 having an inner diameter substantially the same as the outer diameter of the radial needle bearing 24 arranged on the outer periphery of the support shaft portion 21. A plurality of pockets 120 that rotatably hold the needle 64 are formed around the insertion hole 118 of the main body 116. The central axis of these pockets 120 (the axis that coincides with the rotation center of the needle 64). An extension line is provided so as to pass through the center of the insertion hole 118. Reference numeral 122 denotes an oil hole that communicates with the oil supply passage 39.

In the present embodiment, since the cage 114 and the race 102 are rotatably supported by the support shaft portion 21, the race side collar portion 86 is provided between the outer ring side collar portion 84 and the outer peripheral surface of the outer ring 30. When the power roller 8 swings between the outer race surface 102 and the race 102, the outer ring side collar 72 and the outer ring 30 do not interfere with each other, and the race side collar 86 and the race 102 do not interfere with each other. Even if the gap is provided, the displacement of the race 102 with respect to the outer ring 30 can be prevented.
Further, since the central axis of the pocket 120 provided in the cage 114 (the axis that coincides with the rotation center of the needle 64) passes through the center of the insertion hole 118, when the power roller 8 swings. Slip does not occur between the needle 64 and the outer ring 30, and the durability of the thrust needle bearing 58 can be improved.

  Note that the cages 60, 80, 90, 96, 104, and 114 shown in each of the above embodiments are formed by combining two or more metal plates, even if formed by a single metal plate. You may shape | mold.

  The present invention can be applied to various toroidal type continuously variable transmissions such as a single cavity type and a double cavity type.

It is principal part sectional drawing which shows 1st Embodiment concerning this invention. It is a perspective view which shows the holder | retainer used in 1st Embodiment based on this invention. It is a principal part enlarged view of 1st Embodiment which concerns on this invention. It is principal part sectional drawing which shows 2nd Embodiment concerning this invention. It is a perspective view which shows the holder | retainer used in 2nd Embodiment based on this invention. It is a principal part enlarged view of 2nd Embodiment which concerns on this invention. It is a principal part enlarged view of the other location of 2nd Embodiment which concerns on this invention. It is principal part sectional drawing which shows 3rd Embodiment based on this invention. It is a principal part enlarged view of 3rd Embodiment which concerns on this invention. It is principal part sectional drawing of 4th Embodiment based on this invention. It is principal part sectional drawing of 5th Embodiment concerning this invention. It is a figure which shows the race used in 5th Embodiment based on this invention. It is principal part sectional drawing of the 6th Embodiment which concerns on this invention. It is principal part sectional drawing of the 7th Embodiment which concerns on this invention. It is a figure which shows the holder | retainer used in 7th Embodiment based on this invention. It is principal part sectional drawing of 8th Embodiment which concerns on this invention. It is a figure which shows the holder | retainer used in 8th Embodiment based on this invention. It is a figure which shows the basic composition of the conventional toroidal type continuously variable transmission in the state at the time of maximum deceleration. It is a figure which shows the basic composition of the conventional toroidal type continuously variable transmission in the state at the time of maximum speed increase. It is a figure which shows the structure where the conventional trunnion supports a power roller rotatably. It is the figure which showed the shape of the inner surface of a trunnion.

Explanation of symbols

2 Input side disk 4 Output side disk 5 Pivot 6 Trunnion 7 Displacement shaft 8 Power roller 21 Support shaft part 22 Pivot shaft part 30 Outer ring 39 Oil supply passage 40 Intermediate inner side surface (inner side surface)
58 Thrust needle bearing 60, 80, 90, 96, 104, 114 Cage 62, 102 Race 64 Needle (rolling element)
66, 106, 116 Main body 68, 120 Pocket 70, 82 Ridge 72, 84 Outer ring side collar 74, 86 Race side collar 92, 98 Outer circumference side 94, 100 Inner circumference collar 102a, 108, 118 Insertion Hole

Claims (5)

With the inner side surfaces facing each other, the input side disk and output side disk supported concentrically and rotatably, and in a twisted position with respect to the center axis of these input side disk and output side disk A trunnion that swings around a pivot, and a support shaft and a pivot shaft that are eccentric to each other, of which the support shaft is rotatably supported by the trunnion, and the pivot shaft is supported by the trunnion. The displacement shaft protruded from the inner side surface, and is sandwiched between the inner side surfaces of the input side disk and the output side disk in a state of being rotatably supported around the pivot shaft part via a rolling bearing. and power rollers disposed between the outer surfaces of the outer ring is a scan last bearing ring and the inner surface of said trunnion, bearing a thrust direction load applied to the outer ring from said power roller One, a thrust bearing which allows the displacement of the outer ring relative to the trunnion, and an oil supply passage provided inside the trunnion, the toroidal and is opened to the oil supply passageway inside surface of said trunnion CVT In
And the inner surface of the flat Tanmen shape of the trunnion, toroidal-type continuously variable this and the inner surface between the outer surface of the outer ring, and wherein in a retained state to the provision of the thrust bearing by the outer ring transmission. The thrust bearing includes a cage that rotatably holds a rolling element, and a race that is disposed on the inner surface side of the trunnion.
The retainer extends from the outer diameter portion to the outer ring side and extends from the outer diameter portion to the race side by holding the outer periphery of the race. The toroidal-type continuously variable transmission according to claim 1, further comprising a flange portion.   3. The toroidal continuously variable transmission according to claim 2, wherein the race is rotatably provided on the support shaft portion of the displacement shaft.   The cage is rotatably provided on the support shaft portion of the displacement shaft, and an extension line of a rotating shaft of a rolling element rotatably held by the cage is a rotation center of the support shaft portion. The toroidal-type continuously variable transmission according to claim 3, wherein The thrust bearing includes a retainer that rotatably holds a rolling element, and an annular race disposed on the inner surface side of the trunnion,
The retainer extends from an outer diameter portion to the outer ring side, extends to an outer peripheral side collar portion held on the outer peripheral surface of the outer ring, and extends from an inner diameter portion to the race side, and The toroidal-type continuously variable transmission according to claim 1, further comprising a flange on the inner peripheral side that holds the surface.

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