JP4089081B2 - Toroidal continuously variable transmission - Google Patents

Description

[0001]
[Industrial application fields]
The toroidal type continuously variable transmission according to the present invention is used, for example, as a transmission unit for a transmission for an automobile or as a transmission for various industrial machines.
[0002]
[Prior art]
The use of a toroidal continuously variable transmission as schematically shown in FIGS. 6 to 7 has been studied as an automobile transmission. This toroidal-type continuously variable transmission supports an input side disk (first disk) 2 concentrically with the input shaft 1 as disclosed in, for example, Japanese Utility Model Laid-Open No. 62-71465. The output side disk (second disk) 4 is fixed to the end of the output shaft 3 arranged concentrically. Inside the casing containing the toroidal-type continuously variable transmission, there is no pivot that intersects the central axis of the input shaft 1 and the output shaft 3 but is in a twisted position that is perpendicular to the direction of the central axis. Trunnions 6 and 6 that swing about 5 and 5 are provided.
[0003]
Each of these trunnions 6 and 6 is provided with the pivots 5 and 5 on the outer side surfaces of both ends. Further, the intermediate portions of the trunnions 6 and 6 support the base end portions of the displacement shafts 7 and 7, and the trunnions 6 and 6 are swung around the pivot shafts 5 and 5. , 7 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 and 8 are sandwiched between the inner side surfaces 2a and 4a of the input side and output side disks 2 and 4, respectively. Each of these inner side surfaces 2a, 4a has a concave surface obtained by rotating an arc centered on the pivot 5 around the central axis of the disk 2, 4. 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.
[0004]
A loading cam type pressing device 9 is provided between the input shaft 1 and the input side disk 2, and the pressing device 9 elastically presses the input side disk 2 toward the output side disk 4. Yes. 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. On one side surface (left side surface in FIGS. 6 to 7 ) of the cam plate 10, a cam surface 13 that is an uneven surface extending in the circumferential direction is formed, and the outer surface of the input side disk 2 (right side in FIGS. 6 to 7 ) . The same cam surface 14 is also formed on the surface). The plurality of rollers 12 and 12 are supported so as to be rotatable about a radial axis with respect to the center of the input shaft 1.
[0005]
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 by 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 rotates. Then, the rotation of the input side disk 2 is transmitted to the output side disk 4 through the plurality of power rollers 8, 8, and the output shaft 3 fixed to the output side disk 4 rotates.
[0006]
When changing the rotational speed ratio (transmission ratio) between the input shaft 1 and the output shaft 3, and when first decelerating between the input shaft 1 and the output shaft 3, the pivots 5 and 5 are used as the centers. Each trunnion 6, 6 is swung in a predetermined direction. As shown in FIG. 6 , the peripheral surfaces 8 a and 8 a of the power rollers 8 and 8 are formed in a portion near the center of the inner side surface 2 a of the input side disk 2 and a portion near the outer periphery of the inner side surface 4 a of the output side disk 4. The displacement shafts 7 and 7 are inclined so as to contact each other.
[0007]
On the other hand, when increasing the speed, the trunnions 6 and 6 are swung in the opposite directions around the pivots 5 and 5. Then, as shown in FIG. 7 , 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 disc 2 and the central portion of the inner side surface 4a of the output side disc 4, respectively. The displacement shafts 7 and 7 are inclined so as to contact each other. If the inclination angles of these displacement shafts 7 and 7 are set in the middle between FIG . 6 and FIG. 7 , an intermediate gear ratio can be obtained between the input shaft 1 and the output shaft 3.
[0008]
8 to 9 show a more specific toroidal type continuously variable transmission described in the microfilm of Japanese Utility Model Application No. 63-69293 (Japanese Utility Model Laid-Open No. 1-173552). The input side disk 2 and the output side disk 4 are rotatably supported around needle-shaped input shafts 15 via needle bearings 16 and 16, respectively. Further, the cam plate 10 is spline-engaged with the outer peripheral surface of the end portion (left end portion in FIG. 8 ) of the input shaft 15 and the movement of the cam plate 10 in the direction away from the input side disk 2 is prevented by the flange portion 17. The cam plate 10 and the rollers 12, 12 rotate the input side disk 2 while pressing the input side disk 2 against the output side disk 4 based on the rotation of the input shaft 15. Is configured. An output gear 18 is coupled to the output side disk 4 by means of keys 19, 19, so that the output side disk 4 and the output gear 18 rotate in synchronization.
[0009]
Both ends of the pair of trunnions 6 and 6 are supported on the pair of support plates 20 and 20 so as to be swingable and displaceable in the axial direction (front and back direction in FIG . 8 , left and right direction in FIG. 9 ). The displacement shafts 7 and 7 are supported in the circular holes 23 and 23 formed in the intermediate portions of the trunnions 6 and 6. Each of these displacement shafts 7 and 7 has support shaft portions 21 and 21 and pivot shaft portions 22 and 22 that are parallel to each other and eccentric, respectively. Of these, the support shaft portions 21 and 21 are rotatably supported inside the circular holes 23 and 23 via radial needle bearings 24 and 24. Further, power rollers 8 and 8 are rotatably supported around the pivot shaft portions 22 and 22 via radial needle bearings 25 and 25 which are radial bearings for supporting the power rollers 8 and 8. is doing.
[0010]
The pair of displacement shafts 7 and 7 are provided at positions opposite to the input shaft 15 by 180 degrees. Further, the directions in which the pivot shafts 22 and 22 of the displacement shafts 7 and 7 are eccentric with respect to the support shafts 21 and 21 are the same with respect to the rotational directions of the input side and output side disks 2 and 4. It is set as the direction (the left-right reverse direction in FIG. 9 ). The eccentric direction is a direction substantially perpendicular to the direction in which the input shaft 15 is disposed. Accordingly, the power rollers 8 and 8 are supported so as to be slightly displaceable in the direction in which the input shaft 15 is disposed. As a result, the power rollers 8, 8 are displaced in the axial direction of the input shaft 15 (the left-right direction in FIG . 8 , the front-back direction in FIG. 9 ) due to variations in the dimensional accuracy of components, elastic deformation, and the like . Even if it becomes the tendency to do, this displacement can be absorbed, without applying excessive force to each component.
[0011]
Further, between the outer surface of each of the power rollers 8 and 8 and the inner surface of the intermediate portion of each of the trunnions 6 and 6, the power rollers 8 and 8 are sequentially applied from the outer surface side. Thrust ball bearings 26 and 26 which are thrust rolling bearings for supporting a thrust load, and thrust needle bearings 27 and 27 which are thrust bearings for supporting a thrust load applied to thrust outer rings 30 and 30 described below are provided. . Of these, the thrust ball bearings 26, 26 allow the power rollers 8, 8 to rotate while supporting a load in the thrust direction applied to the power rollers 8, 8. Such thrust ball bearings 26, 26 are a plurality of balls 29, 29, annular retainers 28, 28 for holding the balls 29, 29 in a rollable manner, and thrust bearing rings. It is composed of annular thrust outer rings 30 and 30 (power roller thrust bearing outer rings). The thrust inner ring raceways 31 and 31 of the thrust ball bearings 26 and 26 are formed on the outer side surfaces of the power rollers 8 and 8, and the thrust outer ring raceways 32 and 32 are formed on the inner side surfaces of the thrust outer rings 30 and 30, respectively. Yes.
[0012]
Each of the thrust needle bearings 27 and 27 includes a race 33, a cage 34, and needles 35 and 35. Of these, the race 33 and the cage 34 are combined so as to be slightly displaceable in the rotational direction. Such thrust needle bearings 27, 27 are formed between the inner side surface and the outer side surface of the thrust outer ring 30, 30 with the races 33, 33 in contact with the inner side surface of the trunnions 6, 6. Sandwiched between them. Such thrust needle bearings 27 and 27 support the thrust shafts 22 and 22 and the thrust outer ring 30 while supporting the thrust load applied to the thrust outer rings 30 and 30 from the power rollers 8 and 8. 30 is allowed to swing around the support shaft portions 21, 21.
[0013]
Further, driving rods 36 and 36 are coupled to one end portions (left end portions in FIG. 9 ) of the trunnions 6 and 6, respectively, and driving pistons 37 and 37 are fixed to the outer peripheral surface of the intermediate portion of the driving rods 36 and 36, respectively. Has been established. The drive pistons 37 and 37 are oil-tightly fitted in the drive cylinders 42 and 42, respectively.
[0014]
In the case of the toroidal type continuously variable transmission configured as described above, the rotation of the input shaft 15 is transmitted to the input side disk 2 via the pressing device 9. Then, the rotation of the input side disk 2 is transmitted to the output side disk 4 through a pair of power rollers 8, 8, and the rotation of the output side disk 4 is taken out from the output gear 18.
[0015]
When changing the rotation speed ratio between the input shaft 15 and the output gear 18, the pair of drive pistons 37, 37 are displaced in opposite directions. As the drive pistons 37 and 37 are displaced, the pair of trunnions 6 and 6 are displaced in the opposite directions . For example, the lower power roller 8 in FIG. The power rollers 8 are displaced to the left in the figure. As a result, the direction of the tangential force acting on the contact portion between the peripheral surfaces 8a, 8a of the power rollers 8, 8 and the inner side surfaces 2a, 4a of the input side disk 2 and the output side disk 4 changes. To do. The trunnions 6 and 6 swing in opposite directions around the pivots 5 and 5 pivotally supported by the support plates 20 and 20 in accordance with the change in the direction of the force. As a result, as shown in FIGS. 6 to 7 described above, the contact position between the peripheral surfaces 8a and 8a of the power rollers 8 and 8 and the inner surfaces 2a and 4a changes, and the input shaft 15 and The rotational speed ratio with the output gear 18 changes.
[0016]
When the rotational force is transmitted between the input shaft 15 and the output gear 18 in this way, the power rollers 8 and 8 are connected to the input shaft 15 based on the elastic deformation of the constituent members. The displacement shafts 7 and 7 which are displaced in the axial direction and pivotally support the power rollers 8 and 8 are slightly rotated around the support shaft portions 21 and 21. As a result of this rotation, the outer side surfaces of the thrust outer rings 30 and 30 of the thrust ball bearings 26 and 26 and the inner side surfaces of the trunnions 6 and 6 are relatively displaced. Since the thrust needle bearings 27, 27 exist between the outer surface and the inner surface, the force required for this relative displacement is small. Therefore, as described above, the force for changing the inclination angle of each displacement shaft 7, 7 can be small.
[0017]
In the case of the toroidal-type continuously variable transmission configured and operated as described above, it is necessary to feed the lubricating oil to the radial needle bearing 25 and the thrust ball bearing 26 for supporting the power rollers 8 and 8. In any case, when the toroidal type continuously variable transmission is operated, the power rollers 8 and 8 rotate at a high speed while receiving a large load. Therefore, in order to ensure the durability of the radial needle bearing 25 and the thrust ball bearing 26, it is necessary to feed a sufficient amount of lubricating oil to both the bearings 25 and 26.
[0018]
Therefore, conventionally, a lubricating oil passage 38 (see FIG. 9 ) is formed inside the trunnion 6, and oil passage holes 39, 39 are formed in the thrust outer ring 30 constituting the thrust ball bearing 26. Lubricating oil can be fed into the bearing 26 freely. Further, the lubricating oil is fed into the radial needle bearing 25 through an oil supply passage provided on the inner side of the pivot shaft 22 constituting the first half of the displacement shaft 7. The upstream end of the oil supply passage is open to a part of the base end surface 40 of the pivot shaft 22 that is separated from the support shaft 21.
[0019]
When the toroidal continuously variable transmission is operated, the lubricating oil is fed into the lubricating oil passage 38 by the action of a pump (not shown) incorporated in the transmission. First, the lubricating oil flows out from the downstream end opening of the lubricating oil passage 38 into the gap space between the outer side surface of the thrust outer ring 30 and the inner side surface of the trunnion 6 constituting the thrust ball bearing 26. Further, this lubricating oil is sent to the thrust ball bearing 26 through the oil passage holes 39, 39, and to the radial needle bearing 25 through the oil supply passage, thereby lubricating both the bearings 26, 25.
[0020]
[Problems to be solved by the invention]
However, in the case of the conventional structure as described above, it is difficult to ensure a sufficient amount of lubricating oil sent to the thrust ball bearing 26 through the oil passage holes 39, 39. Concerning the reason for this will be described with reference to FIGS. The lubricating oil (traction oil) fed into the lubricating oil passage 38 provided in the trunnion 6 is branched from the lubricating oil passage 38 through the circular hole 23 provided in the central portion of the trunnion 6 (in the case of FIG. 9 ) . It discharges to the inner surface side of the trunnion 6 through the branched flow paths 41 and 41 (in the case of FIG. 10 ). The lubricating oil passes through the thrust needle bearing 27 and then enters the thrust ball bearing 26 through the oil passage holes 39 and 39. In the case of the conventional structure, since the downstream ends of these oil passage holes 39, 39 are opened to the inner diameter side of the thrust outer ring raceway 32, the lubricating oil discharged from the downstream ends of these oil passage holes 39, 39 is provided. Reaches the installation portion of the balls 29 and 29 based on the centrifugal force, and lubricates the thrust ball bearing 26.
[0021]
However, in the case of the conventional structure, a part of the lubricating oil discharged from each oil passage hole 39, 39 passes through the space existing between the balls 29, 29 adjacent in the circumferential direction, and the thrust ball bearing Without being lubricated, it will be discharged to the surroundings. As a result, the amount of lubricating oil used for lubricating the thrust ball bearing 26 is reduced.
[0022]
During the operation of the toroidal type continuously variable transmission, the thrust ball bearing 26 rotates at a high speed in a state where an extremely large thrust load is applied. In addition, since this thrust load is applied non-uniformly in the circumferential direction, the surface applied to the contact portion (rolling contact portion) between the rolling surface of each of the balls 29, 29 and the thrust inner ring raceway 31 and the thrust outer ring raceway 32. The pressure is partly very high. Furthermore, the lubricating oil used to lubricate the toroidal-type continuously variable transmission is a traction oil that has a higher viscosity than the mission oil used in a general gear-type transmission. It is conceivable that the lubricating oil adhering to the part is difficult to rotate around the part to be lubricated.
[0023]
In any case, when the lubricating oil fed into the thrust ball bearing 26 is insufficient, each ball 29, when the toroidal continuously variable transmission is continuously used in a severe condition such as high-speed rotation with a high load, There is a possibility that damage such as early separation may occur on the 29 rolling surfaces, the thrust inner ring raceway 31 and the thrust outer ring raceway 32.
Under such circumstances, it is desired to realize a structure capable of efficiently feeding traction oil, which is lubricating oil, to the thrust ball bearing 26 for supporting the power roller 8 of the toroidal-type continuously variable transmission.
The toroidal continuously variable transmission of the present invention has been invented in view of such circumstances.
[0024]
[Means for solving the problems]
The toroidal type continuously variable transmission of the present invention is the same as the above-described conventional toroidal type continuously variable transmission, in which the inner surfaces of the toroidal type continuously variable transmission are opposed to each other and supported concentrically and rotatably. A second disc and a trunnion that does not intersect the central axes of the first and second discs but swings around a pivot that is at a twisted position that is perpendicular to the direction of the central axis. The support shaft portion and the pivot shaft portion eccentric to each other, the support shaft portion of which is rotatably supported by the trunnion, the displacement shaft projecting the pivot shaft portion from the inner surface of the trunnion, and the above A power roller sandwiched between the inner surfaces of the first and second disks in a state of being rotatably supported around the pivot shaft through a radial bearing, and an outer surface of the power roller And the inner surface of the trunnion A thrust rolling bearing and a thrust bearing provided in order from the power roller side, and a lubricating oil passage provided inside the trunnion for discharging lubricating oil to the inner side surface of the trunnion. The rolling bearing was supported by the thrust inner ring raceway provided on the outer side surface of the power roller and the inner side surface of the trunnion by the thrust bearing in a state in which displacement with respect to the trunnion was allowed around the support shaft portion. A thrust outer ring, a thrust outer ring raceway provided on the inner surface of the thrust outer ring, a plurality of rolling elements provided in a freely rollable manner between the thrust outer ring raceway and the thrust inner ring raceway, and the thrust outer ring An oil passage hole that communicates the both side surfaces and guides the lubricating oil discharged from the lubricating oil passage to the inner side surface of the thrust outer ring. Obtain.
In particular, in the toroidal type continuously variable transmission according to the present invention, the downstream end of the oil passage hole is a part of the thrust outer ring raceway, and the thrust outer ring raceway and each of the rolling elements are related to the radial direction of the thrust outer ring. It opens to the inner diameter side of the rolling contact portion (contact portion) with the rolling surface of the moving body .
[0025]
[Action]
The toroidal type continuously variable transmission of the present invention configured as described above has a rotational force between the first disk and the second disk based on the same operation as the conventional toroidal type continuously variable transmission described above. By performing transmission, and further changing the angle of inclination of the trunnion, the rotational speed ratio of these two disks is changed.
In particular, in the case of the toroidal continuously variable transmission according to the present invention, the oil is discharged from the downstream end opening of the lubricating oil passage provided on the trunnion side to the inner surface side of the trunnion and further flows into the oil passage hole provided in the thrust outer ring. The lubricated oil is discharged as it is to the thrust outer ring raceway portion without flowing around. Accordingly, all of the lubricating oil that has flowed into the oil passage hole is fed into the thrust rolling bearing, and the thrust rolling bearing is sufficiently lubricated.
[0026]
DETAILED DESCRIPTION OF THE INVENTION
1 to 3 show an example of a reference example related to the present invention. The feature of this reference example is that a lubricating oil passage provided in the trunnion 6 is provided in a thrust ball bearing 26 for rotatably supporting the power roller 8 while supporting a thrust load applied to the power roller 8. 38 is a structure of a portion for feeding the lubricating oil fed through 38. Since the structure and operation of the other parts are the same as those of the above-described conventional structure, overlapping illustrations and descriptions are omitted or simplified, and the following description will focus on the characteristic parts of this reference example .
[0027]
The thrust outer ring 30 that constitutes the thrust ball bearing 26 is formed with a plurality of oil passage holes 39 that respectively connect both end surfaces of the thrust outer ring 30 in the axial direction (vertical direction in FIGS. 1 and 2). . The positions where these oil passage holes 39 are formed may be equidistant positions in the circumferential direction, but particularly in a portion where lubricating oil can be fed to a portion to which a large thrust load is applied (a portion immediately before the portion with respect to the rotation direction). If formed, the lubricity can be improved.
[0028]
In particular, in the case of this reference example , a thrust outer ring raceway 32 in which the downstream end (the upper end in FIGS. 1 and 2) of the oil passage hole 39 is formed on the inner side surface (the upper surface in FIGS. 1 and 2) of the thrust outer ring 30. The bottom of the groove is opened. In the case of this example, the contact angle of each ball 29 is 90 degrees as shown in FIG. Accordingly, the rolling surfaces of the balls 29 abut against the peripheral edge of the downstream end opening of the oil passage holes 39. Therefore, the downstream end opening of each oil passage hole 39 is a curved surface having an arc cross section as shown in FIG. 3, and an excessive surface pressure based on the edge load acts on the rolling surface of each ball 29. Is preventing.
[0029]
During operation of the toroidal continuously variable transmission, the lubricating oil (traction oil) fed into the lubricating oil passage 38 provided in the trunnion 6 passes through the branch passages 41, 41 branched from the lubricating oil passage 38. 6 is discharged to the inner surface side. Then, after passing through the thrust needle bearing 27, the lubricating oil enters the oil passage holes 39, and is fed into the thrust ball bearing 26 from the downstream end openings of the oil passage holes 39.
[0030]
In particular, in the case of the toroidal type continuously variable transmission of this reference example , the lubricating oil flowing into each oil passage hole 39 does not flow away to the surroundings, and the thrust outer ring provided on the inner side surface of the thrust outer ring 30 as it is. Discharge to the track 32 portion. Accordingly, all of the lubricating oil flowing into the oil passage hole 39 is sent into the thrust ball bearing 26. Further, most of the lubricating oil fed into the thrust ball bearing 26 in this way is in contact portions (rolling contact portions) between the rolling surfaces of the balls 29 and the thrust inner ring raceway 31 and the thrust outer ring raceway 32. The thrust ball bearing 26 is sufficiently lubricated by adhering.
[0031]
Next, FIG. 4 shows a first example of the embodiment of the present invention. In the case of this example, the downstream end opening of the oil passage hole 39 is opened on the inner diameter side of the pitch circle of the plurality of balls 29. Also in this example, the contact angle of each ball 29 is 90 degrees. Therefore, the downstream end opening of the oil passage hole 39 is present on the inner diameter side of the rolling contact portion between the thrust outer ring raceway 32 and the rolling surface of each ball 29 in the radial direction of the thrust outer ring 30. The 29 rolling surfaces do not contact the peripheral edge of the downstream end opening of the oil passage hole 39. Accordingly, it is not always necessary to form a curved surface at the downstream end opening of each oil passage hole 39. The lubricating oil discharged from the downstream end of the oil passage hole 39 reaches the rolling contact portion based on the centrifugal force, and lubricates the rolling contact portion. Other configurations and operations are the same as those of the reference example described above.
[0032]
Next, FIG. 5 shows a second example of the embodiment of the present invention. In the case of this example, each ball 29 is given a contact angle, and the downstream end of the oil passage hole 39 for feeding the lubricating oil into the thrust ball bearing 26 is opened at the groove bottom of the thrust outer ring raceway 32. Yes. Therefore, also in this example, the downstream end opening of the oil passage hole 39 is on the inner diameter side with respect to the rolling contact portion between the thrust outer ring raceway 32 and the rolling surface of each ball 29 in the radial direction of the thrust outer ring 30. The rolling surface of each ball 29 and the downstream end opening peripheral portion of the oil passage hole 39 do not come into contact with each other, and therefore, it is necessary to form a curved surface at the downstream end opening portion of the oil passage hole 39. There is no.
[0033]
【The invention's effect】
Since the toroidal continuously variable transmission of the present invention is configured and operates as described above, it is possible to feed a sufficient amount of lubricating oil to a thrust rolling bearing that supports a power roller that rotates at a high speed while receiving a high load. It becomes. As a result, it is possible to contribute to improving the durability of the toroidal type continuously variable transmission.
[Brief description of the drawings]
FIG. 1 is a cross-sectional view of an essential part showing one example of a reference example related to the present invention .
FIG. 2 is a half sectional view showing only a thrust ball bearing attached to a power roller.
FIG. 3 is an enlarged view of a part A in FIG. 2;
FIG. 4 is a view similar to FIG. 2, showing a first example of an embodiment of the present invention.
FIG. 5 is a view similar to FIG. 2, showing the second example .
FIG. 6 is a side view showing a basic configuration of a conventionally known toroidal continuously variable transmission in a state at the time of maximum deceleration.
FIG. 7 is a side view showing the state of the maximum speed increase.
FIG. 8 is a cross-sectional view showing an example of a conventional specific structure.
9 is a cross-sectional view taken along the line BB in FIG.
FIG. 10 is a view similar to FIG. 1, showing a conventional structure.
[Explanation of symbols]
1 Input shaft 2 Input side disk (first disk)
2a Inner side surface 3 Output shaft 4 Output side disk (second disk)
4a inner surface 5 pivot 6 trunnion 7 displacement shaft 8 power roller 8a peripheral surface 9 pressing device 10 cam plate 11 cage 12 roller 13, 14 cam surface 15 input shaft 16 needle bearing 17 flange 18 output gear 19 key 20 support plate 21 Support shaft portion 22 Pivot shaft portion 23 Circular holes 24, 25 Radial needle bearing 26 Thrust ball bearing 27 Thrust needle bearing 28 Cage 29 Ball 30 Thrust outer ring 31 Thrust inner ring raceway 32 Thrust outer ring raceway 33 Race 34 Cage 35 Needle 36 Drive Rod 37 Drive piston 38 Lubricating oil passage 39 Oil passage hole 40 Base end face 41 Branch flow path 42 Drive cylinder

Claims (1)

With the inner surfaces facing each other, the first and second disks supported concentrically and rotatably are not intersected with the central axes of these first and second disks. It consists of a trunnion that swings about a pivot that is at a torsional position that is perpendicular to the direction of the central axis, and a support shaft and a pivot shaft that are eccentric to each other. In a state of being supported rotatably, a displacement shaft in which the pivot shaft portion protrudes from the inner surface of the trunnion, and a state in which the pivot shaft portion is rotatably supported around the pivot shaft portion via a radial bearing, A thrust roller bearing provided in order from the side of the power roller between the power roller sandwiched between the inner surfaces of the second discs and the outer surface of the power roller and the inner surface of the trunnion And thrust bearings A lubricating oil passage that is provided inside the trunnion and discharges lubricating oil to the inner side surface of the trunnion, and the thrust rolling bearing includes a thrust inner ring raceway provided on an outer side surface of the power roller, A thrust outer ring supported on the inner side surface of the trunnion by a thrust bearing in a state in which displacement with respect to the trunnion is allowed around the support shaft portion, a thrust outer ring raceway provided on the inner side surface of the thrust outer ring, A plurality of rolling elements provided in a freely rolling manner between the thrust outer ring raceway and the thrust inner ring raceway and both side surfaces of the thrust outer ring communicate with each other, and the lubricating oil discharged from the lubricating oil passage is In a toroidal-type continuously variable transmission having an oil passage hole that leads to an inner surface side of a thrust outer ring, the downstream end of the oil passage hole is connected to the thrust outer ring raceway. Some in, in the radial direction of the thrust outer ring, the toroidal type continuously variable transmission, characterized in that was open to the inner diameter side than the rolling contact portion between the thrust ring raceway and the rolling surface of the rolling elements.

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