JP5673205B2 - Toroidal continuously variable transmission - Google Patents

Description

  The present invention relates to a generator (generator) used in, for example, an automatic transmission for a vehicle (automobile), an automatic transmission for a construction machine (construction machine), an aircraft (a fixed wing aircraft, a rotary wing aircraft, an airship, etc.), etc. The present invention relates to improvement of a half toroidal toroidal continuously variable transmission that is used as an automatic transmission for adjusting the operating speed of various industrial machines such as automatic transmissions and pumps.

  The use of a half-toroidal toroidal continuously variable transmission as a transmission for an automobile is described in many publications such as Patent Documents 1 to 4 and partially implemented, and is well known. Further, a structure in which a toroidal type continuously variable transmission and a planetary gear mechanism are combined to widen the adjustment range of the gear ratio is also described in many publications such as Patent Document 5 and has been widely known. 6 to 7 show a first example of a toroidal-type continuously variable transmission described in each of these patent documents and widely known in the past. In the case of the first example of this conventional structure, a pair of input disks 2 and 2 are disposed around the portions near both ends of the input rotation shaft 1 in a state where the inner surfaces, each of which is a toroidal curved surface, face each other. The rotation synchronized with the rotating shaft 1 is freely supported. An output tube 3 is supported around the intermediate portion of the input rotary shaft 1 so as to freely rotate with respect to the input rotary shaft 1. Further, on the outer peripheral surface of the output cylinder 3, an output gear 4 is fixed at the center in the axial direction, and a pair of output disks 5 and 5 are connected to both ends in the axial direction by spline engagement. Supports rotation synchronized with the motor. In this state, the inner surfaces of the output disks 5 and 5, each of which is a toroidal curved surface, are opposed to the inner surfaces of the input disks 2 and 2.

  Further, a plurality of power rollers 6, 6 each having a spherical convex surface are sandwiched between the input disks 2, 2 and the output disks 5, 5. The power rollers 6 and 6 are rotatably supported by trunnions 7 and 7, respectively. The trunnions 7 and 7 are tilted with respect to the central axes of the disks 2 and 5, respectively. The shafts 8 and 8 are supported so as to be swingable and displaceable. That is, each of the trunnions 7 and 7 includes a pair of tilting shafts 8 and 8 provided concentrically with each other at both axial ends, and a supporting beam existing between the tilting shafts 8 and 8. These tilting shafts 8 and 8 are pivotally supported with respect to the support plates 10 and 10 via radial needle bearings 11 and 11, respectively.

  Each of the power rollers 6 and 6 includes support shafts 12 and 12 in which the base half portion and the tip half portion are eccentric to each other on the inner surface of the support beam portions 9 and 9 constituting the trunnions 7 and 7, respectively. Via a plurality of rolling bearings, the support shafts 12 and 12 are supported so as to be able to rotate around the front half of each of the support shafts 12 and 12 and to be slightly oscillated and displaced about the base half of each of the support shafts 12 and 12. ing. Between the outer side surfaces of the power rollers 6 and 6 and the inner side surfaces of the support beam portions 9 and 9 constituting the trunnions 7 and 7, each is a part of the plurality of rolling bearings. The thrust ball bearings 13 and 13 and the thrust needle bearings 14 and 14 are provided in order from the power rollers 6 and 6 side. Of these, the thrust ball bearings 13, 13 allow the power rollers 6, 6 to rotate while supporting a load in the thrust direction applied to the power rollers 6, 6. Each of these thrust ball bearings 13, 13 has a plurality of balls 18 between an inner ring raceway 15 formed on the outer side surface of each of the power rollers 6, 6 and an outer ring raceway 17 formed on the inner side surface of the outer ring 16. , 18 are provided to be freely rollable. The thrust needle roller bearings 14, 14 support thrust loads applied to the outer rings 16, 16 constituting the thrust ball bearings 13, 13 from the power rollers 6, 6. The front half of each of the support shafts 12 and 12 is allowed to swing around the base half of each of the support shafts 12 and 12.

  During operation of the toroidal-type continuously variable transmission as described above, one input disk 2 (left side in FIG. 6) is rotationally driven by the drive shaft 19 via the pressing device 20. As a result, the pair of input disks 2 and 2 supported at both ends of the input rotating shaft 1 rotate synchronously while being pressed in a direction approaching each other. The rotation is transmitted to the output disks 5 and 5 through the power rollers 6 and 6 and is taken out from the output gear 4. When changing the gear ratio between the input rotary shaft 1 and the output gear 4, the trunnions 7, 7 are displaced in the axial direction of the tilt shafts 8, 8 by hydraulic actuators 21, 21. . 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 6 and 6 and the inner surface of each of the disks 2 and 5 changes (in the rolling contact portion). Side slip occurs). As the direction of the force changes, the trunnions 7 and 7 swing around their tilting shafts 8 and 8, and the peripheral surfaces of the power rollers 6 and 6 and the disks 2 and 8. The contact position with the inner surface of 5 changes. The circumferential surfaces of the power rollers 6 and 6 are in rolling contact with the radially outer portions of the inner surfaces of the input disks 2 and 2 and the radially inner portions of the inner surfaces of the output disks 5 and 5. By doing so, the gear ratio between the input rotary shaft 1 and the output gear 4 is increased. On the other hand, the peripheral surfaces of the power rollers 6 and 6 are arranged radially inwardly on the inner side surfaces of the input disks 2 and 2 and radially outwardly on the inner side surfaces of the output disks 5 and 5. If it is brought into rolling contact with the portion, the gear ratio between the input rotary shaft 1 and the output gear 4 becomes the deceleration side.

  When the toroidal type continuously variable transmission as described above is operated, the members used for power transmission, that is, the input and output disks 2 and 5 and the power rollers 6 and 6 are connected to the pressing device 20. It is elastically deformed based on the pressing force generated. In accordance with this elastic deformation, the input and output disks 2 and 5 are displaced in the axial direction. The pressing force generated by the pressing device 20 increases as the torque transmitted by the toroidal continuously variable transmission increases, and the amount of elastic deformation of the members 2, 5, 6 increases accordingly. Accordingly, in order to properly maintain the contact state between the inner surface of each of the input and output disks 2 and 5 and the peripheral surface of each of the power rollers 6 and 6 regardless of the fluctuation of the torque, the trunnions 7 and 7 7, a mechanism for displacing the power rollers 6 and 6 in the axial direction of the disks 2 and 5 is required. In the case of the above-described first example of the conventional structure, the tip half of each of the support shafts 12 and 12 that support the power rollers 6 and 6 is also oscillated and displaced about the base half as well. The power rollers 6 and 6 are displaced in the axial direction.

  In the case of the first example of the conventional structure as described above, the structure for displacing each of the power rollers 6 and 6 in the axial direction is complicated, and parts manufacturing, parts management, and assembly work are all troublesome and costly. It is inevitable that the volume increases. As a technique for solving such a problem, Patent Document 3 describes a structure as shown in FIGS. Since the present invention improves the second example of the conventional structure shown in FIGS. 8 to 13, the second example of the conventional structure will be described next. The characteristic of the second example of this conventional structure is the structure of the portion that supports the trunnion 7a so that the power roller 6a can be displaced in the axial direction of the input and output disks 2, 5 (see FIG. 6). The overall structure and operation of the toroidal continuously variable transmission are the same as those of the first example of the conventional structure shown in FIGS.

  The trunnion 7a constituting the second example of the conventional structure exists between a pair of tilting shafts 8a and 8b concentrically provided at both ends, and between these tilting shafts 8a and 8b, and at least A support having a cylindrical convex surface 22 on the inner side (upper side in FIGS. 9 and 12 to 13) in the radial direction (up and down direction in FIGS. 9 and 12 to 13) of the input and output disks 2 and 5 (see FIG. 6). And a beam portion 23. Both the tilting shafts 8a and 8b are supported on the support plates 10 and 10 (see FIG. 7) through the radial needle bearings 11a and 11a, respectively, so as to be swingable.

  Further, as shown in FIGS. 9 and 12, the central axis A of the cylindrical convex surface 22 is parallel to the central axis B of the two tilting shafts 8a and 8b, and the central axis B of the two tilting shafts 8a and 8b. Rather than the outer side (the lower side of FIGS. 9 and 12 to 13) in the radial direction of the disks 2 and 5. Further, a concave portion 24 having a partially cylindrical surface is radially crossed on the outer surface of the outer ring 16a constituting the thrust ball bearing 13a provided between the support beam portion 23 and the outer surface of the power roller 6a. It is provided in the state. And this recessed part 24 and the cylindrical convex surface 22 of the said support beam part 23 are engaged, and the said outer ring 16a is rockable displacement about the axial direction of each said disks 2 and 5 with respect to the said trunnion 7a. I support it.

  Further, a support shaft 12a is fixed to the center of the inner surface of the outer ring 16a integrally with the outer ring 16a, and the power roller 6a is rotatable around the support shaft 12a via a radial needle bearing 25. I support it. Furthermore, a pair of stepped surfaces 26 and 26 facing each other are provided on the inner surface of the trunnion 7a at a continuous portion between both end portions of the support beam portion 23 and the pair of tilting shafts 8a and 8b. . Then, these stepped surfaces 26, 26 and the outer peripheral surface of the outer ring 16a constituting the thrust ball bearing 13a are brought into contact with or in close proximity to each other, and any traction force applied from the power roller 6a to the outer ring 16a is selected. These step surfaces 26 and 26 can be supported.

According to the toroidal type continuously variable transmission of the second example of the conventional structure configured as described above, the power roller 6a is displaced in the axial direction of each of the disks 2 and 5, and the amount of elastic deformation of each constituent member is increased. Regardless of the change, a structure capable of appropriately maintaining the contact state between the peripheral surface of the power roller 6a and the disks 2 and 5 can be configured simply and at low cost.
That is, during operation of the toroidal continuously variable transmission, the power rollers 6a are displaced in the axial direction of the disks 2 and 5 based on elastic deformation of the input and output disks 2 and 5 and the power rollers 6a. When necessary, the outer ring 16a of the thrust ball bearing 13a that rotatably supports each of the power rollers 6a is provided with a concave portion 24 having a partial cylindrical surface provided on the outer surface and a cylindrical convex surface 22 of the support beam portion 23. The sliding surface of the cylindrical convex surface 22 is oscillated and displaced about the central axis a. Based on this oscillating displacement, a portion of the peripheral surface of each power roller 6a that is in rolling contact with one axial side surface of each disk 2, 5 is displaced in the axial direction of each disk 2, 5; The contact state is properly maintained.

  As described above, the central axis A of the cylindrical convex surface 22 is larger in diameter than the central axes B of the tilting shafts 8a and 8b, which are the oscillation centers of the trunnions 7a during the shifting operation. Exists with respect to the direction. Therefore, the radius of the rocking displacement about the central axis A of the cylindrical convex surface 22 is larger than the rocking radius at the time of the speed change operation, and both the input disks 2 and 2 and the both output disks 5, 5 Has little effect on the change in the transmission ratio between (and can be neglected or remain within an easily modifiable range).

  In the case of the second example of the conventional structure shown in FIGS. 8 to 13, parts production, parts management, and assembly work are all made easier and cost reduction is possible as compared with the first example shown in FIGS. Although easy to achieve, there is room for improvement in terms of stabilizing the shifting operation. The reason for this is that each step surface 26 is provided in a pair at each end of each support beam 23 so that the outer ring 16a can be smoothly moved and displaced about each support beam 23. , 26 to make the distance D between the outer rings 16a slightly larger than the outer diameter d (D> d). The outer rollers 16a and the power rollers 6a supported concentrically with the outer ring 16a have shafts of the support beam portions 23 corresponding to a difference (D−d) between the distance D and the outer diameter d. Displaceable in the direction.

  On the other hand, during operation of a vehicle equipped with a toroidal-type continuously variable transmission, each power roller 6a receives a force in the opposite direction from the respective disks 2 and 5 during acceleration and deceleration (when the engine brake is activated) ( "2Ft", which is well known in the technical field of toroidal-type continuously variable transmissions, is added. Then, the force 2Ft causes the power rollers 6a to be displaced in the axial direction of the support beam portions 23 together with the outer rings 16a. The direction of this displacement is the same as the direction of displacement of each trunnion 7, 7 (see FIG. 7) by each actuator 21, 21 described above, and the shifting operation is started even if the displacement is about 0.1 mm. Create a possibility. When the shifting operation is started for such a reason, the shifting operation is not directly related to the driving operation, and the driver feels uncomfortable regardless of any correction. In particular, when a shift that is not intended by the driver as described above is performed in a state where the torque transmitted by the toroidal-type continuously variable transmission is low, a sense of discomfort given to the driver tends to increase.

  In order to suppress the occurrence of the speed change operation that is not directly related to the driving operation as described above, the difference (D−d) between the distance D and the outer diameter d is made small (for example, about several tens of μm). ) Can be suppressed. However, during the operation of the half-toroidal toroidal continuously variable transmission, each trunnion 7a is caused by a thrust load applied to each support beam portion 23 from the traction portion via each power roller 6a and each outer ring 16a. As exaggeratedly shown in FIG. 14, the side on which each outer ring 16a is installed is elastically deformed in a concave direction. As a result of this elastic deformation, the distance between the step surfaces 26, 26 provided in pairs for each trunnion 7a is reduced. Even in such a state, in order to prevent the distance D between the two step surfaces 26 and 26 from becoming smaller than the outer diameter d of each outer ring 16a, the normal state (the state where each trunnion 7a is not elastically deformed). It is necessary to ensure a certain difference between the distance D and the outer diameter d. As a result, a shift operation that is not directly related to the driving operation as described above is likely to occur particularly during driving at a low torque, which tends to increase the sense of discomfort.

  On the other hand, in Patent Document 3, the anchor piece locked to a part of the cylindrical convex surface provided on the support beam part side and the anchor groove formed on the inner surface of the concave part on the outer ring side are engaged with each other. A structure for supporting a force 2Ft is described. There is also a structure for supporting the force 2Ft by forming a plurality of balls between the rolling grooves each having an arcuate cross section formed in a portion where the cylindrical convex surface and the concave portion are aligned with each other. Have been described. However, in the case of the former structure, it is difficult to support and fix the anchor piece to the support beam portion with sufficient strength and rigidity to support the force 2Ft, and it is possible to reduce the cost and to provide sufficient reliability. It is difficult to secure. In the latter case, when the force 2Ft increases and the surface pressure of the rolling contact portion between the rolling surface of each ball and each rolling groove increases, an indentation is formed on the inner surface of each rolling groove. As a result, vibration may occur when each inner ring swings and displaces with respect to each trunnion.

JP 2003-214516 A JP 2007-315595 A JP 2008-25821 A JP 2008-275088 A JP 2004-169719 A

  In view of the circumstances as described above, the present invention was invented to realize a structure that facilitates parts production, parts management, and assembly work, facilitates cost reduction, and stabilizes the speed change operation. is there.

The toroidal-type continuously variable transmission of the present invention includes at least a pair of disks, a plurality of trunnions, the same number of power rollers as each trunnion, and the same number of thrust rolling bearings.
In particular, in the toroidal type continuously variable transmission of the present invention, a holding hole having a circular cross section formed in a part of the outer ring of each thrust rolling bearing, and a state in which the inner fitting is fixed to the holding hole by an interference fit Thus, a cylindrical anchor pin partially projecting from the inner surface of the concave portion of the outer ring and a cylindrical convex surface constituting the outer peripheral surface of the support beam portion of each trunnion are formed in the circumferential direction of the cylindrical convex surface. An anchor groove is provided. Then, a part of the anchor pin is engaged with the anchor groove, and the torque applied to each power roller with the rotation of each disk can be supported by the engaging portion between the anchor pin and the anchor groove.

According to the toroidal-type continuously variable transmission of the present invention configured as described above, it is easy to manufacture parts, manage parts, and assemble work, easily reduce costs, and stabilize the speed change operation. realizable.
Of these, cost reduction is easy to achieve for the same reason as in the second example of the conventional structure shown in FIGS.
In addition, the speed change operation is stabilized based on the engagement between a part of the anchor pin provided on the outer ring side and the anchor groove provided on the trunnion side, and the outer ring is displaced relative to the trunnion in the axial direction of the support beam. This can be achieved by preventing this from happening.
Furthermore, it is easy to process the structure for supporting and fixing the anchor pin to the outer ring, and not only the manufacturing cost can be kept low, but also the supporting strength and supporting rigidity of the anchor pin with respect to the outer ring can be sufficiently increased. For this reason, sufficient durability and reliability can be ensured even when implemented with a toroidal continuously variable transmission that transmits a large torque (the force 2Ft increases).

The side view which takes out the trunnion and the outer ring | wheel which show the 1st example of embodiment of this invention, and shows it in the state seen from the same direction as FIG. FIG. 2 is a cross-sectional view taken along line aa in FIG. 1. The figure similar to FIG. 1 which shows the state in the middle of combining a trunnion and an outer ring | wheel. The figure similar to FIG. 1 which shows the 2nd example of embodiment of this invention. Bb sectional drawing of FIG. Sectional drawing which shows the 1st example of a conventional structure. Cc sectional drawing of FIG. The perspective view which looked at the trunnion which supported the power roller via the thrust ball bearing which shows the 2nd example of the conventional structure from the radial direction outer side of each disk. Similarly, the front view shown in the state seen from the circumferential direction of the disk. The top view seen from the upper part of FIG. The side view seen from the right side of FIG. Dd sectional drawing of FIG. Ee sectional drawing of FIG. The sectional view seen from the same direction as Drawing 12 which exaggerates and shows the state where the trunnion was elastically deformed based on the thrust load added from a power roller.

[First example of embodiment]
1 to 3 show a first example of an embodiment of the present invention corresponding to claims 1 to 3. The feature of this example is that the outer ring 16b constituting the thrust ball bearings 13a and 13a (see FIGS. 8 to 13) is provided to the support beam portion 23 of each trunnion 7b to stabilize the speed change operation. The structure is to prevent the displacement of each of the support beam portions 23 in the axial direction while supporting the swinging displacement with respect to the portion 23. Since the structure and operation of the other parts are the same as those of the second example of the conventional structure shown in FIGS. 8 to 13 described above, the illustration and description of the equivalent parts are omitted or simplified. The explanation will be focused on.

  In the case of the structure of this example, the anchor pin 27 supported and fixed on the outer ring 16 b side is engaged with the anchor groove 28 formed on the cylindrical convex surface 22 of the support beam portion 23. A distance D between a pair of step surfaces 26 provided at both ends of the support beam portion 23 in a part of each trunnion 7b is sufficiently larger than the outer diameter d (see FIG. 3) of each outer ring 16b. doing.

  In order to support and fix the anchor pin 27, a part of the outer ring 16b is deviated from the center of the outer ring 16b, and a holding hole 29 having a circular cross section is formed on the central axis of the recess 24 formed on the outer surface of the outer ring 16b. On the other hand, it is formed in a state where both ends open to the outer peripheral surface of the outer ring 16b at a twisted position and in a direction perpendicular to the direction of the central axis. That is, a support shaft 12a is provided at the center of the inner surface of the outer ring 16b, is provided concentrically with the outer ring raceway 17, and is integrally provided with the outer ring 16b. A power roller 6a is provided around the support shaft 12a, and a radial needle bearing 25 is provided. (See FIGS. 12 to 13). Further, the lubricating oil can be fed into the downstream lubricating oil flow path 30 provided in the central portion of the support shaft 12a from the upstream lubricating oil flow path 31 (see FIGS. 12 to 13) provided in the support beam portion 23. It is said. The holding hole 29 and the anchor groove 28 are formed at positions deviating from the center of the support shaft 12 a in the axial direction of the support beam portion 23, avoiding both the lubricating oil flow paths 30 and 31. The direction of the holding hole 29 is perpendicular to the direction of the recess 24 formed on the outer surface of the outer ring 16b (the direction of the central axis of the support beam 23 that engages with the recess 24). Further, in the intermediate portion in the axial direction of the holding hole 29, a portion of about half or less than half of the cross section is opened in a part of the recess 24.

  The anchor pin 27 is made of a hard metal such as bearing steel or high-speed steel, and has a cylindrical shape as a whole, and a chamfered portion having a quarter arc shape in cross section at the outer peripheral edge portion of both axial end surfaces. Forming. The inner diameter of the holding hole 29 in each free state is slightly smaller than the outer diameter of the anchor pin 27, and the anchor pin 27 is press-fitted into the holding hole 29, so that both end portions in the axial direction are connected to the outer ring. The inner fitting is fixed to 16b with an interference fit. In this state, a semi-cylindrical portion, which is a half portion in the radial direction of the intermediate portion of the anchor pin 27, projects from the intermediate portion of the recess 24.

  In addition, the anchor groove 28 is formed in a middle portion of the cylindrical convex surface 22 of the support beam portion 23 in a portion aligned with the middle portion of the anchor pin 27 in a state where the outer ring 16b and the trunnion 7b are combined. ing. The anchor groove 28 has an arc shape in cross section so that the axial intermediate portion of the anchor pin 27 can be engaged without rattling, and is formed on the cylindrical convex surface 22 of the support beam portion 23. It is formed in the circumferential direction. The radius of curvature of the cross-sectional shape of the anchor groove 28 is the same as or slightly larger than 1/2 of the outer diameter of the anchor pin 27. Further, the position where the anchor groove 28 is formed is regulated and the anchor groove 28 and the anchor pin 27 are engaged with each other, so that the outer peripheral surface of the outer ring 16b and the two step surfaces 26 and 26 are sufficiently separated from each other. (No contact despite the elastic deformation as shown in FIG. 14 described above).

  As described above, the toroidal type continuously variable transmission of this example brings the trunnion 7b and the outer ring 16b closer to each other from the state shown in FIG. 3 to the state shown in FIG. The anchor pins 27 are combined in an engaged state. When the toroidal continuously variable transmission is operated in this state, the force 2Ft applied to the trunnion 7b is supported by the engaging portion between the axial intermediate portion of the anchor pin 27 and the anchor groove 28. When the outer ring 16b swings and displaces with respect to the trunnion 7b in accordance with the fluctuation of the torque to be transmitted, the anchor pin 27 and the anchor groove 28 are relatively displaced, and the anchor pin in the anchor groove 28 is this anchor pin. The circumferential position of the part with which the intermediate part of 27 is engaged changes. Since the anchor pin 27 is cylindrical, the relative displacement between the intermediate portion of the anchor pin 27 and the anchor groove 28 is smoothly performed.

  The structure of the present example configured as described above and acting as described above can be obtained by forming a holding hole 29 having a circular cross section in the outer ring 16b in order to support and fix the cylindrical anchor pin 27 to the outer ring 16b. It ’s enough. It is easy to manufacture the cylindrical anchor pin 27 with a predetermined dimensional accuracy and to manufacture the holding hole 29 having a circular cross section with a predetermined dimensional accuracy. In addition, the operation of supporting and fixing the anchor pin 27 in the holding hole 29 is only required to press-fit the anchor pin 27 into the holding hole 29 linearly. After the press-fitting, the anchor pin 27 is supported and fixed to the outer ring 16b at both ends, and the force 2Ft is a so-called doubly supported beam structure applied to the intermediate portion of the anchor pin 27, and the rigidity against the force 2Ft is increased. Becomes larger. As a result, the structure of this example can realize a structure that can secure sufficient durability and reliability at a low cost even when implemented with a toroidal-type continuously variable transmission that transmits a large torque.

[Second Example of Embodiment]
4 to 5 show a second example of an embodiment of the present invention corresponding to claims 1 and 4. In the case of this example, holding holes 29a and 29a each having a circular cross section and having a bottom are formed at two positions in both ends in the width direction of the recess 24 formed on the outer surface of the outer ring 16c. The positions where these holding holes 29a and 29a are formed are portions (positions on the same circumference) where the positions of the central axis of the concave portion 24 coincide with each other. The directions of the holding holes 29a and 29a are the same (parallel) as the direction of the central axis of the support shaft 12a provided on the inner surface of the outer ring 16c. Then, the base halves of the anchor pins 27a and 27a are press-fitted into the holding holes 29a and 29a with an interference fit, respectively, and both the anchor pins 27a and 27a are fixed to the outer ring 16c. And the anchor groove which formed the part which protruded from the inner peripheral surface of the said recessed part 24 in the front half part of these both anchor pins 27a and 27a in the cylindrical convex surface 22 which comprises the outer peripheral surface of the support beam part 23 which comprises the trunnion 16b. 28 is engaged.
Also in the case of the structure of this example as described above, the processing and combination of both the holding holes 29a and 29a and the two anchor pins 27a and 27a can be easily performed. Further, a large force 2 Ft can be supported by the two anchor pins 27a and 27a.

  The present invention can be implemented by a toroidal continuously variable transmission alone, or can be implemented as a continuously variable transmission in combination with a planetary gear mechanism as described in Patent Document 5.

DESCRIPTION OF SYMBOLS 1 Input rotating shaft 2 Input disk 3 Output cylinder 4 Output gear 5 Output disk 6, 6a Power roller 7, 7a, 7b Trunnion 8, 8a, 8b Tilt shaft 9 Support beam part 10 Support plate 11, 11a Radial needle bearing 12, 12a Support shaft 13, 13a Thrust ball bearing 14 Thrust needle bearing 15 Inner ring raceway 16, 16a, 16b, 16c Outer ring 17 Outer raceway 18 Ball 19 Drive shaft 20 Pressing device 21 Actuator 22 Cylindrical convex surface 23 Support beam portion 24 Recess portion 25 Radial needle Bearing 26 Stepped surface 27, 27a Anchor pin 28 Anchor groove 29, 29a Holding hole 30 Downstream lubricant passage 31 Upstream lubricant passage

Claims (4)

Comprising at least one pair of disks, a plurality of trunnions, the same number of power rollers as each trunnion, and the same number of thrust rolling bearings;
Each of these discs is a toroidal curved surface having a circular arc cross section, with the axial one side surfaces facing each other, concentrically supported and freely supported by relative rotation,
Each trunnion exists between a pair of tilting shafts provided concentrically with each other at both ends, and between the two tilting shafts, and at least the inner side surface in the radial direction of each of the disks, A support beam portion having a cylindrical convex surface having a central axis that is parallel to the central axis of both tilting axes and that is present outside the central axis of the tilting axis with respect to the radial direction of each disk. With respect to the axial direction, swinging displacements about the tilting shafts that are twisted with respect to the central axis of each disk can be freely provided at a plurality of locations in the circumferential direction between the axial side surfaces of the respective disks. And
Each of the power rollers is rotatably supported on the inner side surface of each trunnion via a thrust rolling bearing, and each circumferential surface having a spherical convex surface is brought into contact with one axial side surface of each disk. And
Each thrust rolling bearing is provided between the support beam portion of each trunnion and the outer surface of each power roller, and an outer ring provided on each support beam portion side, and an inner ring of each outer ring. A plurality of rolling elements are provided between the outer ring raceway provided on the side surface and the inner ring raceway provided on the outer side surface of each of the power rollers, respectively.
The outer ring of each of the thrust rolling bearings is engaged with the concave portion provided on the outer surface of each of the outer rings and the cylindrical convex surface of each of the support beam portions, so that the axial direction of each of the discs with respect to each of these trunnions. In a toroidal type continuously variable transmission that is supported so as to be capable of rocking displacement,
A holding hole having a circular cross section formed in a part of the outer ring of each thrust rolling bearing, and a circle protruding partly from the inner surface of the recess of the outer ring in a state of being fitted and fixed to the holding hole by an interference fit. A columnar anchor pin, and a cylindrical convex surface forming an outer peripheral surface of the support beam portion of each trunnion are provided with anchor grooves formed in the circumferential direction of the cylindrical convex surface, and a part of the anchor pin and the anchor groove And a torque applied to each of the power rollers as the discs rotate by the engaging portions of the anchor pins and the anchor grooves. The holding hole is formed at a position twisted with respect to the central axis of the recess and in a direction perpendicular to the direction of the central axis, and has an intermediate portion opened to an intermediate portion in the width direction of the recess. ,
The anchor pin has an axially intermediate portion exposed to a part of the concave portion in a state where the axially opposite end portions are fitted and fixed to the holding hole by an interference fit.
The anchor groove has a circular arc shape that engages the axially intermediate portion of the anchor pin without rattling.
With respect to the axial direction of the support beam portion of each trunnion, the outer peripheral surfaces of both end portions of each outer ring and a part of each trunnion are separated from each other, and the engaging portion between the axial intermediate portion of the anchor pin and the anchor groove The toroidal-type continuously variable transmission according to claim 1, wherein torque applied to each power roller with rotation of each disk can be supported.   A support shaft concentric with the outer ring raceway is provided integrally with the outer ring at the center of the inner side surface of each outer ring, and each power roller is rotatable around the support shaft via a radial needle bearing. The lubricating oil can be fed into the downstream lubricating oil flow path provided in the center portion of the support shaft from the upstream lubricating oil flow path provided in the support beam portion of each trunnion, The holding hole and the anchor groove are formed at positions deviating from the center of the support shaft in the axial direction of the support beam portion, and the axial intermediate portion of the anchor pin is formed between the downstream side and the upstream side passages. The toroidal-type continuously variable transmission according to claim 2, wherein the toroidal continuously variable transmission is present in a portion deviated from the communication portion.   The holding holes are formed at two positions in the width direction of the concave portion, where the positions of the central axes of the concave portions in the axial direction coincide with each other, and the anchor pins are respectively connected to the end portions of the holding holes. The toroidal-type continuously variable transmission according to claim 1, which is press-fitted and fixed in a state of protruding from the inner peripheral surface of the recess.

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