JP2018084281A - Toroidal type non-stage transmission - Google Patents

Abstract

PROBLEM TO BE SOLVED: To realize a structure of a toroidal type non-stage transmission capable of lubricating a spline engagement part of an input rotary shaft and an input side disk efficiently by lubricating-oil.SOLUTION: On such a portion adjacent to the downstream side in connection with the flow direction of lubricant-oil with respect of the flow direction of lubricant oil with respect to a female spline portion 38 formed in a center hole 32 in an input side disk 2d, there is supported and fixed a lubricant-oil blocking member 14 having a smaller inner diameter dimension that the dedendum circle diameter of a male spline tooth constituting a male spline portion 30 formed in the outer circumference of an input rotary shaft 1a.SELECTED DRAWING: Figure 2

Description

  The present invention relates to an improvement of a toroidal continuously variable transmission that is used as an automatic transmission device for generators used in, for example, aircrafts, various industrial machines such as pumps, vehicles (automobiles), and construction machines. .

  The use of a toroidal-type continuously variable transmission as a transmission for an automobile is described in publications such as Patent Document 1 and is partially implemented, and is well known. Further, a structure in which the adjustment range of the gear ratio is widened by combining a toroidal type continuously variable transmission and a planetary gear mechanism is described in publications such as Patent Document 2 and has been widely known. FIG. 10 shows an example of a toroidal-type continuously variable transmission described in these patent documents and widely known in the past. In the case of this conventional structure, a pair of input-side discs 2a and 2b are arranged around the portions near both axial ends of the input rotating shaft 1, and axial side surfaces (inner side surfaces) each of which is a toroidal curved surface having an arcuate cross section. Are supported via ball splines 3 and 3 in a state of facing each other. As a result, the pair of input side disks 2a and 2b are configured to be able to move far and near and to rotate in synchronization with each other via the input rotation shaft 1. Further, an output cylinder 4 is supported around an intermediate portion in the axial direction of the input rotary shaft 1 so as to be able to rotate relative to the input rotary shaft 1. Further, an output gear 5 is fixed to the outer peripheral surface of the output cylinder 4 at the center in the axial direction, and a pair of output side disks 6 and 6 are rotated at both ends in the axial direction in synchronization with the output cylinder 4. I support it. Further, in this state, the axial side surfaces of the output side disks 6 and 6, each of which is a toroidal curved surface having an arc cross section, are opposed to the axial side surfaces of the input side disks 2 a and 2 b.

Also, a plurality of power rollers 7 and 7 each having a partially spherical convex surface are sandwiched between the input disks 2a and 2b and the output disks 6 and 6. These power rollers 7 and 7 are rotatably supported by trunnions 8 and 8, and rotate with the rotation of both input side disks 2 a and 2 b, while the both input side disks 2 a and 2 b rotate the both Power is transmitted to the output side disks 6 and 6. That is, during operation of the toroidal-type continuously variable transmission, one input side disk 2a (left side in FIG. 10) is rotationally driven by the drive shaft 9 via the mechanical pressing device 10. As a result, the pair of input-side disks 2a and 2b supported on the axially opposite ends of the input rotating shaft 1 rotate synchronously while being pressed toward each other. The rotation is transmitted to the output side disks 6 and 6 through the power rollers 7 and 7 and is taken out from the output gear 5.
Or, contrary to the above description, the power of the drive source is input to the inner disk provided at the position of the both output side disks 6, 6 and a pair of positions provided at the positions of the both input side disks 2a, 2b. It can also be configured to extract power from the outer disk.

  Preload springs 11a and 11b are provided in the vicinity of both end portions in the axial direction of the input rotary shaft 1 at positions where the both input side disks 2a and 2b are sandwiched from both sides in the axial direction. Even when the pressing device 10 is not in operation (when the drive shaft 9 is stopped), the peripheral surfaces of the power rollers 7 and 7 and the inner surfaces of the input side and output side disks 2a, 2b, 6 are provided. The surface pressure of the rolling contact part (traction part) is secured to the minimum necessary. Therefore, these rolling contact portions start power transmission without causing excessive slip immediately after the start of operation of the toroidal continuously variable transmission.

  By the way, the elasticity for securing the necessary minimum surface pressure can be obtained by the preload spring 11 a disposed on the inner diameter side of the pressing device 10. A preload spring 11b disposed between a loading nut 12 screwed to one axial end portion (tip portion) of the input rotary shaft 1 and the outer surface of the input side disk 2b is applied when the pressing device 10 is suddenly operated. It can alleviate the impact and can be omitted. Therefore, in order to reduce the number of parts and improve the assembly work efficiency, the preload spring is omitted from between the loading nut screwed to one axial end of the input rotation shaft and the outer surface of the input side disk. A structure has been proposed in which the input-side disk is supported relative to the input rotation shaft so as not to be relatively rotatable by spline engagement without using a ball spline (see, for example, Patent Document 3). In addition, instead of providing a loading nut, an outward flange-like flange is provided at the tip of the input rotation shaft, or a structure called a cotter for locking an engagement ring at the tip of the input rotation shaft is also known. .

JP 2003-214516 A JP 2004-169719 A JP-A-2015-090160 JP-A-5-295348 JP-A-6-313471 JP-A-7-332589

  In any of the above-described structures, the male spline portion provided on the outer peripheral surface of the axial end of the input rotation shaft and the female spline portion provided in the center hole of the input side disk are spline-engaged, and this input is performed. The side disc is supported so as to be able to rotate in synchronization with the input rotation shaft, but the spline engaging portion between the male spline portion and the female spline portion has the input side accompanying the pressing force by a power roller. Not only is the stress due to the elastic deformation of the disk easily concentrated, but also the fretting wear is likely to occur due to the gaps existing in the spline engaging portion. Therefore, in order to extend the life of the toroidal continuously variable transmission, it is indispensable to lubricate the spline engaging portion with lubricating oil.

However, in the case of the conventional structure, no special consideration has been given to efficiently lubricating the spline engaging portion. For this reason, most of the lubricating oil supplied to the spline engaging portion moves radially outward of the spline engaging portion by the action of centrifugal force, and the female spline teeth constituting the female spline portion of the input side disk are moved. It is discharged through the outer diameter side lubricating oil passage formed between the tooth bottom surface and the tooth tip surface of the male spline teeth constituting the male spline portion of the input rotating shaft, and the entire spline engaging portion is It was difficult to lubricate.
As other prior art documents related to the present invention, there are inventions described in Patent Documents 4 to 6. However, any of the inventions described in these Patent Documents 4 to 6 is an invention in which a seal member is provided to prevent the lubricating oil that lubricates the spline engaging portion from leaking to the outside. It is not intended to efficiently lubricate the spline engaging portion.
In view of the above circumstances, the present invention was invented to realize a structure of a toroidal continuously variable transmission that can efficiently lubricate a spline engaging portion between a rotating shaft and an outer disk with lubricating oil. is there.

A toroidal continuously variable transmission according to the present invention includes a rotating shaft, a pair of outer disks, an inner disk, a plurality of power rollers, and a lubricating oil damming member.
Among these, the rotating shaft is provided with a male spline portion at one end portion in the axial direction of the outer peripheral surface.
In addition, the pair of outer disks are synchronized with the rotating shafts on both axial sides of the rotating shaft in a state where the axial side surfaces of the pair of outer disks are each a toroidal curved surface having an arcuate cross section. Supported for rotation.
In addition, the inner disk has a rotating shaft around an axially intermediate portion of the rotating shaft in a state in which both axial side surfaces which are toroidal curved surfaces having an arcuate cross section are opposed to the axial side surfaces of the outer disks. Are supported so as to be capable of relative rotation with respect to each other.
Further, each of the plurality of power rollers is rotatably supported by a support member (for example, trunnion), and each peripheral surface formed as a partial spherical convex surface is formed on the pair of axially opposite side surfaces of the inner disk and the pair of power rollers. It is in contact with the axial side surface of the outer disk.
Further, the lubricating oil damming member is formed in an annular shape as a whole, and a female spline constituting a female spline portion formed on one outer disk provided on one end side in the axial direction of the pair of outer disks. An inner diameter dimension (and a larger outer diameter dimension) smaller than the root diameter of the tooth, and spline engagement between the female spline portion and the male spline portion of the one outer disk or the rotating shaft. A portion adjacent to the downstream side of the spline engaging portion with respect to the flow direction of the lubricating oil that passes through the portion in the axial direction and is lubricated is supported, for example, coaxially with the one outer disk or the rotating shaft.
Furthermore, when providing a pressing device additionally, this pressing device is provided between the other outer disk provided on the other axial end side of the pair of outer disks and the rotating shaft, The other outer disk is pressed toward one axial end (one outer disk). As such a pressing device, a mechanical pressing device incorporating a loading cam or a hydraulic pressing device including a hydraulic cylinder and a piston can be used.

When carrying out the present invention as described above, for example, as in the second aspect of the present invention, the inner diameter dimension of the lubricating oil damming member is made smaller than the tip circle diameter of the female spline teeth. Can do.
Moreover, when implementing this invention, the internal diameter dimension of the said lubricating oil damming member can also be made smaller than the root circle diameter of the male spline tooth | gear which comprises the said male spline part.

  When carrying out the present invention, for example, as in the invention described in claim 3, the lubricating oil damming member is adjacent to one axial end of the female spline portion of the one outer disk. Support to the part to be. Further, the inner diameter dimension of the lubricating oil damming member can be made larger than the outer diameter dimension of the portion of the rotating shaft that is located on one end side in the axial direction than the portion where the male spline portion is formed.

According to the toroidal continuously variable transmission of the present invention having the above-described configuration, the spline engaging portion between the rotating shaft and the (one) outer disk can be efficiently lubricated with the lubricating oil.
That is, in the case of the present invention, a portion of the outer disk or the rotating shaft adjacent to the spline engaging portion on the downstream side with respect to the flow direction of the lubricating oil is configured in an annular shape, and the female spline. The lubricating oil damming member having an inner diameter smaller than the root diameter of the female spline teeth constituting the portion is supported.
Therefore, the outlet side of the outer-diameter side lubricating oil flow path formed between the bottom surface of the female spline teeth and the tip surface of the male spline teeth provided on the rotating shaft by the lubricating oil blocking member. Among the openings, at least the outer diameter side portion can be closed (damped).
Therefore, even when the lubricating oil supplied through the oil passage provided inside the rotating shaft moves radially outward due to centrifugal force, the lubricating oil concentrates on the outer-diameter side lubricating oil passage. It can be prevented from passing (the amount of lubricating oil passing through the outer diameter side lubricating oil passage can be reduced).
As a result, according to the present invention, it is possible to easily allow the lubricating oil to pass through a portion other than the outer diameter side lubricating oil passage, and it is possible to efficiently lubricate the entire spline engaging portion.

  According to the invention described in claim 2 as described above, the lubricating oil damming member can block the entire opening on the outlet side of the outer diameter side lubricating oil flow path, and the female spline teeth. At least the outer diameter side portion of the outlet side opening of the inner diameter side lubricating oil passage formed between the tooth tip surface and the tooth bottom surface of the male spline tooth can be closed. For this reason, lubricating oil can be effectively fed into a portion between the tooth surfaces of the female spline teeth and the male spline teeth, and the spline engaging portion can be more effectively lubricated.

  Furthermore, according to the invention described in claim 3 as described above, the lubricating oil damming member can be easily assembled from one axial end side (front end side) of the rotating shaft. For this reason, it is possible to suppress a decrease in the assemblability of the toroidal continuously variable transmission resulting from the provision of the lubricating oil damming member.

Sectional drawing of the toroidal type continuously variable transmission which shows the 1st example of embodiment of this invention. The A section enlarged view of FIG. 1 similarly. The B section enlarged view of FIG. 2 similarly. FIG. 4 is a view taken in the direction of arrow C in FIG. The figure equivalent to FIG. 3 which shows the 2nd example of embodiment of this invention. The figure equivalent to FIG. 3 which shows the 3rd example of embodiment of this invention. The figure equivalent to FIG. 3 which shows the 4th example of embodiment of this invention. The figure (A) equivalent to FIG. 3 which shows the 5th example of embodiment of this invention, and D arrow line view (B) of (A). The front view which takes out and shows the lubricating oil damming member which shows the 6th example of embodiment of this invention. Sectional drawing which shows the toroidal type continuously variable transmission of conventional structure.

[First example of embodiment]
1 to 4 show a first example of an embodiment of the present invention. The toroidal-type continuously variable transmission 13 of this example is a transmission that is used, for example, for an aircraft generator, and each of the input rotary shaft 1a corresponding to the rotary shaft described in the claims, A pair of input side disks 2c and 2d corresponding to the outer disk described in the range, an output side disk 6a corresponding to the inner disk described in the claims, a plurality of power rollers 7 and 7, and not shown A plurality of trunnions, a hydraulic pressing device (loading device) 10a, and a lubricating oil blocking member 14 are provided.

The input rotation shaft 1a is supported on the upper side of the actuator case 15 through a pair of support columns 16 and 16 and the output side disk 6a so as to be rotatable only. Specifically, the input rotary shaft 1a is provided on the inner diameter side of the output side disk 6a rotatably supported by a thrust ring type ball bearing on a support ring portion provided at an intermediate portion between the support columns 16 and 16, respectively. Further, it is rotatably supported by a pair of radial needle bearings.
In the present specification and claims, the “axial direction” refers to the axial direction of the input-side rotary shaft 1a unless otherwise specified, and refers to the horizontal direction in FIGS. Moreover, in the case of this example, the right side of FIGS. 1-3 which is the front end side of the said input rotating shaft 1a is equivalent to the axial direction one end side of a claim.

  The two input-side disks 2c and 2d are disposed at portions close to both ends in the axial direction of the input rotation shaft 1a in a state where the axial side surfaces (inner side surfaces) of the toroidal curved surfaces each having a circular arc cross section are opposed to each other. The rotation is synchronized with the input rotation shaft 1a, and is supported so as to be movable in the near and far directions.

  For this purpose, of the two input side disks 2c and 2d, the input side disk 2c provided on the left side in FIG. 1, which is the other axial end side (base end side) of the input rotary shaft 1a, is pressed. It is supported on the input-side rotary shaft 1a through a cylinder 17 constituting the device 10a so that it can be slightly displaced in the axial direction and can be rotated in synchronization with the input rotary shaft 1a. The cylinder 17 is configured by coupling and fixing an outer peripheral edge portion of the inner diameter side cylinder element 18 and an inner peripheral edge portion of the outer diameter side cylinder element 19, and the inner diameter side cylinder element 18 is connected to the input side. The male spline part formed in the axial direction other end part of the outer peripheral surface of the rotating shaft 1c is engaged with the spline.

  Further, a locking groove 20 is formed in the other end portion in the axial direction of the input rotary shaft 1 a than the portion where the inner diameter side cylinder element 18 is fitted, and the locking groove 20 is locked in the locking groove 20. The ring 21 is locked. Then, one axial end surface of the locking ring 21 is abutted against the other axial end surface of the inner diameter side portion of the inner diameter side cylinder element 18 so that the cylinder 17 moves away from the input side disk 2c (in FIG. 1). To the left). Therefore, the inner diameter side cylinder element 18 is rattled in a state where torque can be transmitted to the portion near the other end in the axial direction of the input rotary shaft 1a and displacement to the other end in the axial direction is prevented. It has been fitted outside.

  The locking ring 21 is formed by combining a plurality of (for example, 2 to 4) partial arc-shaped elements in the circumferential direction. The locking ring 21 is configured. In addition, in order to prevent a plurality of elements constituting the locking ring 21 from coming out radially outward from the locking groove 20, the periphery of each element is covered with a restraining ring 22. In the case of the illustrated structure, the restraining ring 22 is rotationally driven by a power source such as an engine, and the driving torque transmitted to the restraining ring 22 is transmitted via the cylinder 17 to the input rotary shaft 1a and the It is configured to transmit to the input side disk 2c.

  Further, two piston plates 23 a and 23 b are assembled in the cylinder 17. Then, a portion between the piston plate 23a on the other end side in the axial direction and the bottom plate portion 24 of the cylinder 17 and a portion between the piston plate 23b on the one end side in the axial direction and the input side disk 2c are respectively provided in the hydraulic chamber 25a. 25b constitutes the double piston type pressing device 10a. Then, by introducing a predetermined hydraulic pressure into each of the hydraulic chambers 25a and 25b, the input-side disk 2c on the other axial end side is directed toward the input-side disk 2d on one axial end side, and the hydraulic pressure is reduced. It can be pressed with a force according to the size.

  On the other hand, one of the two input-side disks 2c and 2d, which is provided on the right side of FIG. 1 that is one end side (tip side) in the axial direction of the input rotation shaft 1a. The input side disk 2d corresponding to the outer side disk cannot be displaced toward one end in the axial direction, which is a direction away from the input side disk 2c, and can rotate in synchronization with the input rotation shaft 1a. It is supported by the rotating shaft 1a. For this reason, in the case of this example, the portion closer to one end in the axial direction of the input rotary shaft 1a is arranged in order from the other end side in the axial direction to one end side (from left to right in FIG. 1). The shaft portion 27 is configured in a stepped shape in which the shaft side step surface 28 is continuous. Of these, the outer peripheral surface of the small-diameter shaft portion 26 is an inner cylinder whose cross-sectional shape with respect to a virtual plane orthogonal to the central axis of the input rotary shaft 1a is a perfect circular shape without distortion and whose outer diameter does not change in the axial direction. The surface portion 29 is used. Further, a male spline portion 30 having an outer diameter dimension larger than that of the remaining portion of the large diameter shaft portion 27 is provided at an axially intermediate portion of the large diameter shaft portion 27. In the illustrated example, a relief groove 31 that is recessed inward in the radial direction is provided over the entire circumference in a portion of the large-diameter shaft portion 27 adjacent to one end side in the axial direction of the male spline portion 30. ing. The shaft-side step surface 28 exists on a virtual plane orthogonal to the central axis of the input rotation shaft 1a.

  A central hole 32 penetrating in the axial direction is formed in the center of the input side disk 2d so as to pass through the input side rotating shaft 1a. The center hole 32 has a small-diameter hole portion 33 and a medium-diameter hole portion 34 that are continued from the other end side in the axial direction to one end side (from left to right in FIGS. The medium-diameter hole 34 and the large-diameter hole 36 are configured in a stepped shape in which the disk-side flat surface 37 is continuous. A female spline portion 38 that can be spline-engaged with the male spline portion 30 is provided at an intermediate portion in the axial direction of the medium diameter hole portion 34. The inner peripheral surface of the small-diameter hole portion 33 is an outer cylindrical surface portion 39 having an inner diameter smaller than the diameter of the inscribed circle of the female spline portion 38. The outer cylindrical surface portion 39 has a cross-sectional shape with respect to a virtual plane orthogonal to the central axis of the input-side disk 2d, which is a regular circular shape without distortion, and the outer diameter dimension does not change in the axial direction. The inner diameter of the outer cylindrical surface portion 39 in a free state is slightly smaller than the outer diameter of the inner cylindrical surface portion 29 in a free state. Further, the disk-side step surface 35 and the disk-side flat surface 37 exist on a virtual plane orthogonal to the central axis of the input-side disk 2d.

  In the assembled state of the toroidal-type continuously variable transmission 13, an axial side step surface 28 formed on the outer peripheral surface of the input rotary shaft 1a and a disk side step surface 35 formed on the inner peripheral surface of the input side disc 2d are axially arranged. The male spline portion 30 and the female spline portion 38 are spline-engaged with each other in a state where the input side disk 2d is positioned with respect to the input side rotation shaft 1a. The inner cylindrical surface 29 and the outer cylindrical surface portion 39 are fitted (press-fit, inlay fitting) by interference fitting. With such a configuration, the input side disk 2d is rotated in synchronization with the input rotary shaft 1a in a state in which the input side disc 2d is prevented from being displaced toward one end side in the axial direction with respect to a portion near the one end of the input rotary shaft 1a. I support it as possible.

  Further, in order to supply lubricating oil to the spline engaging portion 40 of the male spline portion 30 and the female spline portion 38, a main lubricating oil passage 41 extending in the axial direction is provided inside the input rotary shaft 1a. The auxiliary lubricating oil passage 42 is provided in a state where the main lubricating oil passage 41 branches in a radial direction from a part of the axial direction of the main lubricating oil passage 41. Then, the downstream end portion of the sub-lubricating oil passage 42 is moved from the portion where the male spline portion 30 is provided to the other side in the axial direction on the outer peripheral surface of the large-diameter shaft portion 27 of the input-side rotary shaft 1a. Open in the detached part. For this reason, in the case of this example, the lubricating oil fed into the main lubricating oil passage 41 of the input rotary shaft 1a passes through the auxiliary lubricating oil passage 42 as shown by the arrow in FIG. In an annular oil retaining space 43 provided in a state adjacent to the other axial end side of the spline engaging portion 40 in a portion between the outer peripheral surface of the side rotating shaft 1a and the inner peripheral surface of the input side disk 2d. It is sent. The lubricating oil that has passed through the annular oil retaining space 43 passes through the spline engaging portion 40 from the other end in the axial direction toward one end (from the left side to the right side in FIGS. 1 to 3). The engaging portion 40 is lubricated. In the case of this example, the lubricating oil supplied to the annular oil retaining space 43 is supplied to the other side in the axial direction by a press-fitting portion (fitting portion) between the inner cylindrical surface 29 and the outer cylindrical surface portion 39. Since leakage is prevented, the spline engaging portion 40 can be efficiently supplied.

  Particularly in the case of this example, the lubricating oil damming member 14 is supported and fixed to the input side disk 2d for the purpose of efficiently lubricating the spline engaging portion 40. The lubricating oil damming member 14 is made of an elastic material, and is configured in a circular plate shape as a whole, and is adjacent to one axial end of the female spline portion 38 in the center hole 32 of the input side disk 2d. It is supported and fixed to the part. More specifically, the lubricating oil damming member 14 is a latch formed in a portion adjacent to one end side in the axial direction of the female spline portion 38 in the medium diameter hole portion 34 constituting the center hole 32. An outer diameter side portion of the groove 44 is locked. For this reason, the lubricating oil blocking member 14 is supported by a portion adjacent to the downstream side with respect to the spline engaging portion 40 in the flow direction of the lubricating oil. Further, in this state, the other axial side surface of the lubricating oil damming member 14 is in contact with one axial end surface of the female spline portion 38. However, in the case of this example, the shaft of the male spline portion 30 constituting the spline engaging portion 40 in a state where the shaft side step surface 28 and the disk side step surface 35 are in contact with each other in the axial direction. Since one end surface in the direction is positioned on the other side in the axial direction with respect to the one end surface in the axial direction of the female spline portion 38, the other axial direction side surface of the lubricating oil damming member 14 and the axial direction of the male spline portion 30 are the same. Between the end faces, a slight gap 45 in the axial direction is formed over the entire circumference.

Further, as shown in FIG. 4, of the lubricating oil damming member 14, the outer diameter D is sufficiently than the tooth bottom circle diameter df ₄₆ of the internal spline 46, 46 which constitutes the female spline portion 38 The inner diameter dimension d is smaller than the root circle diameter df _{47 of} the male spline teeth _{47, 47} constituting the male spline portion 30. For this reason, in the lubricating oil damming member 14, the outer peripheral edge O is located radially outside the root circle of the female spline teeth 46, 46, and the inner peripheral edge I is the male spline. The teeth 47 and 47 are located radially inward from the root circle.

  Therefore, the lubricating oil blocking member 14 is formed (defined) between the tooth bottom surface of the female spline teeth 46 and 46 and the tooth tip surface of the male spline teeth 47 and 47. (Or a triangular shape) of the outer-diameter-side lubricating oil passages 48, 48 is located at a portion adjacent to one axial end of the opening (exit side) opening in the axial direction. For this reason, the axially one end side (outlet side) opening of each of the outer diameter side lubricating oil passages 48, 48 has the entire range extending from the outer side in the radial direction to the inner side of the lubricating oil damming member 14. The portion is blocked (damped) in the axial direction by the portion. However, in the case of this example, since the gap 45 is provided between the other axial side surface of the lubricating oil damming member 14 and the one axial end surface of the male spline portion 30, each outer diameter is The lubricating oil that passes through the side lubricating oil passages 48, 48 is not completely discharged from the opening on the one axial end side (exit side), but can be discharged little by little through the gap 45.

  Similarly, the lubricating oil blocking member 14 is formed (defined) between the tooth tip surfaces of the female spline teeth 46 and 46 and the tooth bottom surfaces of the male spline teeth 47 and 47. It is located in the part adjacent to the axial direction one end side of the axial direction one end side (outlet side) opening part of the internal diameter side lubricating oil flow paths 49 and 49 of reverse triangle shape (or rectangular shape). For this reason, the axially one end side (exit side) opening of each of the inner diameter side lubricating oil passages 49, 49 has a whole range extending from the outer side in the radial direction to the inner side by the inner diameter side portion of the lubricating oil damming member 14. It becomes a state of being blocked (dammed) in the axial direction. However, in the case of this example, the gap 45 is provided between the other axial side surface of the lubricating oil damming member 14 and the one axial end surface of the male spline portion 30, so that each inner diameter side The lubricating oil passing through the lubricating oil passages 49, 49 is not completely discharged from the opening on the one axial end side (outlet side), but can be discharged little by little through the gap 45.

Furthermore, in the case of this example, the inner diameter dimension d of the lubricating oil damming member 14 is set to the male diameter portion 27 of the large-diameter shaft portion 27 of the input rotary shaft 1a in both the free state and the assembled state. It is set to be larger than the outer diameter dimension D _{27 of the} axial one end side portion (the tip side portion, the right side portion in FIGS. As a result, in the assembled state, the lubricating oil is passed between the inner peripheral surface of the lubricating oil damming member 14 and the outer peripheral surface of the input rotating shaft 1a (the escape groove 31) toward one end in the axial direction. A clearance is provided for this purpose. The outer diameter dimension D of the lubricating oil damming member 14 is the inner diameter of the medium-diameter hole portion 34 (the portion removed from the portion where the locking groove 44 is provided) in the center hole 32 of the input side disk 2d. It is set to be larger than the dimension d _{34 and} smaller than the inner diameter dimension of the large-diameter hole portion 36.

  When assembling the toroidal continuously variable transmission 13 of this example having the above-described configuration, the input side disk 2d, the output side disk 6a, the input side disk 2c, and the pressing device 10a are arranged in this order. And inserted from the other axial end of the input rotary shaft 1a and assembled to the input rotary shaft 1a. In the case of this example, when the input side disk 2d is attached to a portion near one end in the axial direction of the input side rotating shaft 1a, the fitting portion between the inner cylindrical surface 29 and the outer cylindrical surface portion 39 causes the Since the input side disk 2d can be centered, the female spline portion 38 can be easily splined to the male spline portion 30.

  Further, in the case of this example, the lubricating oil damming member 14 is assembled from one axial end side of the input rotary shaft 1a. Specifically, the lubricating oil damming member 14 is moved around the input rotary shaft 1a from one end side in the axial direction to the other end side, and the outer diameter side portion is moved to the center hole of the input side disk 2d. It is locked in a locking groove 44 provided in 32. In order to pass the inside of the medium diameter hole 34 in the center hole 32, for example, the lubricating oil damming member 14 is arranged such that the outer diameter side portion is closer to one end in the axial direction than the inner diameter side portion. By tilting (twisting) so as to be positioned, the outer diameter dimension is made smaller than the inner diameter dimension of the medium-diameter hole portion 34, or the entire lubricating oil damming member 14 is elastically reduced in diameter. The outer diameter is made smaller than the inner diameter of the medium diameter hole 34.

According to the toroidal type continuously variable transmission 13 of the present example having the above-described configuration, the spline engaging portion 40 between the input rotary shaft 1a and the input side disk 2d can be efficiently lubricated with lubricating oil.
That is, in the case of this example, the lubricating oil, which is formed in an annular shape as a whole in a portion adjacent to the female spline portion 38 on the downstream side with respect to the flow direction of the lubricating oil in the input side disk 2d. The damming member 14 is supported, and the inner diameter d of the lubricating oil damming member 14 is set to a root circle diameter df ₄₆ , a tip circle diameter da _{46 of} the female spline teeth 46, ₄₆ , and the above-mentioned The male spline teeth ₄₇ are smaller than the root diameter df ₄₇ of the teeth ₄₇ (d <df ₄₇ <da ₄₆ <df ₄₆ ). Therefore, in the case of this example, the lubricating oil damming member 14 causes the outer diameter side lubricating oil passages 48 and 48 and the inner diameter side lubricating oil passages 49 and 49 to be at one end side in the axial direction (outlet). Side) The entire opening can be closed in the axial direction. Accordingly, the lubricating oil supplied through the main lubricating oil passage 41, the auxiliary lubricating oil passage 42, and the annular oil retaining space 43 provided inside the input side rotating shaft 1a is radially outward by the action of centrifugal force. Even in the case of movement, it is possible to prevent the lubricating oil from intensively passing through the outer diameter side lubricating oil channels 48, 48 (the amount of lubricating oil passing through the outer diameter side lubricating oil channels 48, 48 is reduced). Can do it). Further, in the case of this example, since the lubricating oil can intensively pass through the respective inner diameter side lubricating oil passages 49, 49, the female spline teeth 46, 46 and the male spline teeth 47, 47 Thus, the lubricating oil can be effectively fed into the portion between the tooth surfaces, and the spline engaging portion 40 can be effectively lubricated.

  Furthermore, in the case of the toroidal type continuously variable transmission 13 of this example, the lubricating oil damming member 14 can be easily assembled from the one end side (tip side) in the axial direction of the input rotary shaft 1a. For this reason, it is possible to suppress a decrease in the assemblability of the toroidal continuously variable transmission 13 due to the provision of the lubricating oil damming member 14.

[Second Example of Embodiment]
A second example of the embodiment of the present invention will be described with reference to FIG. The feature of this example is the method of fixing the lubricating oil damming member 14a to the input side disk 2d. That is, in the case of this example, the lubricating oil damming member 14a is supported and fixed to the input side disk 2d by using a retaining ring 50.

  For this reason, in the case of the present embodiment, in the middle diameter hole portion 34 constituting the center hole 32 of the input side disk 2d, the portion adjacent to one end side in the axial direction of the female spline portion 38 is used in the above embodiment. No locking groove 44 (see FIGS. 1 to 3) for locking the outer diameter side portion of the lubricating oil damming member 14a, as in the case of the first example of FIG. A locking groove 44a for locking the retaining ring 50 is formed. Further, in the case of this example, the lubricating oil damming member 14a is made of an elastic material or metal, and the outer diameter of the lubricating oil damming member 14a is a portion on the one end side in the axial direction from the female spline portion 38 of the medium diameter hole portion 34 ) Is set slightly smaller than the inner diameter dimension. On the other hand, the retaining ring 50 is, for example, in the shape of a ring shape (C shape) and can be reduced in diameter relatively easily.

In the case of this example having the above-described configuration, the lubricating oil damming member 14a is inclined or elastically deformed even when the lubricating oil damming member 14a passes through the inside of the medium diameter hole 34. You do n’t have to. In order to lock the retaining ring 50 in the retaining groove 44a, it is necessary to pass the retaining ring 50 through the inside of the medium-diameter hole 34. There is no need to reduce the inner diameter dimension unlike the oil damming member 14a. For this reason, the operation of locking the retaining ring 50 in the locking groove 44a through the medium diameter hole 34 can be easily performed. Therefore, in the case of this example, the assembly work efficiency of the toroidal type continuously variable transmission 13 can be improved.
About another structure and an effect, it is the same as that of the case of the 1st example of the said embodiment.

[Third example of embodiment]
A third example of the embodiment of the present invention will be described with reference to FIG. The feature of this example is also in the fixing method of the lubricating oil damming member 14b to the input side disk 2d. That is, in the case of this example, the lubricating oil damming member 14b is supported and fixed to the input disk 2d by using the fixing screw 51.

  Therefore, in the case of this example, a female spline portion 38a is formed at one axial end portion of the medium diameter hole portion 34 constituting the center hole 32 of the input side disk 2d. The lubricating oil blocking member 14 b is supported and fixed to the disk-side flat surface 37 constituting the center hole 32 by a plurality of fixing screws 51. Specifically, the other axial end portion (tip portion) of the fixing screw 51 inserted in the axial direction through a portion near the outer diameter of the lubricating oil blocking member 14 b is screwed into the disk-side flat surface 37. doing. In the case of this example, the lubricating oil damming member 14b is made of metal, and the outer diameter of the lubricating oil damming member 14b is the medium diameter hole 34 (of the other end in the axial direction from the female spline 38a). Is set to be sufficiently larger than the inner diameter dimension.

In the case of this example having the above-described configuration, the lubricating oil damming member 14b can be easily supported and fixed from one axial end side of the input side disk 2d using a tool (not shown) such as a driver. Therefore, the assembly work efficiency of the toroidal type continuously variable transmission 13 can be improved. Further, since the lubricating oil damming member 14b is easily visible from the outside after the assembly is completed, it is possible to prevent forgetting to assemble the lubricating oil damming member 14b.
About another structure and an effect, it is the same as that of the case of the 1st example of the said embodiment.

[Fourth Example of Embodiment]
A fourth example of the embodiment of the present invention will be described with reference to FIG. The feature of this example is also in the fixing method of the lubricating oil damming member 14c to the input side disk 2d. That is, in the case of this example, the lubricating oil damming member 14c is directly supported and fixed by press-fitting into the input side disk 2d.

  For this reason, in the case of the present embodiment, in the middle diameter hole portion 34 constituting the center hole 32 of the input side disk 2d, the portion adjacent to one end side in the axial direction of the female spline portion 38 is used in the above embodiment. As in the case of the first example, the female spline portion 38 is formed without forming a locking groove 44 (see FIGS. 1 to 3) for locking the outer diameter side portion of the lubricating oil damming member 14a. A portion on one end side in the axial direction from the portion provided with is a fitting cylindrical surface 52 whose inner diameter dimension does not change in the axial direction. In the case of this example, the lubricating oil damming member 14 c is made of an elastic material or metal, and its outer diameter is slightly larger than the inner diameter of the fitting cylindrical surface 52.

In the case of this example having the above-described configuration, the fitting cylinder is inserted from one end in the axial direction of the input side disk 2d while elastically deforming the lubricating oil damming member 14c without using a tool or the like. By pushing into the surface portion 52, the lubricating oil blocking member 14c can be easily supported and fixed to the input side disk 2d. For this reason, also in the case of this example, the assembly work efficiency of the toroidal-type continuously variable transmission 13 can be improved. Also in the case of this example, since the lubricating oil damming member 14c is easily visible from the outside after the assembly is completed, it is possible to prevent forgetting to attach the lubricating oil damming member 14c. In addition, by reducing the inner diameter of the fitting cylindrical surface toward the one end in the axial direction, it is possible to effectively prevent the lubricating oil damming member from being displaced toward the one end in the axial direction regardless of the pressing force by the lubricating oil. You can also do things.
About another structure and an effect, it is the same as that of the case of the 1st example of the said embodiment.

[Fifth Example of Embodiment]
A fifth example of the embodiment of the present invention will be described with reference to FIG. The feature of this example is that the lubricating oil blocking member 14d is supported not on the input side disk 2e but on the input side rotating shaft 1b. That is, in this example, the lubricating oil damming member 14d is fastened to a portion of the outer peripheral surface of the input rotary shaft 1b adjacent to one end in the axial direction of the portion where the male spline portion 30 is provided. It is fitted and fixed (press-fit) by fitting. In this state, a minute gap is provided between the outer peripheral surface of the lubricating oil damming member 14d and the medium diameter hole 34 of the input side disk 2e. For this reason, the lubricating oil damming member 14 d is a clearance fit with the medium diameter hole 34.

  In the case of this example, the lubricating oil damming member 14d is made of an elastic material or metal, and oil passage grooves 52, 52 that are recessed radially outward are formed on the inner circumferential surface thereof in the circumferential direction. Are provided at equal intervals. These oil passage grooves 52, 52 are provided over the entire length in the axial direction on the inner peripheral surface of the lubricating oil damming member 14d. In the case of this example, the cross-sectional shape of each oil passage groove 52, 52 is substantially semicircular, and the diameter of the circumscribed circle passing through the bottom of each oil passage groove 52, 52 is the input value. It is made smaller than the diameter of the tip circle of the female spline teeth 46 constituting the female spline portion 38 provided on the side disk 2e. The lubricating oil damming member 14d having such a configuration can be easily assembled from one axial end side of the input rotary shaft 1b.

  In the case of this example having the above-described configuration, the lubricating oil damming member 14 d causes the bottom surface of the female spline teeth 46 and the tip surface of the male spline teeth 47 constituting the male spline portion 30 to be formed. The entire opening at one end side (outlet side) in the axial direction of the outer diameter side lubricating oil passage 48 (see FIG. 4) having a substantially rectangular (or triangular) cross section formed therebetween can be closed in the axial direction. . Further, the lubricating oil damming member 14d forms a substantially inverted triangular (or rectangular) inner diameter side formed between the tip surface of the female spline tooth 46 and the bottom surface of the male spline tooth 47. Of the opening on the one end side (outlet side) in the axial direction of the lubricating oil flow path 49 (see FIG. 4), a portion that does not overlap with the oil passage grooves 52, 52 in the axial direction can be blocked in the axial direction.

  Accordingly, even when the lubricating oil supplied through the inside of the input side rotating shaft 1b moves radially outward due to the action of centrifugal force, the lubricating oil concentrates on each outer diameter side lubricating oil flow path 48. It can be prevented from passing (the amount of lubricating oil passing through the outer diameter side lubricating oil passage 48 can be reduced). Further, since the lubricating oil can intensively pass through each of the inner diameter side lubricating oil flow paths 49, the lubricating oil is effectively applied to the portion between the tooth surfaces of the female spline teeth 46 and the male spline teeth 47. The spline engaging portion 40 can be effectively lubricated. In the case of this example, the lubricating oil discharged into the gap 45 between the other axial end surface of the lubricating oil blocking member 14d and the one axial end surface of the male spline portion 30 It is discharged to one end side in the axial direction through 52 and 52.

Although not shown, a portion between the other end surface in the axial direction of the lubricating oil blocking member 14d and one end surface in the axial direction of the female spline portion 38 {a portion surrounded by a broken line in FIG. 8A}. Is sandwiching a sealing member such as an O-ring (not shown), and the lubricating oil discharged into the gap 45 is between the outer peripheral surface of the lubricating oil damming member 14d and the medium diameter hole 34 of the input side disk 2e. It is possible to adopt a configuration that prevents the air from flowing into the device. In the case of providing such a seal member, a seal recess opened in the axial direction on one of the other axial end surface of the lubricating oil damming member 14d and one axial end surface of the female spline portion 38 is provided. Grooves (notches) can be provided.
About another structure and an effect, it is the same as that of the case of the 1st example of the said embodiment.

[Sixth Example of Embodiment]
A sixth example of the embodiment of the present invention will be described with reference to FIG. The feature of this example is a metal circle formed of at least one turn (1 turn in the illustrated example) of a metal wire having a circular cross section or a rectangular cross section as shown in FIG. 9 as the lubricating oil blocking member 14e. It is in the point of using a ring material.

In the case of this example having the above-described configuration, it is possible to reduce the manufacturing cost of the lubricating oil damming member 14e. In addition, since the lubricating oil damming member 14e can be elastically deformed with a relatively small force, the mounting work efficiency can be improved.
About another structure and an effect, it is the same as that of the case of the 1st example of the said embodiment.

  The present invention is not limited to the half toroidal type as shown in the figure, and can be implemented by a full toroidal type toroidal continuously variable transmission. In carrying out the present invention, the support structure of the lubricating oil damming member with respect to the input side disk (outer disk) and the rotating shaft is not limited to the structure of each example of the embodiment as described above. Various support structures known from can be adopted. Further, the shape of the lubricating oil blocking member is not limited to the shape of each example of the above embodiment, and other shapes can be adopted as long as the function can be secured. In each example of the above embodiment, the case where the pair of outer disks are input side disks for inputting power and the inner disk is an output side disk for outputting power has been described. On the contrary, the inner disk may be an input side disk for inputting power, and the pair of outer disks may be an output side disk for outputting power. Furthermore, the structures of the examples of the above-described embodiments can be implemented in appropriate combination.

DESCRIPTION OF SYMBOLS 1, 1a, 1b Input rotary shaft 2a, 2b, 2c, 2d, 2e Input side disk 3 Ball spline 4 Output cylinder 5 Output gear 6, 6a Output side disk 7 Power roller 8 Trunnion 9 Drive shaft 10, 10a Pressing device 11a, 11b Preload spring 12 Loading nut 13 Toroidal side continuously variable transmission 14, 14a-14e Lubricating oil damming member 15 Actuator case 16 Strut 17 Cylinder 18 Inner diameter side cylinder element 19 Outer diameter side cylinder element 20 Locking groove 21 Locking ring 22 Retaining ring 23a, 23b Piston plate 24 Bottom plate portion 25a, 25b Hydraulic chamber 26 Small-diameter shaft portion 27 Large-diameter shaft portion 28 Axial step surface 29 Inner cylindrical surface portion 30 Male spline portion 31 Escape groove 32 Central hole 33 Small-diameter hole portion 34 Medium diameter hole 35 Disc side step surface 36 Large diameter hole 37 D Disk side flat surface 38, 38a Female spline part 39 Outer cylindrical surface part 40 Spline engaging part 41 Main lubricating oil flow path 42 Sub lubricating oil flow path 43 Annular oil retaining space 44 Engaging groove 43 Annular oil retaining space 44 Engaging groove 45 Clearance 46 Female spline teeth 47 Male spline teeth 48 Outer diameter side lubricating oil flow path 49 Inner diameter side lubricating oil flow path 50 Retaining ring 51 Fixing screw 52 Oil passage groove

Claims (3)

A rotating shaft provided with a male spline portion on one end side in the axial direction of the outer peripheral surface;
A pair of outer disks each supported by the rotary shaft to be able to rotate in synchronization with the rotary shaft in a state where the axial side surfaces of the arcuate cross section are opposed to each other;
An inner side that is supported so as to be capable of relative rotation with respect to the rotational axis around an axially intermediate portion of the rotating shaft with both axial side surfaces of the arcuate cross section facing the axial side surface of the pair of outer disks. A disc,
A plurality of power rollers having respective circumferential surfaces abutting against both axial side surfaces of the inner disk and axial side surfaces of the pair of outer disks;
An inner diameter smaller than the diameter of the root circle of the female spline teeth constituting the female spline portion formed on one outer disk provided on one axial end side of the pair of outer disks. A dimension of the one outer disk or the rotating shaft, and the direction of the lubricating oil flowing through the spline engaging portion between the female spline portion and the male spline portion in the axial direction is lubricated. A toroidal continuously variable transmission comprising: a lubricating oil damming member supported by a portion adjacent to the downstream side of the spline engaging portion.   2. The toroidal continuously variable transmission according to claim 1, wherein an inner diameter dimension of the lubricating oil blocking member is smaller than a tip diameter of the female spline teeth.   The lubricating oil damming member is supported on a portion of the one outer disk adjacent to one end side in the axial direction of the female spline portion, and the inner diameter dimension of the lubricating oil damming member is equal to that of the rotating shaft. The toroidal continuously variable transmission according to claim 1, wherein the outer diameter dimension of a portion existing on one end side in the axial direction is larger than a portion where the male spline portion is formed.

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