JP2007051658A - Toroidal type continuously variable transmission - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To provide a toroidal type continuously variable transmission capable of effectively eliminating foreign matters in a lubricant. <P>SOLUTION: This toroidal type continuously variable transmission comprises a first oil passage 90 for supplying the lubricant into a trunnion 15, a second oil passage 90b branched from the first oil passage 90 and supplying the lubricant to a traction face formed between an input-side disc and an output-side disc, and a power roller 11 through the trunnion 15, third oil passages 90a, 100 branched from the first oil passage 90 and supplying the lubricant to a bearing 24 through the trunnion 15 and a displacement shaft 23, a first filter 200 disposed in the first oil passage 90, and second filters 210 disposed in the third oil passages 90a, 100. A mesh size of the second filters is smaller than that of the first filter 200. <P>COPYRIGHT: (C)2007,JPO&INPIT

Description

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

  For example, a double-cavity toroidal continuously variable transmission used as a transmission for an automobile is configured as shown in FIGS. As shown in FIG. 4, an input shaft (center shaft) 1 is rotatably supported inside the casing 50, and two input side disks 2, 2 and two outputs are provided on the outer periphery of the input shaft 1. Side disks 3 and 3 are attached. An output gear 4 is rotatably supported on the outer periphery of the intermediate portion of the input shaft 1. Output side disks 3 and 3 are connected to cylindrical flange portions 4a and 4a provided at the center of the output gear 4 by spline coupling.

  The input shaft 1 is rotationally driven by a drive shaft 22 via a loading cam type pressing device 12 provided between an input side disk 2 and a cam plate 7 located on the left side in the drawing. . The output gear 4 is supported in the casing 50 via a partition wall 13 formed by coupling two members, so that the output gear 4 can rotate around the axis O of the input shaft 1 while the axis O. Directional displacement is prevented.

  The output side disks 3 and 3 are supported by needle bearings 5 and 5 interposed between the input shaft 1 so as to be rotatable about the axis O of the input shaft 1. Further, the left input side disk 2 in the figure is supported on the input shaft 1 via a ball spline 6, and the right side input disk 2 in the figure is splined to the input shaft 1. Rotates with the input shaft 1. A power roller 11 (see FIG. 5) is rotatable between the inner side surfaces (concave surfaces) 2a and 2a of the input side disks 2 and 2 and the inner side surfaces (concave surfaces) 3a and 3a of the output disks 3 and 3. It is pinched.

  A step 2b is provided on the inner peripheral surface 2c of the input disk 2 located on the right side in FIG. 4, and the step 1b provided on the outer peripheral surface 1a of the input shaft 1 is abutted against the step 2b. At the same time, the back surface (the right surface in FIG. 4) of the input side disk 2 is abutted against the loading nut 9. Thereby, the displacement of the input side disk 2 in the direction of the axis O with respect to the input shaft 1 is substantially prevented. Further, a disc spring 8 is provided between the cam plate 7 and the flange 1d of the input shaft 1, and this disc spring 8 is a concave surface 2a, 2a, 3a of each disk 2, 2, 3, 3. , 3a and the contact surface between the peripheral surfaces 11a and 11a of the power rollers 11 and 11 are applied with a pressing force.

  As shown in FIG. 5 which is a cross-sectional view taken along the line C-C of FIG. 4, both the disks 3 and 3 are sandwiched from both sides inside the casing 50 and at the side positions of the output side disks 3 and 3. The pair of yokes 23A and 23B is supported in the state. The pair of yokes 23A and 23B are formed in a rectangular shape by pressing or forging a metal such as steel. In order to support pivots 14 provided at both ends of the trunnion 15 to be described later in a swingable manner, circular support holes 18 are provided at the four corners of the yokes 23A and 23B, and the width direction of the yokes 23A and 23B. A circular locking hole 19 is provided at the center of the.

  The pair of yokes 23 </ b> A and 23 </ b> B are supported so as to be slightly displaceable by support posts 64 and 68 formed on portions of the inner surface of the casing 50 facing each other. These support posts 64 and 68 are provided so as to face the first cavity 221 and the second cavity 222, respectively, between the inner side surface 2a of the input side disk 2 and the inner side surface 3a of the output side disk 3. It has been.

  Accordingly, the yokes 23 </ b> A and 23 </ b> B are supported by the support posts 64 and 68, and their one end faces the outer peripheral portion of the first cavity 221 and the other end is the outer peripheral portion of the second cavity 222. Opposite to.

  Since the first and second cavities 221 and 222 have the same structure, only the first cavity 221 will be described below.

  As shown in FIG. 5, inside the casing 50, the first cavity 221 has a pair of trunnions 15, 15 that swing about a pair of pivots 14, 14 that are twisted with respect to the input shaft 1. Is provided. In addition, illustration of the input shaft 1 is abbreviate | omitted in FIG. Each trunnion 15, 15 is a pair of bent portions formed at both ends in the longitudinal direction (vertical direction in FIG. 5) of the support plate portion 16 that is the main body portion in a state of being bent toward the inner side surface of the support plate portion 16. Wall portions 20 and 20 are provided. The bent wall portions 20 and 20 form concave pocket portions P for accommodating the power rollers 11 in the trunnions 15 and 15. Further, the pivot shafts 14 and 14 are concentrically provided on the outer side surfaces of the bent wall portions 20 and 20, respectively.

  A circular hole 21 is formed in the center portion of the support plate portion 16, and a base end portion (first shaft portion) 23 a of the displacement shaft 23 is supported in the circular hole 21. Then, by swinging each trunnion 15, 15 about each pivot 14, 14, the inclination angle of the displacement shaft 23 supported at the center of each trunnion 15, 15 can be adjusted. In addition, each power roller 11 is rotatably supported around the tip end portion (second shaft portion) 23b of the displacement shaft 23 protruding from the inner surface of each trunnion 15, 15. 11 is sandwiched between the input disks 2 and 2 and the output disks 3 and 3. In addition, the base end part 23a and the front-end | tip part 23b of each displacement shaft 23 and 23 are mutually eccentric.

  As described above, the pivot shafts 14 and 14 of the trunnions 15 and 15 are supported so as to be swingable with respect to the pair of yokes 23A and 23B and displaceable in the axial direction (vertical direction in FIG. 5). The trunnions 15 and 15 are restricted from moving in the horizontal direction by the yokes 23A and 23B. As described above, four circular support holes 18 are provided at the four corners of each of the yokes 23 </ b> A and 23 </ b> B. The pivot shafts 14 provided at both ends of the trunnion 15 are respectively provided in the support holes 18 with the radial needle bearings 30. It is supported so as to be able to swing through. Further, as described above, the circular locking hole 19 is provided in the central portion of the yokes 23A and 23B in the width direction (left-right direction in FIG. 5), and the inner peripheral surface of the locking hole 19 is spherical. Support posts 64 and 68 are internally fitted as concave surfaces. That is, the upper yoke 23A is swingably supported by the spherical post 64 supported by the casing 50 via the fixing member 52, and the lower yoke 23B is supported by the spherical post 68 and the drive for supporting the same. The upper cylinder body 61 of the cylinder 31 is swingably supported.

  The displacement shafts 23 and 23 provided in the trunnions 15 and 15 are provided at positions 180 degrees opposite to the input shaft 1. Further, the direction in which the distal end portion 23b of each of the displacement shafts 23, 23 is eccentric with respect to the base end portion 23a is the same direction as the rotational direction of both the disks 2, 2, 3, 3 (in FIG. (Reverse direction). Further, the eccentric direction is a direction substantially orthogonal to the direction in which the input shaft 1 is disposed. Accordingly, the power rollers 11 and 11 are supported so that they can be slightly displaced in the longitudinal direction of the input shaft 1. As a result, even if each power roller 11, 11 tends to be displaced in the axial direction of the input shaft 1 due to elastic deformation of each component member based on the thrust load generated by the pressing device 12, each component This displacement is absorbed without applying an excessive force to the member.

  Further, between the outer surface of the power roller 11 and the inner surface of the support plate portion 16 of the trunnion 15, a thrust ball bearing 24, which is a thrust rolling bearing, and a thrust needle bearing are sequentially arranged from the outer surface side of the power roller 11. 25. Among these, the thrust ball bearing 24 supports the rotation of each power roller 11 while supporting the load in the thrust direction applied to each power roller 11. Each of the thrust ball bearings 24 is composed of a plurality of balls 26, 26, an annular retainer 27 for holding the balls 26, 26 in a freely rolling manner, and an annular outer ring 28. ing. Further, the inner ring raceway of each thrust ball bearing 24 is formed on the outer side surface (large end surface) of each power roller 11, and the outer ring raceway is formed on the inner side surface of each outer ring 28.

  The thrust needle bearing 25 is sandwiched between the inner surface of the support plate portion 16 of the trunnion 15 and the outer surface of the outer ring 28. Such a thrust needle bearing 25 supports the thrust load applied to each outer ring 28 from the power roller 11, while the power roller 11 and the outer ring 28 swing around the base end portion 23 a of each displacement shaft 23. Allow.

  Further, drive rods (shaft portions extending from the pivot shaft) 29 and 29 are provided at one end portions (lower end portions in FIG. 5) of the trunnions 15 and 15, respectively, and outer peripheral surfaces of intermediate portions of the drive rods 29 and 29 are provided. The drive pistons (hydraulic pistons) 33, 33 are fixedly provided. Each of these drive pistons 33 and 33 is oil-tightly fitted in a drive cylinder 31 constituted by an upper cylinder body 61 and a lower cylinder body 62. The drive pistons 33 and 33 and the drive cylinder 31 constitute a drive device 32 that displaces the trunnions 15 and 15 in the axial direction of the pivots 14 and 14 of the trunnions 15 and 15.

  In the case of the toroidal continuously variable transmission configured as described above, the rotation of the drive shaft 22 is transmitted to the input side disks 2 and 2 and the input shaft 1 via the pressing device 12. Then, the rotation of the input side disks 2 and 2 is transmitted to the output side disks 3 and 3 via the pair of power rollers 11 and 11, and the rotation of the output side disks 3 and 3 is further transmitted to the output gear 4. It is taken out more.

  When changing the rotational speed ratio between the input shaft 1 and the output gear 4, the pair of drive pistons 33, 33 are displaced in opposite directions. As the drive pistons 33 and 33 are displaced, the pair of trunnions 15 and 15 are displaced in directions opposite to each other. For example, the power roller 11 on the left side in FIG. 5 is displaced to the lower side in the figure, and the power roller 11 on the right side in the figure is displaced to the upper side in the figure. As a result, the peripheral surfaces 11a and 11a of the power rollers 11 and 11 act on contact portions of the input side disks 2 and 2 and the inner side surfaces 2a, 2a, 3a and 3a of the output side disks 3 and 3, respectively. The direction of the tangential force changes. As the force changes, the trunnions 15 and 15 swing in opposite directions around the pivots 14 and 14 pivotally supported by the yokes 23A and 23B.

  As a result, the contact position between the peripheral surfaces 11a and 11a of the power rollers 11 and 11 and the inner surfaces 2a and 3a changes, and the rotational speed ratio between the input shaft 1 and the output gear 4 changes. Further, when the torque transmitted between the input shaft 1 and the output gear 4 fluctuates and the amount of elastic deformation of each component changes, the power rollers 11 and 11 and the outer rings attached to the power rollers 11 and 11 will be described. 28 and 28 slightly rotate around the base end portions 23a and 23a of the displacement shafts 23 and 23, respectively. Since the thrust needle bearings 25 and 25 exist between the outer side surfaces of the outer rings 28 and 28 and the inner side surfaces of the support plate portions 16 constituting the trunnions 15 and 15, respectively, the rotation is performed smoothly. Is called. Therefore, as described above, the force for changing the inclination angle of each displacement shaft 23, 23 can be small.

  By the way, in such a toroidal-type continuously variable transmission, power transmission between the power roller 11 and the input / output side disks 2 and 3 is non-contact by a traction force through an oil film in order to prevent damage to the surface of these members. It is done in. Therefore, a sufficient amount of lubricating oil (traction oil) that can form an oil film for transmitting torque in a non-contact manner is supplied to the traction surface formed between the power roller 11 and the input / output side disks 2 and 3. In addition, it is necessary to sufficiently lubricate the bearings (hereinafter also referred to as power roller bearings) that rotatably support the disks 2 and 3 and the power roller 11 (for example, Patent Documents). 1).

JP 2004-232677 A

  Generally, lubricating oil (traction oil) is supplied to a traction surface and a power roller bearing portion by an oil pump. A filter for removing foreign matter such as metal wear powder (hereinafter referred to as “contamination”) is generally installed near the supply and discharge port of the oil pump. Contamination (contamination) may be mixed and the contamination may be caught in a contact portion such as a power roller bearing.

  The present invention has been made in view of the above circumstances, and an object of the present invention is to provide a toroidal continuously variable transmission that can effectively remove foreign matters in lubricating oil.

To achieve the above object, the toroidal continuously variable transmission according to claim 1 rotates concentrically and with an input shaft to which rotational torque is input and respective inner surfaces facing each other. An input-side disk and an output-side disk that are freely supported by the input shaft, a trunnion that swings about a pivot that is twisted with respect to the central axis of the input-side disk and the output-side disk, A power roller sandwiched between the input-side disk and the output-side disk in a state of being rotatably supported by a supported displacement shaft; and a power roller provided between the power roller and the trunnion A toroidal continuously variable transmission having a bearing for supporting a thrust load applied to the
A first oil passage for supplying lubricating oil into the trunnion;
A second oil passage that branches from the first oil passage and supplies lubricating oil to the traction surface formed between the input side disk, the output side disk, and the power roller through the trunnion; ,
A third oil passage branched from the first oil passage and supplying lubricating oil to the bearing through the trunnion and the displacement shaft;
A first filter provided in the first oil passage;
A second filter provided in the third oil passage;
It is characterized by having.

  According to a second aspect of the present invention, in the invention described in the first aspect, the second filter has a mesh size smaller than that of the first filter. Features.

  According to the toroidal type continuously variable transmission of the present invention, the first and second filters are installed in the vicinity of the bearing, and filtration is performed in two stages, so that foreign matters in the lubricating oil supplied to the bearing are removed. It can be effectively removed. Furthermore, by making the mesh size of the second filter smaller than the mesh size of the first filter, the cleanliness of the lubricating oil supplied to the bearing can be increased.

  Hereinafter, embodiments of the present invention will be described with reference to the drawings. The feature of the present invention lies in the form of lubricating oil supplied to the trunnion and the disk, and the other configurations and operations are the same as the conventional configurations and operations described above. Therefore, only the features of the present invention will be described below. Reference is made to the other parts, and the same reference numerals as those in FIGS.

  1 to 3 show an embodiment of the present invention. As shown in FIG. 2, in the toroidal type continuously variable transmission according to the present embodiment, the variator including the power roller 11 and the input / output side disks 2 and 3 has a thrust direction applied to the power roller 11. A thrust ball bearing (bearing, power roller bearing) 24 that allows rotation of the power roller 11 while supporting a load, an oil passage for supplying lubricating oil to the trunnion, and the thrust ball branched from the oil passage. An oil passage for supplying the lubricating oil to the bearing 24 and an oil passage branched from the oil passage and for supplying the lubricating oil to the traction surface are provided.

  Specifically, an oil passage (first oil passage) 90 for supplying lubricating oil into the trunnion 15 is provided in the drive rod 29 coupled to one pivot 14 of the trunnion 15. The oil passage 90 is connected to an oil pump (not shown). The oil passage 90 is provided in the trunnion 15, and is provided in the trunnion 15 with an oil passage 90a (third oil passage) communicating with the base end surface of the base end portion 23a of the displacement shaft 23. Branching into an oil passage 90b (second oil passage) having a discharge port 92 facing a traction surface (a peripheral surface 11a of the power roller 11) formed between the output side disk 3 and the power roller 11. . The oil passage 90b and the discharge port 92 are formed in such a direction that the lubricating oil can be reliably supplied to the traction surface of the power roller 11, for example, contact with the disks 2 and 3 on the peripheral surface 11a of the power roller 11. It is preferable that the lubricating oil be sprayed on the extension line of the point S in the circumferential direction.

  On the other hand, the displacement shaft 23 is provided with an oil passage 100 (third oil passage) that communicates with the oil passage 90a and supplies the lubricating oil sent through the oil passage 90a to the thrust ball bearing 24. Specifically, the oil passage 100 includes an oil passage 51 extending along the longitudinal direction in the displacement shaft 23, and a plurality of oils extending in the radial direction from the middle of the oil passage 51 and opening at the outer peripheral surface of the tip portion 23b. And a path 52. The oil passage 51 communicates with the oil passage 90a.

  Further, the oil passage 52 is opened facing the thrust ball bearing 24. The oil passage 51 opens into a gap 53 formed between the tip surface of the tip portion 23 b of the displacement shaft 23 and the power roller 11, and this gap 53 is formed on the tip portion 23 b by the radial needle bearing 38. The annular ball 55 formed between the outer peripheral surface and the power roller 11 communicates with the thrust ball bearing 24 through a gap 57 that is not closed by the radial needle bearing 38.

  Further, a first mesh filter (first filter) 200 is disposed at the downstream end of the oil passage 90 in order to capture foreign matter in the lubricating oil flowing through the oil passage 90. A second mesh filter (second filter) 210 is disposed at the upstream end of the oil passage 100 (oil passage 51) in order to capture foreign matter in the lubricating oil flowing through the oil passage 100. In this case, the mesh size of the second mesh filter 210 is set smaller than that of the first mesh filter 200.

  Therefore, in the above configuration, the lubricating oil supplied into the trunnion 15 through the oil passage 90 is branched after passing through the first mesh filter 200 provided in the oil passage 90 and formed in the trunnion 15. 90a and oil passage 90b. Lubricating oil flowing through the oil passage 90b is jetted from the discharge port 92 formed in the trunnion 15 to the peripheral surface 11a (traction surface) of the power roller 11. On the other hand, the lubricating oil flowing through the oil passage 90a is introduced into the oil passage 51 of the oil passage 100 in the displacement shaft 23 from the base end surface of the base end portion 23a of the displacement shaft 23 after passing through the second mesh filter 210. On the way, it flows to the oil passage 52 and is directly supplied to the thrust ball bearing 24. On the other hand, the lubricating oil that has flowed from the oil passage 51 to the gap 53 flows to the thrust ball bearing 24 through the gap 57 between the outer peripheral surface of the tip end portion 23 b of the displacement shaft 23 and the power roller 11.

  As described above, in the present embodiment, the first and second filters 200 and 210 are installed near the thrust ball bearing 24 and are filtered in two stages. Therefore, the lubricating oil supplied to the thrust ball bearing 24 The foreign matter inside can be effectively removed. On the other hand, the lubricating oil supplied to the traction surface (peripheral surface 11a) of the power roller 11 is included in the lubricating oil because only a part of the lubricating oil is supplied to the actual contact portion (contact point S of the power roller 11). Therefore, it is sufficient to perform filtration using the first filter 200.

Further, since the mesh size of the second filter 210 is smaller than the mesh size of the first filter 200, the cleanliness of the lubricating oil supplied to the thrust ball bearing 24 of the power roller 11 can be increased.
As described above, since only a part of the lubricating oil supplied to the traction surface is supplied to the actual contact portion (contact point S of the power roller 11), the frequency of biting in the contamination contained in the lubricating oil. However, since it is sufficient to remove only excessive contamination, there is no problem even if the mesh size of the first filter 200 is relatively large. On the other hand, since the entire amount of the lubricating oil supplied to the thrust ball bearing 24 passes through the rolling part, the frequency of biting in contamination increases, so it is preferable to mount the second filter 210 having a small mesh size.
When a filter is mounted as in the present embodiment, there is a concern that the amount of lubricating oil supplied will be insufficient due to clogging. However, the amount of lubricating oil passing through the first filter 200 is the same as that supplied to the traction surface Since this is the total amount supplied to the ball bearing 24, it is difficult to reduce the mesh size of the first filter 200. On the other hand, the lubricating oil that passes through the second filter 210 only needs to be supplied to the thrust ball bearing 24, and is oil that has once passed through the first filter 200. Can be made smaller.

  In the power roller 11, the heat source is the thrust ball bearing 24 and the traction surface, while the input / output side disks 2 and 3 are only the traction surface, and the volume of the input / output side disks 2 and 3 is larger. It can be said that the oil passage configuration of the present embodiment that actively lubricates the power roller 11 is desirable from the viewpoint of cooling.

Further, the first oil passage 90 does not spray the lubricating oil locally in the vicinity of the contact point S with the disks 2 and 3 in the power roller 11 as described in the above-mentioned prior art document 1, for example, the power roller 11 Lubricate a wide range of traction surfaces 11 a including contact points between the input / output side disks 2, 3 and the power roller 11, such as spraying lubricating oil on the circumferential extension line of the contact point S with the disks 2, 3. Since the oil is supplied, lubrication and cooling can be reliably performed, and only a part of the supplied lubricating oil reaches the contact point S. Therefore, even if there is a slight amount of foreign matter in the lubricating oil, the frequency with which the foreign matter is bitten at the contact point can be reduced.
Note that, as in Patent Document 1, locally supplying lubricating oil in the vicinity of the contact point S of the power roller 11 with the disks 2 and 3 is generally caused by a shape error or deformation in a toroidal-type continuously variable transmission. Since the contact point moves as viewed from the trunnion because it moves in the axial direction, it is difficult to always spray lubricating oil from the trunnion 15 to the contact point S.

In the above-described embodiment, the first filter 200 is provided at the downstream end portion of the oil passage 90, but the first filter 200 may be installed at another location of the oil passage 90. In the above-described embodiment, the oil passage 90 is provided in the drive rod 29. Instead, the oil passage 90 is provided across the pivot 14 of the trunnion 15 and the shaft portion extending integrally from the pivot 14. Etc.
In the above-described embodiment, the second filter 210 is provided in the oil passage 100 (oil passage 51). However, the second filter 210 may be provided in the oil passage 90a.
In the above-described embodiment, the outer ring 28 of the thrust ball bearing 24 is formed integrally with the displacement shaft 23. However, as shown in FIG. 5, the displacement shaft 23 and the outer ring 28 may be provided separately. .

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

(A) is a principal part top view of the toroidal type continuously variable transmission which concerns on embodiment of this invention, (b) is a principal part side view. It is sectional drawing which follows the AA line of FIG. It is sectional drawing which follows the BB line of FIG. It is sectional drawing which shows an example of the specific structure of the toroidal type continuously variable transmission conventionally known. It is sectional drawing which follows the CC line of FIG.

Explanation of symbols

2 Input side disk 3 Output side disk 11 Power roller 14 Pivot 15 Trunnion 23 Displacement shaft 24 Thrust ball bearing (bearing)
90 oil passage (first oil passage)
90a Oil passage (third oil passage)
90b Oil passage (second oil passage)
100 oil passage (third oil passage)
200 First mesh filter (first filter)
210 Second mesh filter (second filter)

Claims (2)

An input shaft to which rotational torque is input, an input side disk and an output side disk that are supported concentrically and rotatably by the input shaft in a state where the respective inner surfaces face each other, and these input sides A trunnion that swings about a pivot that is twisted with respect to the central axis of the disk and the output-side disk, and the input-side disk and the output that are rotatably supported by a displacement shaft supported by the trunnion In a toroidal continuously variable transmission comprising a power roller sandwiched between a side disk and a bearing provided between the power roller and the trunnion and supporting a load in the thrust direction applied to the power roller,
A first oil passage for supplying lubricating oil into the trunnion;
A second oil passage that branches from the first oil passage and supplies lubricating oil to the traction surface formed between the input side disk, the output side disk, and the power roller through the trunnion; ,
A third oil passage branched from the first oil passage and supplying lubricating oil to the bearing through the trunnion and the displacement shaft;
A first filter provided in the first oil passage;
A second filter provided in the third oil passage;
A toroidal-type continuously variable transmission.   The toroidal continuously variable transmission according to claim 1, wherein the second filter has a mesh size smaller than that of the first filter.

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