JP2006242314A - Toroidal continuously variable transmission - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To effectively prevent fretting wear of abutting surfaces in a pair of members making minute displacement for the long time in the state of being strongly pressed against each other during operation of a toroidal continuously variable transmission. <P>SOLUTION: In the toroidal continuously variable transmission, at least one surface of a pair of surfaces constituting the abutting surfaces of a pair of members making minute displacement, such as the outside face of an input side disk 10b and a side face of a connection plate 47 constituting a carrier 33, in the state of being pressed against each other in operation of the toroidal continuously variable transmission, is coated with lubrication coatings 53a and 53b formed by shot-peening the surface with a solid lubrication agent. By employing this constitution, fretting wear on the abutting faces are prevented from occurring irrespective of the minute displacement. <P>COPYRIGHT: (C)2006,JPO&NCIPI

Description

  The present invention relates to an improvement of a toroidal type continuously variable transmission used as an automatic transmission for an automobile. Specifically, it is provided adjacently and prevents wear of the butted surfaces of a pair of members that are displaced slightly while being pressed strongly during operation of the toroidal type continuously variable transmission.

  The use of a toroidal-type continuously variable transmission as a transmission for an automobile has been widely known, for example, as described in Non-Patent Documents 1 and 2, and has been partially implemented. Also, a continuously variable transmission in which a toroidal continuously variable transmission and a planetary gear transmission are combined to increase the fluctuation range of the gear ratio has been widely known, for example, as described in Patent Document 1 and the like. It has been. Further, for example, in Patent Documents 2 and 3, it is called so-called geared neutral, and the rotation state of the output shaft can be switched between forward rotation and reverse rotation with the input shaft rotated in one direction with the stop state interposed therebetween. A transmission is described. In the case of such a continuously variable transmission, a starting mechanism such as a torque converter that transmits power with fluid can be omitted, and the power from the engine can be directly transmitted to the continuously variable transmission. For this reason, the transmission device can be reduced in size and weight, and the transmission efficiency can be prevented from being lowered by providing the torque converter, thereby improving the response performance at the time of starting.

  Patent Documents 4 and 5 describe a more specific structure of a continuously variable transmission that can realize the above-mentioned geared neutral. 5 to 7 show continuously variable transmissions described in Patent Documents 4 and 5. This continuously variable transmission is formed by combining a toroidal-type continuously variable transmission 1 and a planetary gear type transmission 2 and has an input shaft 3 and an output shaft 4. Between the input shaft 3 and the output shaft 4, the input rotary shaft 5 and the transmission shaft 6 of the toroidal continuously variable transmission 1 are provided concentrically with the shafts 3 and 4. In the state where the front stage unit 7 and the middle stage unit 8 of the planetary gear type transmission 2 are spanned between the input rotation shaft 5 and the transmission shaft 6, the rear stage unit 9 is connected to the transmission shaft 6 and the transmission shaft 6. Each is provided in a state of being spanned between the output shaft 4.

  The toroidal continuously variable transmission 1 includes a pair of input side disks 10a and 10b, an integrated output side disk 11, and a plurality of power rollers 12 and 12. The pair of input disks 10a and 10b are coupled to each other via the input rotation shaft 5 so as to be concentric with each other and capable of synchronous rotation. The output side disk 11 is concentric with the input side disks 10a and 10b between the input side disks 10a and 10b, and can freely rotate relative to the input side disks 10a and 10b. It is supported.

  Further, each of the power rollers 12 and 12 is provided between an output side concave surface that is both side surfaces in the axial direction of the output side disk 11 and an input side concave surface that is one side surface in the axial direction of the both input side disks 10a and 10b. Each of them is sandwiched by a plurality (two in the illustrated example). Then, power is transmitted from the input disks 10a, 10b to the output disk 11 while rotating with the rotation of the input disks 10a, 10b. The output side disk 11 is rotatably supported at both ends in the axial direction by a pair of support columns 14 and 14 and rolling bearings 15 and 15 which are thrust angular ball bearings. ing. Further, support plates 17a and 17b are respectively supported by support post portions 16a and 16b provided in the vicinity of both ends of the support columns 14 and 14, respectively.

  Further, between the two support plates 17a, 17b, pivots 19, 19 provided concentrically with each other at both ends of a plurality of trunnions 18, 18 which are support members described in the claims, It swings and supports displacement in the axial direction (vertical direction in FIG. 6). The power rollers 12 and 12 are rotated on the inner side surfaces (surfaces facing each other) of the trunnions 18 and 18 through support shafts 20 and 20 and a plurality of sets of rolling bearings, respectively, and the input rotary shaft 5. A slight displacement in the axial direction is supported freely. The peripheral surfaces of the power rollers 12, 12 are brought into rolling contact with the input-side concave surfaces of the input-side discs 10a, 10b and the output-side concave surface of the output-side disc 11.

  When the toroidal-type continuously variable transmission 1 performs a shifting operation, the hydraulic actuators 22 and 22 built in the actuator body 21 in which the lower ends of both the struts 14 and 14 are coupled and fixed are used. The trunnions 18, 18 are displaced in the axial direction of the pivots 19, 19. As a result, side slip occurs at rolling contact portions (traction portions) between the concave surfaces on the input and output sides and the peripheral surfaces, and the trunnions 18 and 18 swing around the pivots 19 and 19. To do. And the position of each said rolling contact part regarding the radial direction of each said disk 10a, 10b, 11 changes, and the gear ratio between both said input side disk 10a, 10b and said output side disk 11 changes. The supply and discharge of the pressure oil to and from the actuators 22 and 22 is performed by switching a speed ratio control valve built in a valve body 23 provided below the actuator body 21.

  In the case of the continuously variable transmission shown in the figure, the base end portion (left end portion in FIG. 5) of the input rotary shaft 5 is coupled to the crankshaft of the engine (not shown) via the input shaft 3. Thus, the input rotary shaft 5 is rotationally driven. Further, a hydraulic pressing device 24 is provided between the base end portion of the input rotating shaft 5 and the input side disk 10a, and one axial side surface (input side concave surface) of both the input side disks 10a and 10b, and Appropriate surface pressure can be freely applied to the rolling contact portion between both axial side surfaces (output side concave surfaces) of the output side disk 11 and the peripheral surfaces of the power rollers 12 and 12.

  The pressing device 24 is a so-called double piston type that can generate a large pressing force in the ratio of the diameter, and has first and second pistons 25 and 26. Of these, the first piston 25 includes an inner peripheral surface of a first cylinder tube portion 27 formed on a cylinder member that is oil-tightly fitted and fixed to a base end portion of the input rotary shaft 5 and a base end of the input rotary shaft 5. An oil-tight and axial displacement is possible between the outer peripheral surface of each part. Further, the second piston 26 has a second cylinder cylinder portion 28 provided integrally with the input side disk 10a on the outer side of the other side surface (outer side surface) in the axial direction of the input side disk 10a and the input rotation. The shaft 5 is fitted between the outer peripheral surface of the proximal end portion of the shaft 5 in an oil-tight manner and capable of axial displacement. A portion closer to the outer diameter of one side surface in the axial direction of the first piston 25 (right side surface in FIG. 5) abuts against the leading edge of the second cylinder tube portion 28.

  When the pressing device 24 is operated, pressure oil is introduced into the first and second cylinder chambers 29 and 30. Then, as the pressure in the first cylinder chamber 29 rises, the first piston 25 presses the input side disk 10a to the right in FIG. As the pressure in the second cylinder chamber 30 increases, the input side disk 10a is pressed to the right in FIG.

  Further, the base end portion (left end portion in FIG. 5) of the hollow rotary shaft 31 is spline engaged with the output side disk 11. The hollow rotary shaft 31 is inserted inside the input side disk 10b on the side far from the engine (right side in FIG. 5) so that the rotational force of the output side disk 11 can be taken out freely. Further, a first stage unit 7 of the planetary gear type transmission 2 is formed in a portion protruding from the outer surface of the input side disk 10b at the tip end portion (right end portion in FIG. 5) of the hollow rotary shaft 31. One sun gear 32 is fixed.

  On the other hand, the first carrier 33 is provided so as to span between the portion protruding from the hollow rotary shaft 31 at the tip end portion (right end portion in FIG. 5) of the input rotary shaft 5 and the input side disk 10b. The input side disk 10b and the input rotating shaft 5 rotate in synchronization with each other. The front unit 7 of the planetary gear type transmission 2 is a double pinion type at circumferentially equidistant positions (generally 3 to 4 positions) on both axial sides of the first carrier 33. The planetary gears 34 to 36 for constituting the middle unit 8 are rotatably supported. Further, a first ring gear 37 is rotatably supported around one half of the first carrier 33 (the right half of FIG. 5).

  Among the planetary gears 34 to 36, the planetary gear 34 provided on the inner side in the radial direction of the first carrier 33 near the toroidal type continuously variable transmission 1 (leftward in FIG. 5) is the first sun gear 32. Is engaged. Further, the planetary gear 35 provided on the inner side with respect to the radial direction of the first carrier 33 on the side far from the toroidal-type continuously variable transmission 1 (right side in FIG. 5) is a base end portion of the transmission shaft 6 (in FIG. 5). It meshes with a second sun gear 38 fixed at the left end). Further, the remaining planetary gear 36 provided on the outer side in the radial direction of the first carrier 33 has a larger axial dimension than the planetary gears 34 and 35 provided on the inner side, and both the planetary gears 34 and 35 are provided. Is engaged. Further, the remaining planetary gear 36 and the first ring gear 37 are meshed with each other.

  On the other hand, a second carrier 39 for constituting the rear stage unit 9 is coupled and fixed to the base end portion (left end portion in FIG. 5) of the output shaft 4. The second carrier 39 and the first ring gear 37 are coupled via a low speed clutch 40. Further, a third sun gear 41 is fixed to a portion near the tip of the transmission shaft 6 (near the right end in FIG. 5). A second ring gear 42 is disposed around the third sun gear 41, and a high speed clutch 43 is provided between the second ring gear 42 and a fixed portion of the casing 13, etc. Further, a plurality of sets of planetary gears 44 and 45 disposed between the second ring gear 42 and the third sun gear 41 are rotatably supported on the second carrier 39. The planetary gears 44 and 45 mesh with each other, and the planetary gear 44 provided on the inner side with respect to the radial direction of the second carrier 39 is provided on the third sun gear 41, and the planetary gear 45 provided on the outer side is provided on the first side. The two ring gears 42 mesh with each other.

  In the case of the continuously variable transmission configured as described above, the power transmitted from the input rotating shaft 5 to the integrated output side disk 11 via the pair of input side disks 10a and 10b and the power rollers 12 and 12, respectively, It is taken out through the hollow rotary shaft 31. In a state where the low speed clutch 40 is connected and the high speed clutch 43 is disconnected, the rotational speed of the input rotary shaft 5 is kept constant by changing the gear ratio of the toroidal continuously variable transmission 1. In this state, the rotational speed of the output shaft 4 can be freely converted into forward rotation and reverse rotation with the stop state interposed therebetween.

  That is, in this state, the differential component between the first carrier 33 that rotates in the forward direction together with the input rotation shaft 5 and the first sun gear 32 that rotates in the reverse direction together with the hollow rotation shaft 31 is the first component. It is transmitted from the ring gear 37 to the output shaft 4 through the low speed clutch 40 and the second carrier 39. In this state, the output shaft 4 is stopped by setting the gear ratio of the toroidal continuously variable transmission 1 to a predetermined value, and the speed ratio of the toroidal continuously variable transmission 1 is increased from the predetermined value. By changing to the side, the output shaft 4 is rotated in the direction in which the vehicle moves backward. On the other hand, the output shaft 4 is rotated in the direction of moving the vehicle forward by changing the gear ratio of the toroidal type continuously variable transmission 1 from the predetermined value to the deceleration side.

  In the state where the high speed clutch 43 is connected and the low speed clutch 40 is disconnected, the output side disk 11 rotates in the first sun of the hollow rotary shaft 31 and the planetary gear type transmission 2. It is transmitted to the output shaft 4 through the gear 32, the planetary gears 34 to 36, the transmission shaft 6, the second sun gear 38, the planetary gears 44 and 45, and the second carrier 39. In this state, as the gear ratio of the toroidal continuously variable transmission 1 is changed to the speed increasing side, the speed ratio of the continuously variable transmission as a whole also changes to the speed increasing side.

  The configuration and operation of the toroidal continuously variable transmission 1 and the continuously variable transmission incorporating the toroidal continuously variable transmission 1 are as described above. The components of the toroidal continuously variable transmission 1 are as follows. Elastically deforms when power is transmitted. Along with this elastic deformation, the abutting surfaces of a pair of adjacent members are slightly displaced, and there is a possibility that fretting wear occurs at the abutting portion. There are a plurality of portions where such fretting wear may occur in the toroidal-type continuously variable transmission 1 and continuously variable transmission. For example, the axial end surface of the first carrier 33 and the input The abutting portion with the outer surface of the side disk 10b is also one of them. Therefore, a mechanism in which fretting wear occurs in this portion will be described with reference to FIGS.

  The first carrier 33 is provided with an intermediate support plate 46 having an L-shaped cross section and an annular shape as a whole as shown in FIGS. The first and second connecting plates 47 and 48 formed in the above are integrally formed. A cylindrical portion 49 provided at the center of the intermediate support plate 46 is spline-engaged with a portion near the tip of the intermediate portion of the input rotating shaft 5 and is held down by a loading nut 50. Further, in order to transmit the rotation between the input side disk 10b and the first carrier 33, convex portions 51 formed at a plurality of locations on the outer side surface of the input side disk 10b, and the first connecting plate 47 The notches 52 and 52 formed in the outer peripheral edge are engaged.

  During the operation of the continuously variable transmission, the thrust generated by the pressing device 24 in order to ensure the surface pressure of each traction portion is caused by the input rotating shaft 5 and the first carrier 33 fixed to the input rotating shaft 5. It is added to the input side disk 10b via the intermediate support plate 46 and the first connecting plate 47 that constitute the same. In other words, the input side disk 10b and the input side disk 10b, which are contact portions between the outer side surface (the right side surface in FIG. 7) of the input side disk 10b and one side surface (the left side surface in FIGS. 7 to 8) of the first connecting plate 47. The pressing device 24 is arranged on the radial intermediate portion of the first connecting plate 47 (the annular portion formed by rotating the portion represented by w in FIG. 7 around the input side disk 10b and the central axis α of the first connecting plate 47). A force based on the thrust generated is added.

  On the other hand, the input-side disk 10b receives the input as shown in an exaggerated manner in FIG. 9, based on the force received from the power rollers 12, 12 (see FIG. 6) based on the thrust generated by the pressing device 24. A portion closer to the outer diameter of the side disk 10 b is elastically deformed in a direction (axial direction) approaching one side surface of the first connecting plate 47. That is, the force applied to the input side disk 10b based on the thrust during operation is about 5 t (tons) at the maximum during the operation of the toroidal continuously variable transmission, and the axial direction of the input side disk 10b based on such a force. The amount of elastic deformation with respect to is a comma number of millimeters (a few tenths of a millimeter) and cannot be ignored. Then, when the input side disk 10b is elastically deformed in the axial direction in this way, the outer surface outer diameter portion of the input side disk 10b and the one side surface of the first connecting plate 47 are intermittently repeatedly contacted. There is a possibility that fretting wear will occur at these parts. In particular, the circumferential position where the input disk 10b is elastically deformed always changes as the portion pressed by the power rollers 12, 12 changes. For this reason, the frequency of the rubbing is considerably high (for example, hundreds of tens Hz), which is a severe condition in terms of occurrence of fretting wear. Such fretting wear may cause the first carrier 33 to shift in the axial direction from a predetermined position, or may be a starting point of damage such as peeling. The fretting wear that occurs in other parts of the toroidal-type continuously variable transmission 1 causes the same inconvenience.

  As a technique for preventing wear of a pair of members that are in contact with each other, Patent Document 6 discloses that a lubricant film made of various solid lubricants is formed on the surface of a component of a rolling bearing used in a portion where lubricant cannot be used. The invention has been described. However, the invention described in Patent Document 6 does not take into consideration prevention of fretting wear at a portion that is slightly displaced. In addition, no specific means for forming the lubricating coating is described. In view of the technical level at the time of filing with respect to Patent Document 6, it is considered that this is due to ordinary coating. In the case of a butt portion between a pair of members adjacent to each other in the toroidal type continuously variable transmission 1 that is the subject of the present invention, a large surface pressure is repeatedly applied to the butt surface based on the large pressing force generated by the pressing device 24. Will be added. Therefore, it is difficult for a lubricating coating formed by a normal coating to peel off at an early stage and suppress the fretting wear generated as described above over a long period of time.

JP 11-63146 A US Pat. No. 5,607,372 JP 2002-139124 A JP 2004-169719 A JP 2004- 211744 A JP-A 63-125824 Motoo Aoyama, “Bessed Best Car Red Badge Series 245 / A book that understands the latest mechanics of cars”, Sangensha Co., Ltd./Kodansha Co., Ltd., December 20, 2001, p. 92-93 Hirohisa Tanaka, “Toroidal CVT”, Corona Inc., July 13, 2000

  In view of the circumstances as described above, the present invention effectively prevents wear of the butted surfaces of a pair of members that are slightly displaced while being pressed strongly during operation of the toroidal continuously variable transmission over a long period of time. It was invented to realize a possible structure.

The toroidal type continuously variable transmission of the present invention is similar to conventionally known toroidal type continuously variable transmissions, for example, as shown in FIGS. A plurality of support members such as trunnions 18, 18, a plurality of power rollers 12, 12, and a hydraulic or mechanical pressing device 24.
Among these, the input side disks 10a and 10b have an input side concave surface which is a concave surface having an arcuate cross section.
The output-side disk 11 has an output-side concave surface that is a concave surface having an arcuate cross section. The output-side concave surface is supported concentrically with the input-side discs 10a, 10b and capable of relative rotation with respect to the input-side discs 10a, 10b with the output-side concave surface facing the input-side concave surface.
Further, the plurality of support members such as the trunnions 18 and 18 are respectively positioned between the input side and output side concave surfaces of the input side and output side discs 10a, 10b and 11 with respect to the axial direction. Oscillating displacements about the pivots 19 and 19 that are twisted with respect to the rotation centers of 10a, 10b, and 11 are freely provided.
The power rollers 12 and 12 are rotatably supported by the support members such as the trunnions 18 and 18, and the respective circumferential surfaces formed as spherical convex surfaces are input sides of the disks 10a, 10b, and 11, respectively. It is in rolling contact with both concave surfaces on the output side.
Further, the pressing device 24 converts one of the disks 10a, 10b, 11 (the input side disk 10a, 10b in the example of FIG. 5) to the other disk (the output side disk 11 in the example of FIG. 5). It is for pressing.

In particular, in the toroidal type continuously variable transmission 1 of the present invention, among a plurality of members constituting the toroidal type continuously variable transmission 1, among the surfaces of at least one pair of members provided adjacent to each other, Covering at least one of the opposing surfaces that are abutted with each other in the assembled state of this toroidal type continuously variable transmission by a solid lubricant colliding with the surface by shot peening is doing.
The type of the solid lubricant is not particularly limited as long as the required heat resistance and oil resistance (not to be altered by traction oil) can be secured and fine particles can be obtained. For example, tin, tin alloy, molybdenum disulfide, tungsten disulfide, boron nitride, polyethylene, fluorine resin, polyamide resin, metal soap, calcium fluoride, and the like can be used.
In the case of forming the lubricating coating, the solid lubricant fine particles as described above are applied to the surface to be processed on which the lubricating coating is to be formed (one or both of a pair of surfaces that face each other and are displaced slightly). Blow strongly. As a result, a solid lubricant film is formed in such a manner that the fine particles of the solid lubricant bite into the base material (metal material such as carbon steel) constituting the surface to be processed.

  According to the toroidal-type continuously variable transmission of the present invention configured as described above, fretting wear on a pair of surfaces that face each other and are slightly displaced can be suppressed regardless of long-term use. For this reason, it is possible to prevent the positional relationship between the pair of members that face each other from occurring, which leads to a decrease in durability and a decrease in transmission efficiency of the toroidal-type continuously variable transmission. Moreover, generation | occurrence | production of the metal powder based on abrasion can be suppressed, and deterioration of the other movable part by abrasion powder can also be aimed at.

In carrying out the present invention, preferably, as described in claim 2, the lubricating coating is coated on the surface on which the minute recesses are formed in advance.
In this case, the depth of the minute recess formed is appropriate to be about 0.1 to 5 μm. The lubricating coating covers the surface of the base material so as to fill each of these minute recesses.
By adopting such a configuration, it is possible to further improve the bonding strength between the lubricating coating and the base material, and to leave the lubricating coating covering the surface over a long period of time. Thus, it is possible to effectively prevent fretting wear on a pair of surfaces that are slightly displaced over a long period of time.
That is, when forming a lubricating coating on at least one of the pair of relatively displaced surfaces, if there are micro-recesses on the surface, the lubricating coating is applied while filling each of these micro-recesses with a solid lubricant. Due to the anchor effect based on the mechanical engagement between the lubricating coating and the minute recesses, the bond strength between the lubricating coating and the base material is remarkably increased (compared to the case where the lubricating coating is coated on a smooth surface). Can be improved. Further, the effect of preventing the fretting wear by the lubricating coating can be effectively achieved over a longer period.

In order to obtain such actions and effects, it is necessary to secure the depth of each minute recess as 0.1 μm or more. On the other hand, if the depth of each of these micro-recesses exceeds 5 μm, not only the above-mentioned action / effect is saturated, but also the mother surface is used to fill these micro-recesses and make the surface roughness of the lubricating coating appropriate. The amount of solid lubricant to be coated on the surface of the material increases, and the cost required to form this lubricating coating increases.
Therefore, preferably, the depth of the minute recess is set to 0.1 μm or more and 5 μm or less. The operation for forming each of these minute recesses is performed by shot peening or barrel processing. As media used when performing shot peening, general media such as steel balls and glass beads can be used.

As a first example of a preferred embodiment of the present invention, a structure corresponding to claim 3 is shown in FIG. In the structure of the first example, the opposing surfaces of a pair of members provided adjacent to each other are arranged on the outer surface of the input side disk 10b and the first carrier 33 of the planetary gear transmission. One side of the connecting plate 47 in the axial direction is used.
In the case of the structure of the first example, as described in FIGS. 5 and 7, the toroidal continuously variable transmission 1 is combined with the planetary gear type transmission 2 to constitute a continuously variable transmission. . As described above with reference to FIGS. 5 to 6, this continuously variable transmission includes an input shaft 3, an output shaft 4, a toroidal continuously variable transmission 1, and a planetary gear transmission 2 that are arranged concentrically with each other. With. The toroidal type continuously variable transmission 1 and the planetary gear type transmission 2 are constituted by the input side disk 10b constituting the toroidal type continuously variable transmission 1 and the planetary gear type transmission 2 (first) carrier 33. And the input side disk 10b and the carrier 33 are combined in a state of rotating in synchronization with each other. The carrier 33 is supported by and fixed to the input shaft 3 via the input rotary shaft 5 of the toroidal-type continuously variable transmission 1 (intermediate), and the carrier plate 46 is concentric with the support plate 46 in the axial direction. (First) connecting plate 47, which is arranged in a state spaced apart from each other, with one side faced to the outer surface of the input side disk 10b, the connecting plate 47 and the support plate 46, And a plurality of planetary shafts supported at both ends.
In order to carry out the present invention with such a structure, one or both of the outer side surface of the input side disk 10b and one axial side surface of the first connecting plate 47 (preferably shown in FIG. 1). In the same manner, both surfaces) are covered with lubricating coatings 53a and 53b formed by causing solid lubricant (fine particles) to collide with the surfaces by shot peening. By covering such lubricating coatings 53a and 53b, it is possible to prevent fretting wear due to minute displacement based on the elastic deformation of the input side disk 10b as described above.

Next, as a second example of a preferred embodiment of the present invention, a structure corresponding to claim 4 is shown in FIG. In the structure of the second example, the pressing device is input by pistons 25 and 26 that are displaced (both first and second) as the hydraulic pressure is introduced into the cylinder chambers 29 and 30 (both first and second). This is a hydraulic cylinder that presses the side disks 10a and 10b toward the output side disk 11 (see FIG. 5 for some members).
Then, one of the opposed surfaces of at least one pair of members provided adjacent to each other is a part of one side surface in the axial direction of the (first) piston 25 (the outer diameter on the right side surface in FIG. 2). It is a close part). The other surface is a tip surface of the second cylinder cylinder portion 28, which is a portion fixed to the outer surface of the input side disk 10a.
In order to carry out the present invention with such a structure, one or both surfaces of a part of one side surface in the axial direction of the (first) piston 25 and the front end surface of the second cylinder tubular portion 28 ( Preferably, as shown in FIG. 2, both surfaces are covered with lubricating coatings 53c and 53d formed by causing solid lubricant (fine particles) to collide with the surfaces by shot peening. If such lubricating films 53c and 53d are coated, fretting wear due to minute displacement based on elastic deformation of the input side disk 10a and the (first) piston 25 can be prevented.

  Furthermore, as a third example of a preferred embodiment of the present invention, a structure corresponding to claim 5 is shown in FIGS. In the structure of the third example, a pair of output side disks 11a are spline-engaged with both ends of the rotating cylinder 54 as described in the above-mentioned Non-Patent Document 1 etc. and widely known. The pair of output side disks 11a are rotated in synchronization with each other. The rotation of both the output side disks 11a is taken out via an output gear 55 fixed on the outer peripheral surface of the intermediate portion of the rotary cylinder 54. Further, the rotating cylinder 54 is supported only freely by a rolling bearing 56 such as an angular ball bearing provided on both side portions of the output gear 55 with respect to an intermediate wall provided in a casing (not shown).

In the case of such a structure, a portion closer to the inner diameter, which is a part of the outer surface of each of the output side disks 11a, supports the output side disk 11a so as to be rotatable while supporting a thrust load applied to the output side disk 11a. It is abutted against the axial side surface of the inner ring 57 constituting the rolling bearing 56, which is a member.
In order to carry out the present invention with such a structure, one or both surfaces of the outer surface inner diameter portion of both the output side disks 11a and the axial side surface of the inner ring 57 constituting the rolling bearing 56 ( Preferably, as shown in FIGS. 3 to 4, both surfaces are covered with lubricating coatings 53 e and 53 f formed by causing solid lubricant (fine particles) to collide with the surfaces by shot peening. By coating such lubricating coatings 53e and 53f, it is possible to prevent fretting wear due to minute displacement based on elastic deformation of the output side disk 11a.

In carrying out the present invention, preferably, the average value of the thickness of the lubricating coating is restricted to a range of 0.1 to 8 μm. In the case of the present invention, of the plurality of members constituting the toroidal continuously variable transmission, the surfaces of at least one pair of adjacent members are pushed against each other in a state where the toroidal continuously variable transmission is assembled. By covering at least one of the opposed surfaces with a lubricant film made of a solid lubricant, the friction generated at the abutting surface portion is reduced, but the average value of the thickness of the lubricant film is If it is too small (if it is less than 0.1 μm), the above friction cannot be reduced sufficiently {It becomes difficult to ensure a sufficient coverage (for example, 75% or more in area ratio) with the lubricating film on the abutting surface portion. The friction of the butt surface portion cannot be sufficiently reduced}. Even if it can be reduced, the lubricating coating is worn away at an early stage, and this friction reducing effect is lost at an early stage. On the other hand, if the average value of the thickness of the lubricating coating is too large (exceeding 8 μm), the effect is not only saturated with respect to the friction reduction and the extension of the time until the lubricating coating is worn. , A part of the lubricating film is missing and easily falls off. And when it falls off, the micro piece produced as a result of the drop enters each rolling contact portion and the like, causing vibration and noise.
Therefore, a preferable range as an average value of the thickness of the lubricating coating is set to 0.1 μm or more and 8.0 μm or less. If the average value of the thickness falls within the range of 0.1 to 8.0 μm, at least one of the facing surfaces that are abutted against each other is sufficiently hardened (not easily lost) by the lubricating coating. The coated lubricant film can be sufficiently prevented from peeling off.

The lubricating coating having the thickness as described above is formed by shot peening as described above. If this lubricating coating is formed in this way, a pair of adjacently provided base materials is formed. The surface portion of the bearing steel such as SUJ2 that constitutes at least one of the members is hardened. That is, in an experiment conducted by the present inventor, after forming a lubricant film, a solid lubricant (for example, Sn powder having an average particle diameter of 45 μm and MoS ₂ powder having an average particle diameter of 3 μm) was shot. When the hardness in the depth range of 2 to 15 μm from the outermost surface of the base material covered with the lubricating coating was measured by a hardness test using a micro hardness tester, the hardness had a gradient in this range. It was confirmed that the highest hardness of the steel increased by 5 to 20% compared to the hardness of the base material before the treatment. Such an increase in hardness is advantageous from the viewpoint of securing a rolling fatigue life of the base material covered with the lubricating coating.

  The present invention can be implemented regardless of whether the type of toroidal continuously variable transmission is a half toroidal type or a full toroidal type.

Sectional drawing which shows the 1st example of preferable embodiment of this invention in the state which decomposed | disassembled the A section of FIG. Sectional drawing which shows the 2nd example in the state which decomposed | disassembled the B section of FIG. The fragmentary sectional view of the toroidal type continuously variable transmission which shows the 3rd example. Sectional drawing which shows the C section of FIG. 3 in the state in the middle of an assembly. Sectional drawing which shows one example of the continuously variable transmission which combined the toroidal type continuously variable transmission and planetary gear type transmission known conventionally. DD sectional drawing of FIG. The E section enlarged view of FIG. The perspective view which takes out and shows the carrier of a planetary gear type transmission. FIG. 6 is a schematic cross-sectional view exaggeratingly showing the state of elastic deformation of the input side disk that is connected to fretting wear.

Explanation of symbols

DESCRIPTION OF SYMBOLS 1 Toroidal type continuously variable transmission 2 Planetary gear type transmission 3 Input shaft 4 Output shaft 5 Input rotation shaft 6 Transmission shaft 7 Front stage unit 8 Middle stage unit 9 Rear stage unit 10a, 10b Input side disk 11, 11a Output side disk 12 Power roller DESCRIPTION OF SYMBOLS 13 Casing 14 Support | pillar 15 Rolling bearing 16a, 16b Support post part 17a, 17b Support plate 18 Trunnion 19 Axis 20 Support shaft 21 Actuator body 22 Actuator 23 Valve body 24 Pressing device 25 1st piston 26 2nd piston 27 1st cylinder cylinder part 28 Second cylinder cylindrical portion 29 First cylinder chamber 30 Second cylinder chamber 31 Hollow rotating shaft 32 First sun gear 33 First carrier 34 Planet gear 35 Planet gear 36 Planet gear 37 First ring gear 38 Second sun gear 39 First sun gear 39 Nika A 40 Low-speed clutch 41 Third sun gear 42 Second ring gear 43 High-speed clutch 44 Planetary gear 45 Planetary gear 46 Intermediate support plate 47 First connection plate 48 Second connection plate 49 Cylindrical portion 50 Loading nut 51 Convex portion 52 Cutting Notch 53a to 53f Lubrication coating 54 Rotating cylinder 55 Output gear 56 Rolling bearing 57 Inner ring

Claims (5)

  An input-side disk having an input-side concave surface with an arc-shaped cross section and an output-side concave surface with an arc-shaped cross-section, and concentric with the input-side disk, with the output-side concave surface facing the input-side concave surface And an output side disk supported so as to be capable of relative rotation with respect to the input side disk, and both of the input side and the output side of the both sides of the input side and output side discs in the axial direction. A plurality of support members that are provided with a freely oscillating displacement about a pivot that is in a twisted position with respect to the center of rotation of the disk, and each of the support members are rotatably supported to form a spherical convex surface. A plurality of power rollers whose circumferential surfaces are in rolling contact with both the input and output concave surfaces of the two disks, and a pressing device for pressing one of the disks toward the other disk; In the toroidal type continuously variable transmission provided, the toroidal type continuously variable transmission among the surfaces of at least one pair of adjacent members among a plurality of members constituting the toroidal type continuously variable transmission. At least one of the facing surfaces that face each other in the assembled state of the machine is covered with a lubricating coating formed by colliding solid lubricant with the surface by shot peening. Toroidal type continuously variable transmission.   The toroidal continuously variable transmission according to claim 1, wherein the lubricating coating is coated on a surface in which a minute concave portion is previously formed.   A toroidal continuously variable transmission is combined with a planetary gear type transmission to form a continuously variable transmission, and the continuously variable transmission includes an input rotary shaft and an output shaft that are arranged concentrically with each other. A toroidal continuously variable transmission and a planetary gear type transmission. These toroidal type continuously variable transmission and planetary gear type transmission include an input side disk and a planetary gear constituting the toroidal type continuously variable transmission. The input side disk and the carrier are combined in a state where the carrier and the carrier constituting the transmission are adjacent to each other, and the carrier is supported and fixed to the input rotation shaft. It is arranged concentrically with this support plate and spaced apart in the axial direction, and its one side is opposed to the outer side which is the opposite side of the input side concave surface among the two axial sides of the input side disk. In a ring shape And a plurality of planetary shafts supported at both ends by the connection plate and the support plate, and at least one pair of adjacent members opposed to each other. The toroidal continuously variable transmission according to any one of claims 1 and 2, wherein the surfaces are an outer surface of the input-side disk and an axial one surface of the connecting plate.   The pressing device is a hydraulic cylinder that presses the input-side disk toward the output-side disk by a piston that is displaced as the hydraulic pressure is introduced into the cylinder chamber, and at least one pair of adjacent members are abutted against each other. The opposed surface is a part of one side surface in the axial direction of the piston and the tip surface of the portion fixed to the outer surface which is the surface opposite to the concave surface on the input side, on both side surfaces in the axial direction of the input side disk. The toroidal continuously variable transmission according to any one of claims 1 to 3.   A part of the outer side surface, which is the opposite side of the output side concave surface, on both sides in the axial direction of the output side disk supports the output side disk rotatably while supporting the thrust load applied to the output side disk. The opposing surfaces of the at least one pair of adjacent members that are abutted against the axial side surface of the support member are a part of the outer side surface of the output side disk and the axial side surface of the support member. The toroidal continuously variable transmission according to any one of claims 1 to 4.

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