JP2011133059A - Continuously variable transmission - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To provide a continuously variable transmission which imparts loading force in part of a disk where deformation rigidity is high, prevents the deterioration of transmission efficiency, prevents the occurrence of fretting, and reduces bending stress. <P>SOLUTION: A protrusion 113 is formed on an inside diameter side surface of a first connecting part 103 of a carrier 102 toward an input side disk 112 which is an outside disk of the toroidal type continuously variable transmission 111, and a recess 114 is formed on an outside surface of the input side disk 112 in a position corresponding to the protrusion 113 so as to be fitted to the protrusion 113. The outside diameter of a sun gear 109 is larger than the inside diameter of the first connecting part 103. In this embodiment, the outside diameter part 117 of a flange part 116 provided on one end of an input shaft 115 and the inside diameter part 118 of a second connecting part 104 of the carrier 102 are formed into a spigot shape so as to be fitted with each other, and are spline-joined, and are rotated together, and are integrated by welding (beam welding). <P>COPYRIGHT: (C)2011,JPO&amp;INPIT

Description

  The present invention relates to a continuously variable transmission in which a toroidal continuously variable transmission and a planetary gear transmission are used as an automatic transmission for automobiles or a transmission for adjusting the operating speed of various industrial machines. It is.

  The use of a toroidal continuously variable transmission as an automatic transmission for automobiles has been studied and implemented in part. In addition, as described in the patent literature, it has been conventionally proposed to configure a continuously variable transmission by combining a toroidal type continuously variable transmission and a planetary gear type transmission. FIG. 2 shows the continuously variable transmission described in Patent Document 1 among them. This continuously variable transmission is formed by combining a toroidal type continuously variable transmission 1 and a planetary gear type transmission 2. Of these, the toroidal continuously variable transmission 1 includes an input shaft 3, a pair of input side disks 4, 4, an output side disk 5, and a plurality of power rollers 6, 6.

  The planetary gear type transmission 2 includes a carrier 7 coupled and fixed to the input shaft 3 and one input side disk 4 (right side in FIG. 2). A first transmission shaft 10 having planetary gears 8 and 9 fixed to both ends of the carrier 7 in the radial direction intermediate portion is rotatably supported. Further, a second transmission shaft 13 having sun gears 11 and 12 fixed to both ends thereof is supported on the opposite side of the input shaft 3 with the carrier 7 interposed therebetween, and is rotatably supported concentrically with the input shaft 3. ing. The planetary gears 8 and 9 and the sun fixed to the distal end portion (the right end portion in FIG. 2) of the hollow rotary shaft 14 whose base end portion (the left end portion in FIG. 2) is coupled to the output side disk 5. The gear 15 or the sun gear 11 fixed to one end portion (left end portion in FIG. 2) of the second transmission shaft 13 is engaged with each other. Further, one (left side in FIG. 2) planetary gear 8 is meshed with a ring gear 17 rotatably provided around the carrier 7 via another planetary gear 16.

  On the other hand, planetary gears 19 and 20 are rotatably supported on a second carrier 18 provided around the sun gear 12 fixed to the other end portion (the right end portion in FIG. 2) of the second transmission shaft 13. . The second carrier 18 is fixed to the proximal end portion (left end portion in FIG. 2) of the output shaft 21 that is disposed concentrically with the input shaft 3 and the second transmission shaft 13. The planetary gears 19 and 20 mesh with each other, and one planetary gear 19 is provided in the sun gear 12 and the other planetary gear 20 is provided around the second carrier 18 so as to be rotatable. The ring gears 22 mesh with each other. The ring gear 17 and the second carrier 18 can be freely engaged and disengaged by a low speed clutch 23, and the second ring gear 22 and a fixed portion such as a housing can be freely disengaged by a high speed clutch 24. It is said.

  Patent Document 2 discloses a continuously variable transmission as shown in FIG. The continuously variable transmission shown in FIG. 3 has the same function as that of the conventionally known continuously variable transmission shown in FIG. 2, but the structure of the planetary gear type transmission 2a is the same. By devising, the assemblability of the planetary gear type transmission 2a is improved. A pair of planetary gears 25a, 25b, 26a, and 26b are rotatably supported on both side surfaces of the carrier 7a that rotates together with the input shaft 3 and the pair of input side disks 4a and 4b. Then, the planetary gears 25a and 25b supported on the side surfaces of the carrier 7a and the planetary gears 26a and 26b are meshed with each other, and the planetary gears 25a and 26a on the inner diameter side are connected to the output side disk 5 with the base. First and second fixed respectively to the distal end portion (right end portion in FIG. 3) of the hollow rotary shaft 14a to which the end portion (left end portion in FIG. 3) is coupled and one end portion (left end portion in FIG. 3) of the transmission shaft 27. The planetary gears 25b and 26b on the outer diameter side are engaged with the ring gear 30 and the sun gears 28 and 29, respectively.

  On the other hand, the planetary gears 32a and 32b are rotatably supported by the second carrier 18a provided around the third sun gear 31 fixed to the other end portion (the right end portion in FIG. 3) of the transmission shaft 27. . The second carrier 18a is fixed to the base end portion (left end portion in FIG. 3) of the output shaft 21a arranged concentrically with the input shaft 3. The planetary gears 32a and 32b mesh with each other, and the planetary gear 32a on the inner diameter side is rotatable around the third sun gear 31 and the planetary gear 32b on the outer diameter side is rotatable around the second carrier 18a. Are respectively meshed with the second ring gear 22a. Further, the ring gear 30 and the second carrier 18a can be engaged and disengaged by a low speed clutch 23a, and the second ring gear 22a and a fixed part such as a housing can be engaged and disengaged by a high speed clutch 24a. It is said.

  In the case of the improved continuously variable transmission configured as described above, the power of the input shaft 3 causes the ring gear 30 to be driven when the low speed clutch 23a is connected and the high speed clutch 24a is disconnected. Via the output shaft 21a. By changing the gear ratio of the toroidal-type continuously variable transmission 1, the gear ratio of the continuously variable transmission, that is, the gear ratio between the input shaft 3 and the output shaft 21a changes. On the other hand, when the low speed clutch 23a is disconnected and the high speed clutch 24a is connected, the power of the input shaft 3 is applied to the planetary gears 25a, 25b, the ring gear 30, and the planetary gears. It is transmitted to the output shaft 21a through the gears 26a and 26b, the transmission shaft 27, the planetary gears 32a and 32b, and the second carrier 18a. And the gear ratio as the whole continuously variable transmission changes by changing the gear ratio of the toroidal type continuously variable transmission 1.

  As shown in FIGS. 4 to 5 to be described below, an outer planetary gear 25 having a long axial dimension is used, and this long planetary gear 25 is used as an inner planetary gear 25a, 26a and a ring. The same function can be exhibited even if a structure for meshing with the gear 30a is employed. In this case, the axial dimension of the ring gear 30a having a large diameter can be shortened to reduce the weight of the planetary gear type transmission 2b.

  The above-described structures of FIG. 2 and FIG. 3 described above are fundamental and do not indicate a specific structure. 4 to 6 show an example of a specific structure of the continuously variable transmission considered above. In this structure, as described above, the planetary gear 25 on the outer diameter side having a long axial dimension is used, and the long planetary gear 25 is used as the planetary gears 25a and 26a and the ring gear 30a on the inner diameter side. Meshing.

  A pair of support columns 34 are supported and fixed at predetermined positions in the housing 33 via a connecting plate 35 and a valve body 36. The valve body 36 incorporates a control valve device for controlling the gear ratio of the toroidal type continuously variable transmission 1. Further, support plates 37 and 37 for supporting both ends of the trunnion for supporting the power rollers 6 and 6 (see FIG. 2) in a swingable and axially displaceable manner at both ends of each of the columns 34 and 34, respectively. Support. Further, the output side disk 5 is rotatably supported by a pair of rolling bearings 38, 38 between the intermediate portions of the respective pillars 34, 34 formed in an annular shape. And the base half part (the left half part of FIG. 4) of the hollow rotating shaft 14a is coupled to the inner diameter side of the output side disk 5 based on the spline engagement so as to be able to transmit the rotation.

  The input shaft 3a is inserted inside the hollow rotary shaft 14a. One input side disk 4a (on the left side in FIG. 4) is supported by a ball spline 39 near the base end portion of the input shaft 3a, and the input side disk 4a is supported by a hydraulic pressing device 40. The output side disk 5 can be pressed freely. On the other hand, the other input side disk 4b (on the right side in FIG. 4) is rotated and axially moved by a radial needle bearing 41 around a portion near the tip of the middle part (right side in FIG. 4) of the hollow rotating shaft 14a. Supports displaceability. The other input side disk 4b and the input shaft 3a are coupled via a carrier 7a. Accordingly, the pair of input side disks 4a and 4b provided at the positions sandwiching the output side disk 5 from both sides in the axial direction rotate synchronously via the input shaft 3a and the carrier 7a.

  As shown in detail in FIGS. 5 to 6, the carrier 7 a includes an intermediate support plate 42 having an L-shaped cross section and an annular shape as a whole, and first and second connecting plates 43 each formed in an annular shape, A plurality of (for example, three) first and second planetary shafts 45 and 46 are respectively provided between the first and second connecting plates 43 and 44 (for example, three). 3) third planetary shafts 47 are spanned over each other. The planetary gears 25a, 26a, 25 are rotatably supported around the planetary shafts 45-47 via radial needle bearings 48a, 48b, 48c, respectively. Then, the planetary gear 25 on the outer diameter side and the planetary gears 25a and 26a on the inner diameter side are engaged with each other, and the planetary gears 25a and 26a on the inner diameter side are connected to the distal end portion of the hollow rotary shaft 14a (see FIGS. 4 to 5). The planetary gear 25 on the outer diameter side is meshed with the ring gear 30a to the first sun gear 28 fixed to the right end portion) or the second sun gear 29 fixed to the base end portion of the transmission shaft 27, respectively. .

  A cylindrical portion 49 provided at the center of the intermediate support plate 42 is spline-engaged with a portion closer to the front end of the intermediate portion of the input shaft 3 a and is held down by a loading nut 50. As shown in FIG. 6, the annular portion 51 of the intermediate support plate 42 and the first and second connecting plates 43, 44 are disengaged from the planetary gears 25a, 26a, 25 in the circumferential direction. They are connected to each other by connecting portions 57, 57 provided at different positions. In the case of the illustrated example, the intermediate support plate 42 and the first and second connecting plates 43 and 44 constituting the carrier 7a are integrally formed. And by this structure, the intensity | strength and rigidity with respect to the force of the rotation transmission direction of the said carrier 7a are ensured. Further, in order to transmit the rotation between the other input side disk 4b and the carrier 7a, convex portions 52 formed at a plurality of locations on the outer side surface of the other input side disk 4b, and the first connecting plate A notch 53 formed on the outer peripheral edge portion of 43 is engaged. Further, during operation, the input shaft 3a is rotationally driven by the drive shaft 54. At the same time, hydraulic pressure is introduced into the pressing device 40, and the surface pressure of the rolling contact portion (traction portion) between the side surfaces of the input side disks 4a, 4b and the output side disk 5 and the peripheral surfaces of the power rollers 6, 6 is adjusted. Secure.

  In the case of the continuously variable transmission shown in FIGS. 4 to 6 as described above, the rotation transmission between the other input side disk 4 b and the carrier 7 a is performed by the concave and convex engagement between the convex portion 52 and the notch 53. . Further, the thrust generated by the pressing device 40 in order to ensure the surface pressure of the traction portion is transmitted through the input shaft 3a and the intermediate support plate 42 and the first connecting plate 43 constituting the carrier 7a fixed to the input shaft 3a. To the other input side disk 4b. In other words, these inputs are the contact portions between the outer side surface (the right side surface in FIGS. 4 to 6) of the other input side disk 4b and one side surface (the left side surface in FIGS. 4 to 6) of the first connecting plate 43. In the radial intermediate portion of the side disk 4b and the first connecting plate 43 (a ring-shaped portion formed by rotating the portion represented by w in FIG. 5 around the central axis α of the input side disk 4b and the first connecting plate 43), A force based on the thrust generated by the pressing device 40 is applied.

  On the other hand, the other input side disk 4b is formed on the input side disk 4b as shown in an exaggerated manner in FIG. 7 based on the force received from the power rollers 6 and 6 based on the thrust generated by the pressing device 40. The portion closer to the outer diameter is elastically deformed in a direction (axial direction) approaching one side surface of the first connecting plate 43. That is, the force applied to the other input side disk 4b 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 shaft of the input side disk 4b based on such a force. The amount of elastic deformation related to the direction is a comma number of mm (a few tenths of a millimeter) and cannot be ignored. When the other input side disk 4b is elastically deformed in the axial direction in this way, the outer surface of the other input side disk 4b and the one side surface of the first connecting plate 43 are repeatedly and repeatedly applied. When they come into contact with each other, they rub against each other, and there is a possibility that fretting wear will occur at those portions. In particular, the circumferential position at which the input disk 4b is elastically deformed always changes as the portions pressed by the power rollers 6 and 6 change. 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 carrier 7a to shift in the axial direction from a predetermined position, or may be a starting point of damage such as peeling. The first connecting plate 43 constituting the carrier 7a is made of a relatively soft metal as compared with the input side disk 4b. For this reason, with the elastic deformation of the input side disk 4b, the first connecting plate 43 may be similarly elastically deformed. Such elastic deformation of the first connecting plate 43 tilts the planetary shafts 45 to 47 supported by the first connecting plate 43, and planetary gears 25a and 26a rotatably supported on the planetary shafts 45 to 47. , 25 and the ring gear 30a and the sun gears 28, 29 are deteriorated. If the meshing state deteriorates in this way, the durability of each of the gears 25a, 26a, 25, 30a, 28, 29 may be reduced, and the transmission efficiency of the planetary gear type transmission 2b may be reduced. In particular, in the case of a continuously variable transmission that is an object of the present invention, the transmission efficiency of the planetary gear transmission 2b greatly affects the transmission efficiency of the entire continuously variable transmission. It is not preferable that the transmission efficiency decreases. Further, the generated wear powder contaminates the lubricating oil (traction oil), which may cause the lubrication state of each part to be poor.

  As a means for improving the above problem, there is a continuously variable transmission described in Patent Document 3. As shown in FIG. 8, the continuously variable transmission is configured such that one side surface of the first connection plate 43a and the outer surface of the input side disk 4b are connected to each other in the radial direction of the first connection plate 43a and the input side disk 4b. While abutting on the inner diameter side, the outer diameter side is also opposed through a gap. As a result, the elastic deformation of the input side disk 4b is hardly transmitted to the first connecting plate 43a, and the above problem can be solved. Alternatively, the two side surfaces are brought into contact with only a portion of the carrier 7a having a low axial rigidity, a coating for preventing wear is formed on both side surfaces, or a recess for storing lubricating oil. Is formed.

JP 2000-220719 A JP 2004-225888 A JP 2005-249181 A

  However, in this prior art, since the carrier is configured by connecting the ring portion of the intermediate support plate and the connecting plate, the rigidity of the carrier is low, so that the carrier follows by the deformation of the disk. As a result, the planetary shafts are deformed and the transmission efficiency is lowered.

  In order to solve the above problem, the present invention includes an input shaft, a toroidal continuously variable transmission, and a planetary gear type transmission, which are arranged concentrically with each other. An inner disk, a pair of outer disks supported on both sides of the inner disk, concentrically with the inner disk, and independently of the inner disk so as to freely rotate, both side surfaces of the inner disk, and side surfaces of the outer disk And the planetary gear mechanism includes a sun gear around the input shaft, a ring gear arranged around the sun gear, a sun gear, and a ring. A planetary gear disposed between the gear and a carrier that supports the planetary gear, and the toroidal continuously variable transmission and the planetary gear type transmission constitute a toroidal continuously variable transmission. In the continuously variable transmission in which the side disk and the carrier constituting the planetary gear type transmission are adjacent to each other and the one outer disk and the carrier are rotated in synchronization with each other, the input shaft has a radially outer side. A flange portion extending to the outer disk, the flange portion and the carrier are non-rotatably engaged, and the outer diameter of the sun gear is larger than the inner diameter of the carrier on the side adjacent to the outer disk. A step portion is provided on the outer disk side of the end of the flange portion, an engagement portion that engages with the step portion is provided on the carrier, the flange portion and the carrier are engaged with each other in the circumferential direction, and the flange is further provided. The part and the carrier are welded.

  According to the present invention, it is possible to apply a loading force when the deformation rigidity of the disk is high, thereby preventing a decrease in transmission efficiency, and preventing the occurrence of fretting and reducing bending stress.

It is a figure which shows the cross-sectional shape of embodiment of this invention. It is a schematic sectional drawing which shows the continuously variable transmission conventionally known. It is a schematic sectional drawing which shows the continuously variable transmission conventionally known. It is a schematic sectional drawing which shows the specific structure of the continuously variable transmission conventionally known. It is an expanded sectional view equivalent to the B section of Drawing 4. It is a perspective view which takes out and shows a carrier. It is sectional drawing exaggeratingly showing the elastic deformation of an input side disk. It is sectional drawing which shows the conventional improved continuously variable transmission.

FIG. 1 shows an example of an embodiment of the present invention.
In this embodiment, the carrier 102 of the planetary gear type transmission 101 spans a plurality of planetary shafts 105 between the first and second connecting portions 103 and 104 each formed in a ring shape. Become. A planetary gear 106 is rotatably supported around the planetary shaft via a radial needle bearing 107. Then, the planetary gear 106 is meshed with a sun gear 109 and a ring gear 110 fixed at the tip of the hollow shaft 108, respectively.

  Further, a convex portion 113 is formed on the inner side surface of the first connecting portion 103 of the carrier 102 toward the input side disc 112 which is an outer disc of the toroidal type continuously variable transmission 111, and the convex portion 113 is engaged with the convex portion 113. A concave portion 114 is formed on the outer surface of the input side disk 112 at a position corresponding to the convex portion 113 so as to match. The outer diameter of the sun gear 109 is made larger than the inner diameter of the first connecting portion 103.

  In the case of the present embodiment, the outer diameter portion 117 of the flange portion 116 provided at one end portion of the input shaft 115 and the inner diameter portion 118 of the second connecting portion 104 of the carrier 102 are inserted in the axial direction so as to fit each other. It is formed into a shape, is splined in the circumferential direction, rotates together, and is further integrated by welding (beam welding or the like).

  In the case of the present embodiment configured as described above, since the outer diameter of the sun gear 109 is made larger than the inner diameter of the first connecting portion 103, the outer side of the input side disk 112 that is less deformed during operation. Since the portion closer to the inner diameter of the side surface and the inner diameter side surface of the first connecting portion 3 of the carrier 102 can be brought into contact with each other, fretting wear caused by friction between the input side disk 112 and the first connecting portion 103 is prevented. In addition, since the carrier 102 composed of the first connecting portion 103 and the second connecting portion 104 is integrally formed, the rigidity can be increased compared to the case where the connecting portions are connected to each other and integrated, and the planetary shaft 105 The support holes 119 and 119 for supporting the first connection part 103 and the second connection part 104 can be processed at the same time, so that the concentricity of the support holes 119 and 119 can be improved. Inclination and deviation can be prevented, transmission efficiency of the planetary gear type transmission 101 can be prevented from being lowered, and the flange portion 116 provided on the input shaft 115 and the carrier 102 are spline-coupled in an in-row shape, so that a loading nut is not necessary. As a result, the number of parts is reduced, and the cost can be reduced.

  In the present embodiment, the engagement position between the input shaft 115 and the carrier 102 is outside the outer diameter of the sun gear. With such a positional relationship, the sun gear 109 can be inserted into the carrier 102.

  The present invention can be used as a continuously variable transmission that combines a toroidal type continuously variable transmission and a planetary gear type transmission.

1 Toroidal continuously variable transmission 2, 2a, 2b Planetary gear type transmission 3, 3a Input shaft 4, 4a, 4b Input side disk 5 Output side disk 6 Power roller 7, 7a Carrier 8 Planetary gear 9 Planetary gear 10 First Transmission shaft 11 Sun gear 12 Sun gear 13 Second transmission shaft 14, 14a Hollow rotating shaft 15 Sun gear 16 Planet gear 17 Ring gear 18, 18a Second carrier 19 Planet gear 20 Planet gear 21, 21a Output shaft 22, 22a Second Ring gear 23, 23a Low speed clutch 24, 24a High speed clutch 25, 25a, 25b Planetary gear 26a, 26b Planetary gear 27 Transmission shaft 28 First sun gear 29 Second sun gear 30, 30a Ring gear 31 Third sun gear 32a , 32b Planetary gear 33 Housing 34 Strut 35 Connecting plate 36 Valve body 37 Support plate 38 Rolling Receptacle 39 Ball spline 40 Press device 41 Radial needle bearing 42 Intermediate support plates 43, 43a, 43b, 43c First connection plate 44 Second connection plate 45 First planetary shaft 46 Second planetary shaft 47 Third planetary shafts 48a, 48b, 48c Radial needle bearing 49 Cylindrical portion 50 Loading nut 51 Annulus portion 52 Protruding portion 53 Notch 54 Drive shaft 55, 55a Concavity portion 56, 56a Convex portion 57 Connecting portion 58 Convex portion 59 Convex portion 60 Concavity portion 61 62a, 62b Film 63 Minute recessed portion 64 Groove groove 65a, 65b Annular groove 66 Radial groove 101 Planetary gear type transmission 102 Carrier 103 First connecting portion 104 Second connecting portion 105 Planetary shaft 106 Planetary gear 107 Radial needle bearing 108 Hollow shaft 109 Sun gear 100 ring gear 111 toroidal type continuously variable transmission 112 input side disc 113 convex portion 114 concave portion 115 input shaft 116 flange 117 flange outer diameter 118 second connection portion inner diameter portion 119 supporting hole

Claims (3)

  An input shaft, a toroidal-type continuously variable transmission, and a planetary gear-type transmission, which are arranged concentrically with each other, include a toroidal-type continuously variable transmission, an inner disk and inner disks on both sides of the inner disk. A pair of outer disks supported concentrically and independently of the inner disk so as to freely rotate, and a plurality of powers sandwiched between both side surfaces of the inner disk and the side surfaces of the outer disk. The planetary gear mechanism includes a sun gear around the input shaft, a ring gear arranged around the sun gear, and a planetary gear arranged between the sun gear and the ring gear; A carrier for supporting the planetary gear, and these toroidal-type continuously variable transmission and planetary gear-type transmission constitute an outer disk and a planetary gear-type transmission constituting the toroidal-type continuously variable transmission. In the continuously variable transmission in which the one outer disk and the carrier rotate in synchronization with each other, a flange portion extending radially outward is provided on the input shaft, and the flange portion The continuously variable transmission is characterized in that the outer diameter of the sun gear is larger than the inner diameter of the carrier on the side adjacent to the outer disk.   A step portion is provided on the outer disk side at the tip of the flange portion with respect to the axial direction, an engagement portion that engages with the step portion is provided on the carrier, and the flange portion and the carrier are unevenly engaged with each other in the circumferential direction. The continuously variable transmission according to claim 1, wherein:   The continuously variable transmission according to claim 1, wherein the flange portion and the carrier are welded.

Images