JP2006009995A - Toroidal continuously variable transmission - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To dispense with forming a supply/discharge hole in an input shaft 5 to supply/discharge pressurized oil into the hydraulic pressure chamber 38 of a pressing device 37, reduce size and weight by preventing the diameter of the input shaft 5 from becoming large, and reduce cost. <P>SOLUTION: The supply/discharge of the pressurized oil into and from the hydraulic pressure chamber 38 are performed through an oil passage 49 formed in a support post 17a for supporting an output side disk 9. Since the support post 17a does not receive a large force, it must not be increased in size by forming the oil passage 49 therein. The hole for supplying/discharging the pressurized oil into and from the hydraulic pressure chamber 38 must not be formed in the input shaft 5 receiving a large force. <P>COPYRIGHT: (C)2006,JPO&NCIPI

Description

  The present invention relates to an improvement of a toroidal continuously variable transmission that is used as an automatic transmission for a vehicle (automobile) or as a transmission for adjusting the operating speed of various industrial machines such as a pump.

  The use of a toroidal-type continuously variable transmission as an automatic transmission for automobiles has been studied and, for example, as described in Non-Patent Document 1, has been partially implemented. The structure and theory of the toroidal continuously variable transmission are described in detail in Non-Patent Document 2. As is well known and described in many documents including Non-Patent Document 2, the toroidal continuously variable transmission has a plurality of power rollers sandwiched between an input side disk and an output side disk, Power is transmitted at the rolling contact portion between the side surfaces of the two disks and the peripheral surfaces of the power rollers. The toroidal continuously variable transmission is provided with a pressing device in order to prevent an excessive slip from occurring at the rolling contact portion and to efficiently transmit power. During operation of the toroidal continuously variable transmission, the surface pressure of each of the rolling contact portions is ensured based on the pressing force generated by the pressing device.

  Conventionally, a mechanical loading cam device has been used as such a pressing device. However, by using a hydraulic pressing device, the surface pressure of each of the rolling contact portions can be adjusted according to the operating conditions. It is considered to make fine adjustments. A toroidal-type continuously variable transmission incorporating such a hydraulic pressing device is known and described in many documents, but as a document describing a specific structure, Patent Document 1 There is. This Patent Document 1 describes a specific structure of a continuously variable transmission that is a coaxial combination of a toroidal type continuously variable transmission and a planetary gear type transmission. 3 to 4 show the continuously variable transmission described in Patent Document 1 as described above.

  This continuously variable transmission is composed of a combination of a toroidal type continuously variable transmission 1 and first to third planetary gear type transmissions 2 to 4, and is supported concentrically and relatively rotatably. An input shaft 5, a transmission shaft 6, and an output shaft 7 are included. The third planetary gear type transmission 4 is connected to the transmission shaft 6 in a state where the first and second planetary gear type transmissions 2 and 3 are spanned between the input shaft 5 and the transmission shaft 6. And the output shaft 7 are provided in a state of being spanned.

  Of these, the toroidal-type continuously variable transmission 1 is a pair of input-side disks 8a and 8b, each of which is an outer disk described in the claims, and a second disk also described in the claims. An integrated output side disk 9 that is an inner side disk and a plurality of power rollers 10 and 10 are provided. Note that one input side disk 8a of the pair of input side disks 8a and 8b corresponds to the first disk described in the claims. These two input-side disks 8a and 8b are positioned at two positions separated from each other in the axial direction in the input shaft 5 in a state in which one axial side surfaces, which are toroidal curved surfaces each having a circular arc cross section, are opposed to each other. Rotation that is concentric with each other and synchronized with the input shaft 5 is supported freely. Further, the output side disk 9 has both axial side surfaces, each of which is a toroidal curved surface having a circular arc cross section, at a position between the input side disks 8a and 8b around the intermediate portion of the input shaft 5. In a state of being opposed to one side surface in the axial direction of the input side discs 8a and 8b, the input side discs 8a and 8b are concentrically supported and freely supported for relative rotation with respect to the both input side discs 8a and 8b. .

  Further, a plurality of each of the power rollers 10 and 10 is sandwiched between both side surfaces in the axial direction of the output side disk 9 and one side surface in the axial direction of the both input side disks 8a and 8b. Each of the power rollers 10 and 10 has a spherical convex surface, and both the input side and output side discs 8a are sandwiched between the input side discs 8a and 8b and the output side disc 9. , 8b, 9 can freely transmit power. The power rollers 10 and 10 are rotatably supported on the inner surfaces of the trunnions 11 and 11. The trunnions 11 and 11 support the pivot shafts 12 and 12 provided at both ends of the trunnions 11 and 13b on support plates 13a and 13b installed in the casing 14 so as to be swingable and axially displaceable. . Both the support plates 13a and 13b are supported on both ends of support posts 17 and 17 that are supported and fixed in the casing 14 via the connecting plate 15 and the actuator body 16, respectively.

  Further, the output side disk 9 is rotatably supported by a pair of thrust angular ball bearings 19 and 19 between the support ring portions 18 and 18 provided at the intermediate portions of the support posts 17 and 17. Yes. Further, a base end portion (left end portion in FIG. 3) of the hollow rotary shaft 20 is spline-engaged with the output side disk 9. The hollow rotary shaft 20 is inserted inside the input side disk 8a on the side far from the engine (right side in FIG. 3) so that the power transmitted to the output side disk 9 can be taken out. Further, the first planetary gear type transmission 2 is configured at a portion protruding from the outer side surface (right side surface in FIG. 3) of the input side disk 8a at the tip end portion (right end portion in FIG. 3) of the hollow rotary shaft 20. For this purpose, the first sun gear 21 is fixed.

  On the other hand, between the portion protruding from the hollow rotary shaft 20 at the tip end portion (the right end portion in FIG. 3) of the input shaft 5 inserted inside the hollow rotary shaft 20 and the input-side disk 8a. The first carrier 22 corresponding to the carrier described in the above-mentioned range is provided so that the input side disk 8a and the input shaft 5 rotate in synchronization with each other. Then, the first and second planetary gear type shifts each having a double pinion type at circumferentially equidistant positions (generally 3 to 4 positions) on both side surfaces in the axial direction of the first carrier 22. Planetary gears 23 to 25 for constituting the machines 2 and 3 are rotatably supported. Further, a first ring gear 26 is rotatably supported around one half (the right half in FIG. 3) of the first carrier 22.

  Among the planetary gears 23 to 25, the planetary gear 23 provided on the inner side in the radial direction of the first carrier 22 near the toroidal type continuously variable transmission 1 (leftward in FIG. 3) is the first sun gear 21. Is engaged. Further, the planetary gear 24 provided on the inner side with respect to the radial direction of the first carrier 22 on the side far from the toroidal-type continuously variable transmission 1 (the right side in FIG. 3) is a base end portion of the transmission shaft 6 (in FIG. 3). It meshes with the second sun gear 27 fixed at the left end). The remaining planetary gears 25 provided on the outer side in the radial direction of the first carrier 22 have a larger axial dimension than the planetary gears 23 and 24 provided on the inner side, so that both the planetary gears 23 and 24 are provided. Is engaged. Further, the remaining planetary gear 25 and the first ring gear 26 are meshed with each other.

  On the other hand, a second carrier 28 for constituting the third planetary gear type transmission 4 is coupled and fixed to a base end portion (left end portion in FIG. 3) of the output shaft 7. The second carrier 28 and the first ring gear 26 are coupled via a low speed clutch 29. Further, a third sun gear 30 is fixedly provided near the tip of the transmission shaft 6 (near the right end in FIG. 3). A second ring gear 31 is disposed around the third sun gear 30, and a high speed clutch 32 is provided between the second ring gear 31 and a fixed portion such as the casing 14. Further, a plurality of planetary gears 33 and 34 disposed between the second ring gear 31 and the third sun gear 30 are rotatably supported on the second carrier 28. The planetary gears 33 and 34 mesh with each other, and the planetary gear 33 provided on the inner side with respect to the radial direction of the second carrier 28 is provided on the third sun gear 30 and the planetary gear 34 provided on the outer side is provided on the first. The two ring gears 31 mesh with each other.

  During operation of the continuously variable transmission configured as described above, the drive shaft 35 is rotationally driven via a torsion damper 36 by an engine crankshaft (not shown), and the input shaft 5 is further driven by this drive shaft 35. Rotating drive. Then, the power transmitted from the input shaft 5 to the integrated output side disk 9 through the pair of input side disks 8 a and 8 b and the power rollers 10 and 10 is taken out through the hollow rotary shaft 20. In the low speed mode in which the low speed clutch 29 is connected and the high speed clutch 32 is disconnected, the rotational speed of the input shaft 5 is made constant by changing the gear ratio of the toroidal continuously variable transmission 1. The rotation speed of the output shaft 7 can be freely converted into forward rotation and reverse rotation with the stop state therebetween. On the other hand, in the high speed mode in which the low speed clutch 29 is disconnected and the high speed clutch 32 is connected, the output shaft 7 is rotated in the direction in which the vehicle moves forward. In this state, the rotational speed of the output shaft 7 can be increased as the gear ratio of the toroidal type continuously variable transmission 1 is changed to the speed increasing side.

  During the operation of the toroidal type continuously variable transmission 1 constituting the continuously variable transmission as described above, the side surfaces of the disks 8a, 8b, 9 and the peripheral surfaces of the power rollers 10, 10 as described above. It is necessary to ensure the surface pressure of the rolling contact portion (traction portion). Therefore, in the case of the structure described in Patent Document 1, a hydraulic pressing device 37 is provided between the input shaft 5 and the input side disk 8b. The pressing device 37 is a double piston type provided with a pair of hydraulic chambers 38a and 38b that can be expanded and contracted in the axial direction. However, the hydraulic pressing device is not limited to the double piston type, and may be a single piston type as shown in FIG. In short, the type is selected according to the relationship between the maximum value of the required pressing force and the maximum value of the obtained hydraulic pressure. Regardless of which type is adopted, in the case of a structure equipped with a hydraulic pressing device 37, the surface pressure applied to each traction section can be controlled by controlling the hydraulic pressure introduced into each hydraulic chamber 38a, 38b. It can always be adjusted to an appropriate value. Therefore, the efficiency and durability of the toroidal type continuously variable transmission 1 can be ensured at a higher level than the loading cam type pressing device as described above.

  In the case of the conventional structure described in Patent Document 1, the pressure oil is fed into each of the hydraulic chambers 38a and 38b from an oil feed pump installed at an end plate 39 portion that closes the front end opening of the casing 14. The oil supply holes 40a and 40b provided in the center of the drive shaft 35 and the input shaft 5 are configured. For this purpose, the base end portion (the left end portion in FIGS. 3 and 5) of the input shaft 5 is connected to the oil supply hole 40 b in addition to the oil supply hole 40 b and the oil passage through which the outer peripheral surface of the input shaft 5 communicates. Holes 41a and 41b are also formed.

  Regardless of whether the pressing device is of a double piston type or a single piston type, the drive shaft 35 and the input shaft 5 are provided with oil supply holes 40a, 40b and oil passage holes 41a, 41b, so that the weight can be reduced. In addition to the difficulty of ensuring durability, it is inevitable that costs will increase. The reason for this is as follows. Since the reaction force of the pressing force generated by the pressing device 37 is supported at the base end portion of the input shaft 5, a large stress is generated. In order to prevent the occurrence of damage such as cracks at the base end portion of the input shaft 5 in which the oil supply hole 40b and the oil passage holes 41a and 41b are formed, regardless of such a large stress, The diameter of the shaft 5 needs to be increased, and the toroidal-type continuously variable transmission including the input shaft 5 becomes large, resulting in an increase in weight. In addition, the operation of forming the oil supply hole 40b and the oil passage holes 41a and 41b at the base end portion of the input shaft 5 made of hard metal such as bearing steel is troublesome and causes a high processing cost.

Japanese Patent Laid-Open No. 2004-084712 Motoo Aoyama, “Red Badge Super Illustrated Series / A book that shows 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 has been invented to realize a structure of a toroidal type continuously variable transmission that can achieve both weight reduction and ensuring durability and can be manufactured at low cost.

The toroidal continuously variable transmission of the present invention is similar to the previously known toroidal continuously variable transmissions described above, and includes first and second disks, a plurality of power rollers, a pressing device, and a support. With post.
Of these, the first and second discs are supported concentrically and relatively rotatably, with one axial side surface having a circular arc cross section facing each other.
Each of the power rollers is sandwiched between the two disks in a state where the peripheral surfaces of the power rollers are in rolling contact with the side surfaces of the two disks.
The pressing device presses the first disk toward the second disk and is hydraulic.
Further, the support post rotatably supports the end of the second disk.
In particular, in the toroidal type continuously variable transmission of the present invention, pressure oil is supplied to and discharged from the hydraulic chamber of the pressing device through an oil passage provided in the support post.

  In the case of the toroidal-type continuously variable transmission of the present invention configured as described above, both weight reduction and ensuring of durability can be achieved at a low cost. In other words, the support post for supplying and discharging the pressure oil into and from the hydraulic chamber of the pressing device does not receive the reaction force generated by the pressing device, so it does not need to be made of extremely hard metal. It is not necessary to make the wall thickness particularly large. For this reason, the weight of the support post does not increase, and an operation of forming an oil passage on the support post can be easily performed, so that weight reduction, durability can be secured, and cost can be reduced.

In carrying out the present invention, preferably, as described in claim 2, a rotating shaft, a pair of outer disks, an inner disk formed by combining a single element or a pair of elements, and a plurality of supports A member and a plurality of power rollers are provided.
Both of these outer discs are located at two positions separated from each other in the axial direction at the intermediate portion of the rotary shaft in a state where the axial side surfaces of each of the outer discs are arcuate in cross section. Synchronized rotation is supported freely.
In addition, the inner disk is in a state where both axial side surfaces having an arc cross section are opposed to one axial side surface of each outer disk around the intermediate portion of the rotating shaft between the outer disks. The relative rotation with respect to the rotating shaft is freely supported.
The supporting members are pivoted in a twisted position with respect to the rotating shaft, each in a plurality of positions between both axial side surfaces of the inner disk and one axial side surface of the outer disk with respect to the axial direction. Oscillating displacement about the center is freely provided.
Each of the power rollers is rotatably supported by the support member and has a spherical convex surface that is in rolling contact with both axial sides of the inner disk and one axial side of each outer disk. It has been made.
Further, a pair of support posts having support ring portions at their respective intermediate portions are fixed between both axial side surfaces of the inner disk and one axial side surface of each outer disk. Further, both ends in the axial direction of the inner disk, which is the second disk, are rotatably supported by the support ring portions of the two support posts, and one of the pair of outer disks, which is the first disk. A hydraulic pressing device is provided between the outer disk and one end of the rotating shaft.
Then, pressure oil is supplied to and discharged from the hydraulic chamber of the pressing device through an oil passage provided in one of the pair of support posts.
If the present invention is implemented with such a structure as described in Patent Document 1, an oil supply hole and an oil passage hole for supplying and discharging pressure oil into and from the hydraulic chamber are formed on the rotating shaft. Therefore, the diameter of the rotating shaft can be kept small, and the toroidal continuously variable transmission can be effectively reduced in size and weight. Further, the both support posts only support the inner disk rotatably, and a large radial load or an axial load does not act on the support posts. Therefore, it is difficult to cause a problem that the strength of the support post is reduced due to the provision of the oil passage in the one support post, and it is not necessary to enlarge the support post. The toroidal continuously variable transmission It does not hinder the overall size and weight reduction.

When carrying out the invention described in claim 2 as described above, for example, as described in claim 3, the axial displacement of one outer disk, which is the first disk, with respect to the rotation axis by a ball spline. Support freely. A spline groove for forming an inner cylindrical surface portion provided at one end in the axial direction near the inner disk of the inner peripheral surface of the one outer disk and forming the ball spline on the outer peripheral surface of the intermediate portion of the rotating shaft. The part removed from the slidable surface is brought into sliding contact with oil tightness.
Further, an outer diameter side cylindrical surface portion provided at one end in the axial direction near the inner disk of the outer peripheral surface of the one outer disk is formed on a part of the inner peripheral surface of the support ring portion of the one support post. The fixed cylindrical surface portion is slidably contacted with oil tightness.
Further, among the one outer disk, a second oil passage formed in the axial direction one end portion near the inner disk in a state of passing through this portion in the radial direction and the oil passage provided in the one support post. Communicate with the road.
Then, the oil passage and the hydraulic chamber of the pressing device are communicated with each other via the second oil passage and the spline groove.
By adopting such a configuration, the oil passage provided in the one support post and the hydraulic chamber of the pressing device are reliably communicated with each other, and pressure oil is efficiently supplied to and discharged from the hydraulic chamber. Can be made.

Alternatively, as described in claim 4, a pressing device is configured in combination with one outer disk which is the first disk, and a cylinder end plate constituting a hydraulic chamber is formed between the outer disk and the rotating shaft. On the other hand, it is externally fitted and fixed so as to be rotatable in synchronization with the rotating shaft.
Further, the one outer disk is supported so as to be axially displaceable with respect to the rotary shaft in a state where a gap through which oil can flow is interposed between the outer disc and the outer peripheral surface of the rotary shaft.
Further, the inner cylindrical surface portion provided at one end in the axial direction near the inner disk of the inner peripheral surface of the one outer disk is slidably contacted with the outer peripheral surface of the intermediate portion of the rotating shaft while maintaining oil tightness. Let
Further, an outer diameter side cylindrical surface portion provided at one end in the axial direction near the inner disk of the outer peripheral surface of the one outer disk is formed on a part of the inner peripheral surface of the support ring portion of the one support post. The fixed cylindrical surface portion is brought into sliding contact with oil tightness.
Further, among the one outer disk, a second oil passage formed in the axial direction one end portion near the inner disk in a state of passing through this portion in the radial direction and the oil passage provided in the one support post. Communicate with the road.
Then, the oil passage and the hydraulic chamber of the pressing device are communicated with each other via the second oil passage and the gap.
Even with such a configuration, the oil passage provided in the one support post and the hydraulic chamber of the pressing device can reliably communicate with each other, and the hydraulic oil can be efficiently supplied to and discharged from the hydraulic chamber. it can.

Further, when the invention described in claims 2 to 4 is carried out, the inner disk is preferably an integrated output disk as described in claim 5.
Further, the base end portion of the hollow rotary shaft, which is disposed around the middle portion of the rotary shaft so as to freely rotate relative to the rotary shaft, is coupled to the output side disk for transmission of rotational force.
Further, the intermediate portion of the hollow rotary shaft is inserted through the inner diameter side of the other outer disk, and the tip of the hollow rotary shaft is inserted into the side surface of the outer disk in the axial direction opposite to the output disk. The rotation of the output side disk can be taken out freely by projecting from the disk.
In this case, for example, as described in claim 6, a planetary gear type transmission is provided adjacent to the other outer disk and concentrically with the outer disk. A sun gear of the planetary gear type transmission is provided at the tip of the hollow rotary shaft, and a carrier of the planetary gear type transmission is provided between the other outer disk and the rotary shaft.
If comprised in this way, the structure which can accommodate the cross-sectional area as the whole toroidal type continuously variable transmission small can be implement | achieved.
A structure capable of obtaining a wide gear ratio can be realized by combination with a planetary gear type transmission.

  FIG. 1 shows Embodiment 1 of the present invention corresponding to claims 1 to 3, 5 and 6. The feature of this embodiment is that the surface pressure of the rolling contact portion between the side surfaces of the pair of input side disks 8a and 8b and the output side disk 9 and the peripheral surfaces of the power rollers 10, 10 (see FIG. 4). The pressure oil is supplied to and discharged from the hydraulic chamber 38 of the pressing device 37. Since the structure and operation of the other parts are the same as those of the toroidal type continuously variable transmission 1 incorporated in the continuously variable transmission shown in FIGS. 3 to 4 described above, the illustration and description of the equivalent parts are omitted or simplified. In the following, the description will focus on the features of this embodiment.

  The input side disk 8b, which is the first disk and one of the outer disks, can be freely rotated in synchronization with the input shaft 5 by the ball spline 42 with respect to the input shaft 5 which is the rotation shaft, and in the axial direction. Supports displaceability. For this purpose, a male ball spline groove 43 is formed on the outer peripheral surface of the intermediate portion proximal end (left side in FIG. 1) of the input shaft 5, and a female ball spline groove 44 is formed on the inner peripheral surface of the input side disk 8b. A plurality of balls 45 and 45 are formed between the ball spline grooves 43 and 44 so as to be freely rollable.

  Further, an inner diameter side cylindrical surface portion 46 is provided at one axial end portion (right end portion in FIG. 1) of the input side disc 8b near the output side disc 9 which is an inner disc. On the other hand, an outer diameter side cylindrical surface portion 47 is formed in a portion of the intermediate portion outer peripheral surface of the input shaft 5 that is axially disengaged from the male ball spline groove 43. Then, the inner ring side cylindrical surface portion 46 and the outer diameter side cylindrical surface portion 47 are brought into contact with each other by bringing the seal ring locked to the axially intermediate portion of the outer diameter side cylindrical surface portion 47 into sliding contact with the inner diameter side cylindrical surface portion 46. The sliding contact is made while maintaining oil tightness.

  In addition, a second oil passage 48 is formed in one end of the input side disk 8b in the axial direction near the output side disk 9 so as to penetrate this part in the radial direction. The inner diameter side opening end of the second oil passage 48 communicates with the end of the male ball spline groove 43 formed on the outer peripheral surface of the intermediate portion of the input shaft 5, and the outer diameter side opening end is one of the outer diameter side opening ends. It communicates with the inner diameter side opening end of the oil passage 49 provided in the support post 17a. Also, the outer diameter side opening end of the oil passage 49 is open to both end surfaces of the support post 17a, and the both end surface opening portions are the connecting plate 15 and the actuator body 16 (see FIGS. 3 to 4). It communicates with the pressure oil supply / discharge flow path provided inside.

  In order to make the inner diameter side opening end of the oil passage 49 and the outer diameter side opening end of the second oil passage 48 communicate in an oil-tight manner, a piece of the support ring portion 18a of the support post 17a is provided. A second inner diameter side cylindrical surface portion 50 is formed on the inner peripheral surface of the half portion (left half portion in FIG. 1). A second outer-diameter-side cylindrical surface portion 51 is formed on one end portion in the axial direction near the output-side disc 9 in the outer peripheral surface of the input-side disc 8b. Then, a pair of seal rings that are engaged with the second outer diameter side cylindrical surface portion 51 at positions sandwiching the outer diameter side opening ends of the second oil passage 48 from both sides in the axial direction. The two inner diameter side cylindrical surface portions 50 are in sliding contact.

  In the case of the present embodiment configured as described above, the pressure oil supply / discharge passage provided in the connecting plate 15 and the actuator body 16 and the hydraulic chamber 38 of the pressing device 37 are connected to the oil passage 49. The second oil passage 48 and the male ball spline groove 43 communicate with each other. Accordingly, by introducing a predetermined hydraulic pressure into the supply / discharge flow path, this hydraulic pressure is introduced into the hydraulic chamber 38, and the pressing device 37 generates a predetermined pressing force. A clearance channel is set in a fitting portion between the inner diameter side portion of the cylinder end plate 52 and the inner diameter side portion of the input side disk 8b constituting the pressing device 37, and the male ball spline groove 43 and the hydraulic pressure are set. The chamber 38 is in communication.

  In the case of the toroidal-type continuously variable transmission according to the present embodiment configured as described above, it is possible to achieve both weight reduction and ensuring durability, and at a low cost. That is, the support post 17a provided with the oil passage 49 for supplying and discharging the pressure oil into the hydraulic chamber 38 of the pressing device 37 only supports the output side disk 9 rotatably. Neither the pressing force generated by the pressing device 37 nor the reaction force is received. For this reason, it is not necessary to make it from an extremely hard metal like bearing steel, and it is not necessary to make it thick especially by providing the oil passage 49. Therefore, the weight of the support post 17a is not increased, and the operation of forming the oil passage 49 in the support post 17a can be easily performed. On the other hand, the input shaft 5 which is a member for transmitting a large power and further needs to be made of a hard metal to receive the reaction force generated by the pressing device 37 is shown in FIGS. It is not necessary to form the oil supply holes 40b and the oil passage holes 41a and 41b as in the conventional structure. Therefore, the strength required for the input shaft 5 can be ensured without particularly increasing the diameter of the input shaft 5. Moreover, the trouble of processing the input shaft 5 made of hard metal can be reduced. As a result, it is possible to reduce the weight, ensure the durability, and reduce the cost.

  FIG. 2 shows a second embodiment of the present invention corresponding to claims 1, 2, 4 to 6. In the case of the present embodiment, the pressing device 37 is constituted, and the cylinder end plate 52 constituting the hydraulic chamber 38 is formed between the rotating disk and the input side disk 8b which is the outer disk (left side in FIG. 2). The input shaft 5 is externally fixed so as to be rotatable in synchronism with the input shaft 5 by interference fitting or uneven engagement. The input side disk 8b is supported around the input shaft 5 via a ball bush 53 so as to be freely displaced in the axial direction. Further, the outer peripheral edge portion of the cylinder end plate 52 and the outer peripheral edge portion of the input side disk 8b are engaged with each other. Accordingly, the cylinder end plate 52 and the input side disk 8b rotate in synchronization with the input shaft 5.

  In the case of the present embodiment configured as described above, the pressure oil supply / discharge passage provided in the connecting plate 15 and the actuator body 16 (see FIGS. 3 to 4) and the hydraulic chamber 38 of the pressing device 37 are provided. The oil passage 49 provided in the support post 17 a communicates with the second oil passage 48 provided in the input side disk 8 b through the clearance of the ball bush 53. Since the configuration and operation of the other parts are the same as those in the first embodiment described above, a duplicate description is omitted.

  The present invention is not limited to the structure shown in the drawings, and can be implemented with other structures known in the art. In other words, in the illustrated example, the present invention is applied to a continuously variable transmission device that is a combination of a double cavity type half toroidal continuously variable transmission and a planetary gear type transmission. On the other hand, the present invention is not limited to such a structure, and can be implemented by a continuously variable transmission including a combination of a full toroidal toroidal continuously variable transmission and a planetary gear type transmission. Furthermore, the present invention can also be implemented in a structure that is used alone with a toroidal continuously variable transmission, regardless of whether it is a half toroidal type or a full toroidal type.

BRIEF DESCRIPTION OF THE DRAWINGS FIG. 1 is a cross-sectional view of an essential part showing Embodiment 1 of the present invention. Sectional drawing which shows the principal part which shows the same Example 2. FIG. Sectional drawing which shows the 1st example of the continuously variable transmission incorporating the conventional toroidal type continuously variable transmission. AA sectional drawing of FIG. The principal part sectional drawing which shows the 1st example of the continuously variable transmission which integrated the conventional toroidal type continuously variable transmission.

Explanation of symbols

DESCRIPTION OF SYMBOLS 1 Toroidal type continuously variable transmission 2 1st planetary gear type transmission 3 2nd planetary gear type transmission 4 3rd planetary gear type transmission 5 Input shaft 6 Transmission shaft 7 Output shaft 8a, 8b Input side disk 9 Output side disk DESCRIPTION OF SYMBOLS 10 Power roller 11 Trunnion 12 Axis 13a, 13b Support plate 14 Casing 15 Connection plate 16 Actuator body 17, 17a Support post 18, 18a Support ring part 19 Ball bearing 20 Hollow rotating shaft 21 First sun gear 22 First carrier 23 Planetary gear 24 planetary gear 25 planetary gear 26 first ring gear 27 second sun gear 28 second carrier 29 low speed clutch 30 third sun gear 31 second ring gear 32 high speed clutch 33 planetary gear 34 planetary gear 35 drive shaft 36 torsion damper 37 Pressing device 38, 38a, 38b Hydraulic chamber 39 End 40a, 40b Oil supply hole 41a, 41b Oil passage hole 42 Ball spline 43 Male ball spline groove 44 Female ball spline groove 45 Ball 46 Inner diameter side cylindrical surface portion 47 Outer diameter side cylindrical surface portion 48 Second oil passage passage 49 Oil passage passage 50 First Second inner diameter side cylindrical surface part 51 Second outer diameter side cylindrical surface part 52 Cylinder end plate 53 Ball bushing

Claims (6)

  The first and second discs are concentrically and relatively rotatably supported with one axial side surface facing each other, each having an arc of cross section, and the respective circumferences on the side surfaces of both discs. A plurality of power rollers sandwiched between the two disks in a rolling contact state, a hydraulic pressing device that presses the first disk toward the second disk, and the first In a toroidal-type continuously variable transmission having a support post that rotatably supports the end of the second disk, pressure oil is supplied to and discharged from the hydraulic chamber of the pressing device in the support post. A toroidal-type continuously variable transmission characterized by being performed through an oil passage.   Rotation synchronized with this rotating shaft is carried out at two positions separated in the axial direction at the intermediate portion of this rotating shaft with the rotating shaft and each axial side surface having an arc cross section facing each other. A pair of outer disks that are freely supported, and a portion between the outer disks around the middle part of the rotating shaft, and both axial side surfaces that are arc-shaped in cross section are formed on one axial side surface of each outer disk. In an opposed state, an inner disk that is supported by relative rotation with respect to the rotating shaft and is integrally or by combining a pair of elements, both axial side surfaces of the inner disk with respect to the axial direction, A plurality of support members each provided at a position between one side surface in the axial direction of the outer disk and provided with a swinging displacement centering on a pivot that is twisted with respect to the rotation shaft, and each of these support members Supported rotatably Power rollers each having a spherical convex surface in rolling contact with both axial sides of the inner disk and one axial side of each outer disk, and both axial sides of the inner disk and the respective A pair of support posts having a support ring portion at each intermediate portion is fixed between one side surface in the axial direction of the outer disk, and both end portions in the axial direction of the inner disk, which is the second disk, are fixed to the both support posts. And a hydraulic pressing device is provided between one outer disk of the pair of outer disks and one end of the rotating shaft as a first disk. The toroidal-type non-loading device according to claim 1, wherein supply and discharge of the pressure oil to and from the hydraulic chamber of the pressing device is performed through an oil passage provided in one support post of the pair of support posts. Step transmission.   One outer disk, which is the first disk, is supported by a ball spline so as to be axially displaceable with respect to the rotation shaft, and one axial end of the inner disk near the inner disk on the inner peripheral surface of the one outer disk The cylindrical surface portion on the inner diameter side is slidably brought into contact with the outer peripheral surface of the rotating shaft away from the spline groove for forming the ball spline while maintaining oil tightness. Oil-tightness is maintained in a fixed cylindrical surface portion formed on a part of the inner peripheral surface of the support ring portion of one support post, with the outer diameter side cylindrical surface portion provided at one end in the axial direction near the inner disk of the outer peripheral surface. The second oil passage and the one support post formed in the state of passing through this portion in the axial direction at one end portion in the axial direction near the inner disk of the one outer disk. Inside The oil passage provided is communicated, and the oil passage and the hydraulic chamber of the pressing device are communicated via the second oil passage and the spline groove. Toroidal continuously variable transmission.   Combined with one outer disk, which is the first disk, constitutes a pressing device, and the cylinder end plate constituting the hydraulic chamber between the outer disk and the outer disk is rotatable with respect to the rotation axis in synchronization with the rotation axis. An external displacement is fixed, and the one outer disk is displaced in the axial direction with respect to the rotary shaft in a state in which a gap through which oil can flow is interposed between the outer disc and the outer peripheral surface of the rotary shaft. The inner cylindrical surface portion provided at one end in the axial direction near the inner disk of the inner peripheral surface of the one outer disk is held freely, and the intermediate outer peripheral surface of the rotating shaft is kept oil tight. Of the outer peripheral surface of the one outer disk, and the outer diameter side cylindrical surface portion provided at one end in the axial direction near the inner disk is connected to the inner peripheral surface of the support ring of one support post. Oil tightness is maintained on the fixed cylindrical surface formed on the The second oil passage and the one support post formed in the state of passing through this portion in the axial direction at one end portion in the axial direction near the inner disk of the one outer disk. An oil passage provided in the passage is communicated, and the oil passage and the hydraulic chamber of the pressing device are communicated with each other via the second oil passage and the gap. The toroidal continuously variable transmission described.   The inner disk is an integrated output disk, and the base end of the hollow rotating shaft, which can freely rotate relative to the rotating shaft around the middle of the rotating shaft, can be used to transmit rotational force to the output disk. In addition, the hollow rotary shaft is inserted through the inner diameter side of the other outer disk, and the tip end of the hollow rotary shaft is inserted on the opposite side of the outer disk in the axial direction. The toroidal continuously variable transmission according to any one of claims 2 to 4, wherein the rotation of the output-side disk can be taken out freely by projecting from the side surface.   A planetary gear type transmission is provided adjacent to the other outer disk and concentrically with the outer disk, the sun gear of the planetary gear type transmission is disposed at the tip of the hollow rotation shaft, and the other outer disk and the rotation shaft are connected to each other. The toroidal continuously variable transmission according to claim 5, wherein a carrier for the planetary gear type transmission is provided between each of them.

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