JP2009197891A - Continuously variable transmission - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To provide a continuously variable transmission constructed with a carrier 23a whose elastic deformation is reduced, to compatibly secure transmitting efficiency and durability and miniaturize itself. <P>SOLUTION: An inner diameter d<SB>51</SB>of each of disk side supporting holes 51, 51 which are provided in a disk side connection plate 37a for supporting the one-side ends of first and second disk side planetary shafts 41a, 43a internally fitted thereto, respectively, is smaller than an inner diameter D<SB>52</SB>of each of counter disk side supporting holes 52, 52 which are provided in a supporting plate 36a and a counter disk side connection plate 39a for supporting the other-side ends of the planetary shafts 41a, 43a internally fitted thereto, respectively. <P>COPYRIGHT: (C)2009,JPO&INPIT

Description

  The present invention relates to a toroidal continuously variable transmission and a planetary gear type transmission that are used as an automatic transmission for vehicles (automobiles) or as a transmission for adjusting the operating speed of various industrial machines such as pumps. The present invention relates to an improvement of a combined continuously variable transmission. Specifically, it is possible to reduce the elastic deformation of the carrier constituting the continuously variable transmission, and to realize a structure in which transmission efficiency, durability and downsizing can be arranged side by side.

  The use of a toroidal type continuously variable transmission as an automatic transmission for automobiles has been studied and implemented in part. In addition, as described in Patent Documents 1 to 4 and the like, 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. 4 to 7 show the continuously variable transmission described in Patent Documents 3 and 4 among them. 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 outer disks 10a and 10b, an integrated inner disk 11 corresponding to the second disk described in the claims, and a plurality of power rollers 12. , 12. Outer disks 10a and 10b among these are connected concentrically with each other via the input rotary shaft 5 so as to freely rotate in synchronization. The inner disk 11 is supported between the outer disks 10a and 10b so as to be concentric with the outer disks 10a and 10b and to be relatively rotatable with respect to the outer disks 10a and 10b. . Further, a plurality of each of the power rollers 12 and 12 are provided between two axial side surfaces of the inner disk 11 and one axial side surface of the outer disks 10a and 10b (two in the illustrated example). ) Are pinched one by one. Power is transmitted between the outer disks 10a and 10b and the inner disk 11 while rotating with the rotation of the outer disks 10a and 10b.

  The inner 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. Yes. Further, support plates 16 and 16 are supported in the vicinity of both ends of the both columns 14 and 14, respectively. Then, a plurality of trunnions (support members) 17, 17 are provided between the support plates 16, 16, and swing and axial directions about pivots 18, 18 provided concentrically with each other at both ends (FIG. 4). (5 up and down direction) is supported. Further, the power rollers 12 and 12 are respectively rotated on the inner side surfaces (surfaces facing each other) of the trunnions 17 and 17 through support shafts 19 and 19 and a plurality of sets of rolling bearings, 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 axial side surfaces of the outer disks 10a, 10b and the axial side surfaces of the inner disk 11.

  In the case of the illustrated continuously variable transmission, the base end portion (left end portion of FIG. 4) of the input rotary shaft 5 is coupled to the crankshaft of an engine (drive source) (not shown) via the input shaft 3, The crankshaft is configured to rotationally drive the input rotary shaft 5. Further, a hydraulic pressing device 20 is provided between the base end portion of the input rotating shaft 5 and the outer disk 10a on the side close to the engine (left side in FIG. 4), and is brought into rolling contact as described above. Appropriate surface pressure is applied to each rolling contact portion (traction portion). Further, the base end portion (left end portion in FIG. 4) of the hollow rotary shaft 21 is spline-engaged with the inner disk 11. And this hollow rotating shaft 21 is inserted inside the outer disk 10b on the side far from the engine (the right side in FIG. 4) corresponding to the first disk described in the claims, and the inner disk 11 is inserted. The rotational force of can be taken out freely. Further, a sun gear for constituting the front stage unit 7 of the planetary gear type transmission 2 at a portion protruding from the outer surface of the outer disk 10b at the tip end portion (right end portion in FIG. 4) of the hollow rotary shaft 21. 22 is fixed.

  On the other hand, a carrier 23 is provided between the outer disk 10b and a portion protruding from the hollow rotary shaft 21 at the tip of the input rotary shaft 5 (the right end in FIGS. 4 and 5). The outer disk 10b and the input rotation shaft 5 rotate in synchronization with each other. Then, the front stage unit 7 of the planetary gear type transmission 2 and each of which is a double pinion type at circumferentially equidistant positions (generally 3 to 4 positions) on both sides in the axial direction of the carrier 23 and the aforementioned Planetary gears 24 to 26 for constituting the middle unit 8 are rotatably supported. Further, a ring gear 27 is rotatably supported around one half of the carrier 23 (the right half of FIG. 4). A second sun gear 28 fixed to the base end portion (left end portion in FIG. 4) of the transmission shaft 6 is disposed on the inner diameter side of the ring gear 27.

  A second carrier 29 for constituting the rear stage unit 9 is coupled and fixed to the base end portion (left end portion in FIG. 4) of the output shaft 4. And this 2nd carrier 29 and the said ring gearwheel 27 are couple | bonded via the low speed clutch 30 which comprises a clutch apparatus. Further, a third sun gear 31 is fixedly provided near the tip of the transmission shaft 6 (near the right end in FIG. 4). Further, a second ring gear 32 is disposed around the third sun gear 31, and a high speed clutch 33 constituting a clutch device is formed between the second ring gear 32 and a fixed portion such as the casing 13. Is provided. Further, a plurality of sets of planetary gears 34 and 35 disposed between the second ring gear 32 and the third sun gear 31 are rotatably supported by the second carrier 29.

  In the case of the continuously variable transmission configured as described above, the power transmitted from the input rotating shaft 5 to the integrated inner disk 11 via the pair of outer disks 10a and 10b and the power rollers 12 and 12 is the above described hollow. It is taken out through the rotating shaft 21. In the so-called low-speed mode in which the low-speed clutch 30 is connected and the high-speed clutch 33 is disconnected, the input rotary shaft 5 is changed by changing the gear ratio of the toroidal continuously variable transmission 1. The rotation speed of the output shaft 4 can be freely converted into forward rotation and reverse rotation with a so-called geared neutral stop state in between. On the other hand, in the so-called high speed mode in which the high speed clutch 33 is connected and the low speed clutch 30 is disconnected, the speed ratio of the toroidal-type continuously variable transmission 1 is not increased as the speed ratio is increased. The speed ratio of the step transmission as a whole also changes to the speed increasing side. 4 to 6 in this state, the toroidal continuously variable transmission 1 transmits part of the power transmitted from the input shaft 3 to the output shaft 4 via the input-side rotating shaft 5. Is in a so-called power split state. In this power split state, since the torque passing through the toroidal continuously variable transmission 1 can be reduced, the durability of the toroidal continuously variable transmission 1 is improved and the transmission efficiency of the continuously variable transmission as a whole is improved. I can plan.

  During the operation of the continuously variable transmission as described above, the outer disks 10a and 10b provided at positions sandwiching the inner disk 11 from both sides in the axial direction are synchronized with each other via the input rotating shaft 5 and the carrier 23. Rotate. Of these, the carrier 23 includes a support plate 36, a disk side connection plate 37 (FIGS. 6 and 7), a plurality of disk side coupling portions 38 and 38 (FIG. 7), and an anti-disk side connection plate 39 (FIG. 6, FIG. 7), a plurality of anti-disk-side coupling portions 40, 40 (FIG. 7), a plurality of first disk-side planetary shafts 41 each corresponding to the planetary axis recited in the claims, and a plurality of anti-disk-side coupling portions A disk-side planetary shaft 42 and a plurality of second disk-side planetary shafts 43 each corresponding to the planetary shaft described in the claims are provided. Of these, the support plate 36, the disk side coupling plate 37, the plurality of disk side coupling portions 38, 38, the anti-disk side coupling plate 39, and the plurality of anti-disk side coupling portions 40, 40 are made of carbon. As shown in detail in FIGS. 6 to 7, the whole is integrally formed by machining a metal material having sufficient strength and rigidity such as steel and bearing steel.

  A support tube portion 44 having a female spline portion on the inner peripheral surface is integrally provided at the center of the support plate 36. The support plate 36 and the support tube portion 44 are circular in shape with an L-shaped cross section. Annular. The disk-side connecting plate 37 is a ring-shaped, concentric with the support plate 36 and spaced axially, and is the first of the outer disks 10a and 10b. It is arranged on the side of the outer disk 10b far from the engine, and one side surface (the left surface in FIGS. 6 to 7) is opposed to the outer surface of the outer disk 10b. Each of the disk-side coupling portions 38, 38 is for coupling and fixing the support plate 36 and the disk-side coupling plate 37. Between the side surfaces of the plates 36, 37 facing each other, It is arranged intermittently with respect to the direction. Similarly to the disk side connection plate 37, the anti-disk side connection plate 39 is opposite to the outer disk 10b on the side farther from the engine, with the support plate 36 being concentric and spaced apart in the axial direction. Arranged on the side. The anti-disk side coupling portions 40 and 40 are for fixing and fixing the support plate 36 and the anti-disk side coupling plate 39, and are disposed intermittently with respect to the circumferential direction of the plates 36 and 39. ing.

  The first disk-side planetary shafts 41 are circumferentially disengaged from the disk-side coupling portions 38, 38 between the support plate 36 and the disk-side connecting plate 37 at both ends. It is supported and fixed in position. Further, each of the anti-disk side planetary shafts 42 is disengaged from each of the anti-disk side coupling portions 40, 40 in the circumferential direction between the support plate 36 and the anti-disk side coupling plate 39. It is supported and fixed at the specified position. Further, each of the second disk side planetary shafts 43 has both end portions between the disk side and anti-disk side coupling plates 37, 39, and the disk side and anti-disk side coupling portions 38, 40. Is supported and fixed at a position deviated in the circumferential direction. For this purpose, the end portions of the planetary shafts 41 to 43 are fitted and fixed at positions where the plates 36, 37 and 39 are partly removed from the coupling portions 38 and 40 in the circumferential direction. Support holes 45 and 45 (FIGS. 6 and 7) are provided. Further, notches 46 and 46 (FIG. 7) are formed in portions of the support plate 36 where the second disk side planetary shafts 43 are to be provided.

  The carrier 23 configured as described above is coupled to the input rotary shaft 5 by causing the support cylinder portion 44 to be spline-engaged with a portion near the tip of the intermediate portion of the input rotary shaft 5 and restrained by a loading nut 47. It is fixed. Further, in order to transmit rotation between the outer disk 10b far from the engine and the carrier 23, convex portions 48 formed at a plurality of positions on the outer surface of the outer disk 10b, and the disk side connecting plate 37. Are engaged with notches 49, 49 formed in the outer peripheral edge portion.

  During operation of the continuously variable transmission, the torque transmitted from the engine to the input side rotating shaft 5 is transmitted to the outer disk 10a on the side close to the engine via the ball spline 50, and also via the carrier 23. Thus, it is also transmitted to the outer disk 10b far from the engine. That is, the carrier 23 has a function of transmitting the torque of the engine to the outer disk 10b on the side far from the engine. Furthermore, the carrier 23 also has a function of transmitting the thrust (axial force) generated by the pressing device 20 to the outer disk 10b on the side far from the engine. That is, the thrust generated by the pressing device 20 in order to ensure the surface pressure of each rolling contact portion (traction portion) is supported by the input rotating shaft 5 and the carrier 23 fixed to the input rotating shaft 5. The outer disk 10b is joined via the plate 36, the disk side coupling portions 38 and 38, and the disk side connecting plate 37.

  Therefore, the carrier 23 has a role of transmitting a large torque and a large axial load during operation of the continuously variable transmission. Moreover, this torque changes frequently and greatly depending on the driving conditions of the automobile and various industrial machines equipped with the continuously variable transmission, and the axial load applied based on the thrust of the pressing device 20 is also accompanying this. It changes a lot. The axial load is transmitted between the outer disk 10b on the side far from the engine and the support plate 36 coupled and fixed to the input side rotating shaft 5 (the outer disk 10b and the support plate 36). One side becomes the input side and the other side becomes the output side). For this reason, a considerably large stress is generated in a part of the carrier 23 (for example, the disk side connecting plate 37). In particular, the axial load generated in association with ensuring the surface pressure of each rolling contact portion (traction portion) becomes considerably large. Note that such an axial load is proportional to the torque passing through the toroidal type continuously variable transmission 1 (torque transmitted by the toroidal type continuously variable transmission 1). In the case of a continuously variable transmission capable of realizing the geared neutral state, the speed is considerably increased in the state in the vicinity of the geared neutral state, that is, when the vehicle starts.

  A large torque and a large axial load as described above become a force for elastically deforming the carrier 23. However, if the elastic deformation of the carrier 23 is increased, the following inconvenience may occur. That is, when the carrier 23 is elastically deformed, for example, the outer disk 10b adjacent to the carrier 23 is also elastically deformed together with the disk-side connecting plate 37 of the carrier 23. Such elastic deformation of the outer disk 10b makes the contact state of the rolling contact portion between the side surface of the outer disk 10b and the peripheral surfaces of the power rollers 12 and 12 unstable (for example, the contact point shifts from an ideal position). ), Which may lead to unnecessary change in the transmission ratio and a decrease in transmission efficiency.

  When the carrier 23 is elastically deformed, the amount of axial displacement of the outer disk 10b increases along with the elastic deformation, and the carrier 23 and members existing around the carrier 23 are likely to interfere with each other. Become. In order to prevent such interference, for example, a clearance (gap, clearance) between the carrier 23 and a member adjacent to the carrier 23 needs to be increased, but if the clearance is increased in this way, Accordingly, there is a possibility that the entire apparatus is increased in size. In particular, the continuously variable transmission is installed in a limited space, and many members need to be incorporated within a limited range in the casing 13 of the continuously variable transmission. There is little space to get enough. For this reason, it is preferable that the elastic deformation of the carrier 23 as described above and the axial displacement of the outer disk 10b associated therewith are as small as possible.

  As the carrier 23 is elastically deformed, the first, second disk-side and counter-disk-side planetary shafts 41 to 43 supported by the carrier 23 are inclined (the center axis is deviated from the ideal position. There is also a possibility that the center axis of the axis 5 is not parallel. Such inclination of the planetary shafts 41 to 43 causes unnecessary loads to be applied to the meshing portions of the planetary gears 24 to 26 rotatably supported by the planetary shafts 41 to 43, thereby reducing transmission efficiency. In addition to this, there is a possibility that the durability of each of the planetary gears 24 to 26 is reduced or damaged. Furthermore, along with the elastic deformation of the carrier 23, one side surface of the disk-side connecting plate 37 of the carrier 23 and the outer surface of the outer disk 10b are likely to rub against each other, and there is a possibility that fretting wear occurs in the portion. . Such fretting wear is also undesirable because it leads to a decrease in durability.

In the case of the conventional structure shown in FIGS. 4 to 7 described above, one end of each of the first and second disk-side planetary shafts 41 and 43 provided on the disk-side connecting plate 37 (left end in FIG. 6). The other end portions (the right end portion in FIG. 6) of the planetary shafts 41 and 43 provided with the inner diameter D of the support holes 45 and 45 in the support plate 36 or the anti-disk side connection plate 39 are provided. It is made larger than the internal diameter d of the support holes 45 and 45 for supporting.
Further, in the case of another example of the conventional structure as shown in FIGS. 8 to 10, for example, the outer diameter of the planetary gear 26a (long in the axial direction) provided between the disk side connecting plate 37 and the non-disk side connecting plate 39. In the case of a structure in which the one end side and the other end side are different from each other with respect to the axial direction, it is the same as in the case of the conventional structure described above. That is, the inner diameter D of the support holes 45 and 45 for supporting one end (the left end in FIG. 8) of the first and second disk side planetary shafts 41 and 43 provided on the disk side connecting plate 37 is supported. The inner diameter d of the support holes 45 and 45 for supporting the other end portions (the right end portions in FIG. 8) of the planetary shafts 41 and 43 provided on the plate 36 or the non-disk side connecting plate 39 is made larger. . In the case of the structure shown in FIGS. 8 to 10, the planetary gear 26a (long in the axial direction) is provided between the disk-side connecting plate 37 and the support plate 36 (short in the axial direction). Positioned on the inner diameter side of the gear 24, one end (the left end in FIG. 8) of the planetary gear 26a meshes with the planetary gear 24 and the sun gear 22 (see FIGS. 4 and 6). A ring gear 27 (see FIGS. 4 and 6) is engaged with the planetary gear 24, and the other end portion (right end portion in FIG. 8) of the planetary gear 26a is connected to the second sun gear 28 (see FIGS. 4 and 6). ). Another planetary gear that meshes with the other end of the planetary gear 26a is not provided.

JP 2004-368877 A JP 2004-218769 A JP 2005-249181 A JP 2006-242314 A

  In view of the circumstances as described above, the present invention has been invented to realize a structure that can reduce the elastic deformation of the carrier, and can ensure the transmission efficiency, the durability, and the miniaturization.

The continuously variable transmission according to the present invention includes an input shaft, an output shaft, a toroidal continuously variable transmission, and a planetary gear, which are arranged concentrically with each other, like the previously known continuously variable transmissions. Type transmission.
The toroidal continuously variable transmission and the planetary gear type transmission constitute the first disk and the planetary gear type transmission of the first and second disks constituting the toroidal type continuously variable transmission. The carrier is adjacent to each other, and the first disk and the carrier are combined so as to rotate synchronously.

The carrier includes a support plate, a disk side connection plate, an anti-disk side connection plate, and a plurality of planetary shafts.
The support plate is supported and fixed to an input rotation shaft that is provided at the center of the toroidal-type continuously variable transmission and rotates together with the input shaft.
The disk side connecting plate is in the shape of a ring and is arranged on the first disk side in a state of being concentric with the support plate and spaced apart in the axial direction. It faces the side.
The anti-disk-side connecting plate has an annular shape, and is disposed on the side opposite to the first disk in a state of being concentric with the support plate and spaced apart in the axial direction.
Each planetary shaft (for example, the first and second disk-side planetary shafts) supports both end portions between the disk-side connecting plate and the support plate or the counter-disk-side connecting plate. .
And the planetary gear which comprises the said planetary gear type transmission is rotatably supported around each said planetary shaft.
Further, the disk side connecting plate and the first disk are combined so that torque can be transmitted.

In particular, in the continuously variable transmission according to the present invention, the inner diameter of a support hole (for example, a disk-side support hole) provided in the disk-side connecting plate for internally fitting and supporting each planetary shaft (one end thereof). Is smaller than the inner diameter of a support hole (for example, the anti-disk side support hole) provided in the support plate or the anti-disk side connecting plate for internally fitting and supporting each of these planetary shafts (the intermediate portion or the other end portion thereof). is doing.
When implementing such a continuously variable transmission according to the present invention, for example, as in the second aspect of the present invention, in the outer peripheral surface of each planetary shaft, it is fitted in the support hole of the disk side connecting plate. The part (one outer peripheral surface of the planetary shaft) to be made has a smaller diameter than the other parts (intermediate outer peripheral surface or other end outer peripheral surface of the planetary shaft).
Preferably, as in the invention described in claim 3, an oil supply passage is provided at the center of each planetary shaft, and an oil supply passage (for example, upstream) provided in the support plate or the non-disk side connection plate is provided in the oil supply passage. Oil (lubricating oil, traction oil) is supplied through the side oil supply passage), and no oil supply passage (for example, upstream oil supply passage) is provided in the disk side connecting plate.
Preferably, as in the invention described in claim 4, the support hole of the disk side connecting plate is a bottomed bag hole which does not open on the side surface on the first disk side.

According to the continuously variable transmission of the present invention configured as described above, the elastic deformation of the carrier can be reduced, and the transmission efficiency, the durability, and the size can be reduced.
That is, the inner diameter of the support hole of the disk-side connecting plate, which is combined with the first disk so as to be able to transmit torque, is reduced. For this reason, a large torque and an axial load are applied (the most elastic deformation among the carriers is easy), and the strength of the disk side connection plate is ensured. Can be reduced. As a result, the clearance (gap, margin) to prevent interference with this carrier can be reduced, the overall device can be reduced in size, and the inclination of each planetary shaft supported by this carrier can also be reduced. Ensuring durability, ensuring durability, preventing damage and the like. Further, fretting wear at the contact portion between the disk-side coupling plate and the first disk can be reduced, and durability can be ensured also from this surface. As in the third aspect of the present invention, if no oil supply passage is provided in the disk side connecting plate, further strength of the disk side connecting plate can be ensured, and elastic deformation of the carrier can be reduced. . Further, as in the invention described in claim 4, even if the support hole of the disk side connecting plate is a bottomed bag hole, further securing of the strength of the disk side connecting plate can be ensured. The elastic deformation can be reduced.

[First example of embodiment]
FIG. 1 shows a first example of an embodiment of the present invention corresponding to claims 1 and 2. The feature of this example is that the structure of the carrier 23a is devised so that the carrier 23a constituting the continuously variable transmission is less likely to be elastically deformed. Since the structure and operation of the other parts are the same as those of the conventional structure shown in FIGS. 4 to 10 described above, the illustration and description of the equivalent parts are omitted or simplified, and the following description will focus on the characteristic parts of this example. To do.

The carrier 23a includes a support plate 36a, a disk side connection plate 37a, and an anti-disk side connection plate 39a, each of which includes a plurality of first and second disk sides corresponding to the planetary shaft described in the claims. Planetary shafts 41a and 43a are provided. Of these, the first disk side planetary shafts 41a are supported and fixed at both ends by the support plate 36a and the disk side connection plate 37a, and are prevented from rotating by pins 57. The planetary shafts 43a on the second disk side support and fix both ends of the second disk side planetary shafts 43a on both the disk side and anti-disk side connection plates 37a and 39a, and prevent rotation by pins 57. In particular, in the case of the continuously variable transmission of this example, one end (the left end in FIG. 1) of each of the first and second disk-side planetary shafts 41a and 43a provided on the disk-side connecting plate 37a is connected to the inner side. The other end portions of the planetary shafts 41a and 43a (the right end portion in FIG. 1) provided with the inner diameter d51 of the disk-side support holes 51 and ₅₁ for fitting and supporting in the support plate 36a and the anti-disk-side connecting plate 39a ) is smaller than the inner diameter D ₅₂ of the counter-disk-side support hole 52, 52 for the inner fitting support.

According to the continuously variable transmission of this example configured as described above, it is possible to reduce the elastic deformation of the carrier 23a, and to ensure the transmission efficiency, the durability, and the miniaturization.
That, combined to allow the transmission of torque between the outer disk 10b (see FIGS. 4 and 6), has a smaller inner diameter d ₅₁ of the disk-side support hole 51 of the disk-side connecting plate 37a. For this reason, a large torque and an axial load are applied (the most easily elastically deformed among the carriers 23a), the strength of the disk side connecting plate 37a is secured, and the disk side connecting plate 37a, and thus the carrier 23a as a whole. The elastic deformation of can be reduced. As a result, the clearance (gap, margin) for preventing interference with the carrier 23a can be reduced, the overall apparatus can be reduced in size, and the first and second disk sides supported by the carrier 23a can be reduced. The inclination of the planetary shafts 41a and 43a can be reduced, and transmission efficiency, durability, damage prevention, and the like can be achieved. Further, fretting wear at the contact portion between the disk-side connecting plate 37a and the outer disk 10b can be reduced, and durability can be ensured also from this surface.

[Second Example of Embodiment]
FIG. 2 shows a second example of an embodiment of the present invention corresponding to claims 1 to 3. In the case of the structure of the first example of the above-described embodiment, the oil supply passages 53 and 53 are provided in the central portions of the first and second disk-side planetary shafts 41a and 43a, respectively. Then, through these oil supply passages 53 and 53, through the upstream oil supply passages 54 and 54 provided in the disk side connecting plate 37a, the radial needle bearings 55 and 55 that rotatably support the planetary gears 24 and 26a are oiled (lubricated). Oil, traction oil). For this purpose, the upstream side oil supply passages 54, 54 are provided in the disk side connecting plate 37a in the radial direction so as to correspond to the number of the first and second disk side planetary shafts 41a, 43a. . On the other hand, in the case of this example, the upstream side oil supply passages 54, 54 are provided in the anti-disk side connecting plate 39b, and the first, The oil is supplied to oil supply passages 53 and 53 provided in the second disk-side planetary shafts 41b and 43a. That is, in the case of this example, the oil supply passage (upstream oil supply passage 54) is not provided in the disk side connecting plate 37b. Accordingly, in the case of this example, the other end portion (the right end portion in FIG. 2) of each of the first disk side planetary shafts 41b is extended until it reaches the anti-disk side connecting plate 39b (first The other end of each of the disk-side planetary shafts 41b is fitted and supported in the anti-disk-side support hole 52a of the anti-disk-side connecting plate 39b), and through the upstream oil supply passage 54 of the anti-disk-side connecting plate 39b The oil is supplied to the oil supply passage 53 of each side planetary shaft 41b.

In the case of this example, since the upstream side oil supply passages 54, 54 are not provided in the disk side connecting plate 37b, the strength of the disk side connecting plate 37b can be secured, and the carrier 23b can be elastically deformed. It can be reduced more. In addition, in the case of this example, the upstream side oil supply passages 54 and 54 are provided in the anti-disk side connection plate 39b, to which the degree of torque and axial load applied is small compared to the disk side connection plate 37b. It is easy to increase the inner diameter of the side oil supply passages 54, 54. That is, when such upstream oil supply passages 54 and 54 are provided, for example, stress tends to concentrate on the opening edges of the respective upstream oil supply passages 54 and 54 (stress increases). In the case of the structure of the first example of the embodiment, it is difficult to increase the inner diameters of the upstream oil supply passages 54 and 54 in order to ensure the strength of the disk side connecting plate 37a. On the other hand, in the case of this example, as described above, each upstream-side oil supply passage 54, the anti-disk-side connection plate 39b, to which torque and an axial load are applied, is smaller than the disk-side connection plate 37b. Since 54 is provided, the inner diameters of these upstream oil supply passages 54 and 54 can be easily increased. In addition, since the inner diameter of the upstream oil supply passages 54, 54 can be increased in this way, the resistance to the oil flowing through each of the upstream oil supply passages 54, 54 can be reduced, and the planetary gears 24, 26a having severe use conditions, More oil can be supplied to the radial needle bearings 55 and 55 that rotatably support the planetary gears 24 and 26a.
Other configurations and operations are the same as those of the first example described above, and thus redundant description is omitted.

[Third example of embodiment]
FIG. 3 shows a second example of an embodiment of the present invention corresponding to claims 1 to 4. In the case of this example, the disk-side support holes 51 and 51 of the disk-side coupling plate 37c are formed as bottomed bag holes that do not open on the side surface on the outer disk 10b (see FIGS. 4 and 6) side (left side in FIG. 3). Yes. In the case of this example, since the disk side support holes 51 and 51 are not through holes, it is possible to secure further strength of the disk side connection plate 37c and to further reduce the elastic deformation of the carrier 23c.
In the case of the illustrated example, the downstream end opening of the oil supply passages 53, 53 that opens to one end face (the left end face in FIG. 3) of the first and second disk-side planetary shafts 41b, 43a is connected to the plug 56, 56, respectively. However, in the case of this example, since the disk-side support holes 51, 51 are bottomed bag holes, the plugs 56, 56 can be omitted. In this case, the cost can be reduced by omitting these plugs 56 and 56.
Other configurations and operations are the same as those of the first example and the second example described above, and therefore, redundant description is omitted.

The structure of the continuously variable transmission that is an object of the present invention is not particularly limited as long as the condition described in claim 1 of the claims is satisfied. However, as in the case of the continuously variable transmission shown in FIGS. 4 to 7 described above, the present invention can be applied if the geared neutral state can be realized in the low speed mode and the power split state can be realized in the high speed mode. The technical significance of In other words, in the geared neutral state, the torque passing through the toroidal type continuously variable transmission becomes very large, and the thrust generated by the pressing device to prevent gross slip, which is excessive slippage at the traction section, also increases. The thrust load applied to is also increased. For this reason, according to the structure of the present invention, a remarkable effect can be obtained by securing the strength of the carrier and keeping the elastic deformation of the carrier low.
Moreover, although the example of illustration demonstrated about the case where a half toroidal type thing was used as a toroidal type continuously variable transmission which comprises the continuously variable transmission used as the object of this invention, this invention is a half toroidal type. The present invention is not limited to this, and can also be implemented with a full toroidal toroidal continuously variable transmission.

Sectional drawing similar to FIG. 8 which shows the 1st example of embodiment of this invention. Sectional drawing similar to FIG. 1, showing the second example. Sectional drawing similar to FIG. 1 showing the third example. Sectional drawing which shows the 1st example of a conventional structure. AA sectional drawing of FIG. Sectional drawing equivalent to the B section of FIG. The perspective view which takes out and shows a carrier. Sectional drawing which shows the other example of the prior art structure seen from the same direction as FIG. The perspective view seen from the left side of FIG. The perspective view seen from the right side of FIG.

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 Outer disk 11 Inner disk 12 Power roller 13 Casing 14 Prop DESCRIPTION OF SYMBOLS 15 Rolling bearing 16 Support plate 17 Trunnion 18 Pivot 19 Support shaft 20 Pressing device 21 Hollow rotary shaft 22 Sun gear 23, 23a, 23b, 23c Carrier 24 Planetary gear 25 Planetary gear 26, 26a Planetary gear 27 Ring gear 28 Second sun gear 29 Second carrier 30 Low speed clutch 31 Third sun gear 32 Second ring gear 33 High speed clutch 34 Planetary gear 35 Planetary gear 36, 36a Support plate 37, 37a, 37b, 37c Disc side connecting plate 38 Disc side coupling portion 39 , 39a, 39b Anti-disk side connecting plate 40 Anti-disk side coupling portion 41, 41a, 41b First disk-side planetary shaft 42 Anti-disk-side planetary shaft 43, 43a Second disk-side planetary shaft 44 Support cylinder portion 45 Support hole 46 Notch 47 Loading nut 48 convex portion 49 notch 50 ball spline 51 disk side support hole 52, 52a anti-disk side support hole 53 oil supply passage 54 upstream oil supply passage 55 radial needle bearing 56 plug 57 pin

Claims (4)

  An input shaft, an output shaft, a toroidal type continuously variable transmission, and a planetary gear type transmission, which are arranged concentrically with each other, are provided with a toroidal type continuously variable transmission and a planetary gear type transmission. The first disk of the first and second disks constituting the continuously variable transmission is adjacent to the carrier constituting the planetary gear transmission, and the first disk and the carrier rotate in synchronization. The carrier is provided at the center of the toroidal-type continuously variable transmission and rotates together with the input shaft. The support plate is supported and fixed to the input rotation shaft, and is concentric with the support plate. And a disc-side coupling plate that is in the shape of a ring and is disposed on the first disc side with an axial interval therebetween, with one side faced to the outer side surface of the first disc, and the support Concentric with the board An anti-disk-side connecting plate that is in the shape of a ring and is disposed on the side opposite to the first disk with a space in the direction, and the disk-side connecting plate and the support plate or the anti-disk-side connecting plate A plurality of planetary shafts supported at both ends thereof, and the planetary gears constituting the planetary gear type transmission are rotatably supported around the planetary shafts. In the continuously variable transmission that combines the disk-side connecting plate and the first disk so that torque can be transmitted, the planetary shafts provided on the disk-side connecting plate are internally fitted. A continuously variable transmission characterized in that an inner diameter of a support hole for supporting is made smaller than an inner diameter of a support hole provided in the support plate or the anti-disk side connecting plate for supporting and fitting these planetary shafts. apparatus.   2. The continuously variable transmission according to claim 1, wherein a portion of the outer peripheral surface of each planetary shaft that is fitted into the support hole of the disk side coupling plate has a smaller diameter than other portions.   An oil supply passage is provided at the center of each planetary shaft, and oil is supplied to the oil supply passage through an oil supply passage provided on the support plate or the anti-disk side connection plate, and no oil supply passage is provided on the disk side connection plate. The continuously variable transmission according to any one of claims 1 and 2.   The continuously variable transmission according to any one of claims 1 to 3, wherein the support hole of the disk side connecting plate is a bottomed bag hole that does not open on a side surface on the first disk side.

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