JP2006009994A - Continuously variable transmission - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To realize a structure capable of preventing fretting wear based on the elastic deformation of an input side disk 8a and sufficiently securing the amount of a lubricating oil fed to a radial needle bearing 31c rotatably pivoting a planetary gear 30. <P>SOLUTION: The lubricating oil fed from the lubricating oil flow passage 50 of an input shaft into a lubricating oil flow passage 53 in a first carrier 21 is fed to the radial needle bearing 31c through a recessed part 58 formed in the axial end face of the first carrier 21 and a second lubricating oil flow passage 60 formed in a third planetary shaft 27. Also, a copper or copper-based alloy thrust plate 63 is held between the first carrier 21 and the input side disk 8a. <P>COPYRIGHT: (C)2006,JPO&NCIPI

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.

  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 Patent Documents 1 to 8 and the like, it is conventionally known that a continuously variable transmission device is configured by combining a toroidal type continuously variable transmission and a planetary gear type transmission. 4-6 has shown the continuously variable transmission described in patent document 4 among these. This continuously variable transmission is a combination of a toroidal-type continuously variable transmission 1 and first to third planetary gear transmissions 2 to 4, and is supported concentrically and relatively rotatably. Further, it has an input shaft 5, a transmission shaft 6, and an output shaft 7. 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 includes a pair of input-side disks 8 a and 8 b, an integrated output-side disk 9, and a plurality of power rollers 10 and 10. Of these, the two input side disks 8a and 8b have two axially spaced apart portions of the input shaft 5 in a state in which one axial side surfaces, each of which is a toroidal curved surface having an arcuate cross section, are opposed to each other. The position is concentric with each other and supports the rotation in synchronism with the input shaft 5 as free. 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 respectively supported by both ends of support columns 17 and 17 supported and fixed in the casing 14 via a connecting plate 15 and an actuator body 16.

  Further, the output side disk 9 is rotatably supported by a pair of thrust angular ball bearings 18 and 18 between the intermediate portions of the respective pillars 17 and 17 formed in an annular shape. Further, the base end portion (the left end portion in FIG. 4) of the hollow rotary shaft 19 is spline engaged with the output side disk 9. The hollow rotary shaft 19 is inserted inside the input side disk 8a on the side far from the engine (right side in FIG. 4) so that power transmitted to the output side disk 9 can be taken out. Further, a first sun gear for constituting the first planetary gear type transmission 2 at a portion protruding from the outer surface of the input side disk 8a at the tip end portion (the right end portion in FIG. 4) of the hollow rotary shaft 19. The gear 20 is fixed.

  On the other hand, between the portion protruding from the hollow rotary shaft 19 at the tip end portion (the right end portion in FIG. 4) of the input shaft 5 inserted inside the hollow rotary shaft 19 and the input side disk 8a, there is a claim. The input side disk 8a and the input shaft 5 rotate in synchronization with each other by providing a first carrier 21 corresponding to the carrier described in the above-mentioned range. As shown in detail in FIGS. 6 to 7, the first carrier 21 includes an intermediate support plate 22 having an L-shaped cross section and an annular shape as a whole, and first and second connecting plates each formed in an annular shape. A plurality of (for example, three) first and second planetary shafts 25 and 26 are provided between the first and second connecting plates 23 and 24, respectively. The third planetary shafts 27 (for example, three) are spanned over each other. Further, the planetary gears 28 to 30 are rotatably supported around the planetary shafts 25 to 27 via radial needle bearings 31a, 31b and 31c, respectively. Then, the planetary gear 30 on the outer diameter side and the planetary gears 28 and 29 on the inner diameter side are meshed with each other, and the planetary gears 28 and 29 on the inner diameter side are connected to the tip of the hollow rotary shaft 19 (see FIGS. 4 and 6). The planetary gear 30 on the outer diameter side is placed around the first carrier 21 on the first sun gear 20 fixed on the right end) or the second sun gear 32 fixed on the base end of the transmission shaft 6. The first ring gears 33 are rotatably meshed with each other.

  A cylindrical portion 34 provided at the center of the intermediate support plate 22 is spline-engaged with a portion near the tip of the intermediate portion of the input shaft 5 and is held down by a loading nut 35. As shown in FIG. 7, the annular ring portion 36 of the intermediate support plate 22 and the first and second connecting plates 23, 24 are positioned away from the planetary gears 28-30 in the circumferential direction. Are connected to each other by column portions 37, 37. In the case of the illustrated example, the intermediate support plate 22 and the first and second connecting plates 23 and 24 constituting the first carrier 21 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 1st carrier 21 are ensured. Further, in order to transmit rotation between the input side disk 8a and the first carrier 21, convex portions 38 formed at a plurality of locations on the outer surface of the input side disk 8a, and the first connecting plate 23 A notch 39 formed at the outer peripheral edge is engaged.

  On the other hand, a second carrier 40 for constituting the third planetary gear type transmission 4 is coupled and fixed to the base end portion (left end portion in FIG. 4) of the output shaft 7. The second carrier 40 and the first ring gear 33 are coupled via a low speed clutch 41. Further, a third sun gear 42 is fixed to a portion near the tip of the transmission shaft 6 (near the right end in FIG. 4). A second ring gear 43 is disposed around the third sun gear 42, and a high speed clutch 44 is provided between the second ring gear 43 and a fixed portion of the casing 14, etc. Further, a plurality of planetary gears 45 and 46 disposed between the second ring gear 43 and the third sun gear 42 are rotatably supported by the second carrier 40. These planetary gears 45 and 46 mesh with each other, and the planetary gear 45 provided on the inner side with respect to the radial direction of the second carrier 40 is provided on the third sun gear 42, and the planetary gear 46 provided on the outer side is provided on the first side. The two ring gears 43 mesh with each other.

  In the case of the continuously variable transmission configured as described above, it is transmitted from the drive shaft 47 to the input shaft 5 and further from the input shaft 5 via the input disks 8a and 8b and the power rollers 10 and 10. The power transmitted to the integrated output disk 9 is taken out through the hollow rotary shaft 19. In the low speed mode in which the low speed clutch 41 is connected and the high speed clutch 44 is disconnected, the rotational speed of the input shaft 5 is kept constant by changing the gear ratio of the toroidal continuously variable transmission 1. In this state, the rotational speed of the output shaft 7 can be freely converted into forward rotation and reverse rotation with the stop state interposed therebetween. That is, in this state, the differential component between the first carrier 21 that rotates in the forward direction together with the input shaft 5 and the first sun gear 20 that rotates in the reverse direction together with the hollow rotation shaft 19 is converted into the first ring. The gear 33 is transmitted to the output shaft 7 through the low speed clutch 41 and the second carrier 40. In this state, the output shaft 7 is stopped by setting the gear ratio of the toroidal continuously variable transmission 1 to a predetermined value, and the speed ratio of the toroidal continuously variable transmission 1 is increased from the predetermined value. By changing to the side, the output shaft 7 is rotated in the direction in which the vehicle moves backward. On the other hand, the output shaft 7 is rotated in the direction in which the vehicle moves forward by changing the gear ratio of the toroidal type continuously variable transmission 1 from the predetermined value to the deceleration side.

  Further, in the high speed mode in which the low speed clutch 41 is disconnected and the high speed clutch 44 is connected, the output shaft 7 is rotated in the direction in which the vehicle moves forward. That is, in this state, the first carrier 21 that rotates in the forward direction together with the input shaft 5 and the first sun gear 20 that rotates in the reverse direction together with the hollow rotation shaft 19 rotate according to the differential component. The rotation of the planetary gear 28 of the first planetary gear type transmission 2 is transmitted to the planetary gear 29 of the second planetary gear type transmission 3 via the planetary gear 30 on the outer diameter side, and the second planetary gear type transmission 3 The transmission shaft 6 is rotated via the sun gear 32. The third sun gear 42 provided at the tip of the transmission shaft 6, the second ring gear 43 and the planetary gears 45, 46 constituting the third planetary gear type transmission 4 together with the third sun gear 42. Based on the meshing, the second carrier 40 and the output shaft 7 coupled to the second carrier 40 are rotated in the forward direction. 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 operation of the continuously variable transmission as described above, the inner surfaces of the input side disks 8a and 8b and the axially opposite side surfaces of the output side disk 9 and the power rollers 10 constituting the toroidal type continuously variable transmission 1 are provided. It is necessary to apply an appropriate surface pressure to the rolling contact portion (traction portion) with 10 peripheral surfaces. Therefore, in the case of the toroidal type continuously variable transmission 1 constituting the continuously variable transmission shown in FIGS. 4 to 5, the end of the input shaft 5 on the drive shaft 47 side and the periphery of the end A pressing device 48 is provided between the disk 8b and the input side disk 8b. In the case of the structure shown in FIG. 4, the pressing device 48 is a double piston type provided with a pair of hydraulic chambers 49a and 49b, each of which can be expanded and contracted in the axial direction. In the case of such a structure equipped with a hydraulic pressure device 48, the surface pressure applied to each traction portion is always adjusted to an appropriate value by controlling the pressure oil fed into the hydraulic chambers 49a and 49b. To do.

  Further, during the operation of the continuously variable transmission, the planetary gears 28 to 30, 45 and 46 constituting the first to third planetary gear type transmissions 2 to 4 rotate at a high speed. Therefore, it is necessary to supply a sufficient amount of lubricating oil to the radial needle bearings 31a, 31b, 31c that rotatably support the planetary gears 28-30 around the planetary shafts 25-27 ( The same applies to the radial needle bearing that rotatably supports the planetary gears 45 and 46). For this reason, in the illustrated example, the lubricating oil discharged radially outward from the base lubricating oil flow path 50 provided at the center of the input shaft 5 is, for example, an oil supply passage 51a formed in each of the connecting plates 23 and 24. , 51b, 51c, and are introduced into the second oil supply passages 52a, 52b, 52c provided at the center of the planetary shafts 25-27. Lubricating oil introduced into each of these second oil supply passages 52a, 52b, 52c is discharged from a nozzle hole provided in an intermediate portion of each of the planetary shafts 25-27, and each of the radial needle bearings 31a, 31b, 31c is discharged. Lubricate. In addition, as shown in FIG. 8, the lubricating oil supply to each radial needle bearing 31a, 31b which rotatably supports the planetary gears 28, 29 on the inner diameter side is an oil supply provided on the second connecting plate 24 side. A structure that is performed only from the side of the passage 51b is also considered.

  During the operation of the conventionally known continuously variable transmission as described above, the thrust generated by the pressing device 48 to ensure the surface pressure of each traction portion is applied to the input shaft 5 and the input shaft 5. Via the intermediate support plate 22 and the first connecting plate 23 constituting the fixed first carrier 21, the first carrier 21 is added to the input side disk 8 a provided adjacent to the first carrier 21. In other words, at the contact portion between the outer side surface of the input side disk 8a (the right side surface in FIGS. 4 and 6) and one side surface of the first connecting plate 23 (the left side surface in FIGS. 4 and 6), A force based on the generated thrust is applied.

  On the other hand, the input side disk 8a is formed on the outside of the input side disk 8a as shown in an exaggerated manner in FIG. 9 based on the force received from the power rollers 10 and 10 based on the thrust generated by the pressing device 48. The portion near the diameter is elastically deformed in a direction (axial direction) approaching one side surface of the first connecting plate 23. That is, the force applied to the input side disk 8a based on the thrust during operation is about 49 KN (5 Tf) at the maximum during operation of the toroidal continuously variable transmission 1. The amount of elastic deformation in the axial direction of the input side disk 8a based on such a large force is a comma number of mm (a few tenths of a millimeter), which is a nonnegligible amount. Then, when the input side disk 8a is elastically deformed in the axial direction in this way, the outer surface outer diameter portion of the input side disk 8a and one side surface of the first connecting plate 23 are intermittently repeatedly contacted. There is a possibility that fretting wear will occur at these parts. In particular, the circumferential position at which the input side disk 8a is elastically deformed always changes as the portions pressed by the power rollers 10 and 10 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 first carrier 21 to shift in the axial direction from a predetermined position, or may be a starting point of damage such as peeling. Further, the generated wear powder contaminates the lubricating oil (traction oil), which may cause the lubrication state of each part to be poor.

  Further, in the case of the conventionally known continuously variable transmission as described above, there is a possibility that sufficient lubricating oil to be fed to the radial needle bearings 31a, 31b, 31c cannot be secured. The reason for this is that the lubricating oil discharged from the base lubricating oil flow path 50 to the outer diameter side of the input shaft 5 is fed to the oil supply passages 51a, 51b, 51c formed in the connecting plates 23, 24. This is because the centrifugal force accompanying the rotation of the shaft 5 and the first and second sun gears 20 and 32 is used. That is, the lubricating oil is caused to flow by the centrifugal force generated by the rotation of the members 5, 20, and 32, and the lubricating oil passages formed in the members 5, 20, and 32 are radiated outwardly. It is made to send to 51b and 51c. In the case of such an oil supply structure, when the lubricating oil is transferred between the members adjacent in the radial direction, the amount of the lubricating oil scattered around increases, and the oil supply passages 51a, 51b, 51c are correspondingly increased. Thus, the amount of lubricating oil fed into the radial needle bearings 31a, 31b, 31c is reduced.

JP-A-6-174033 JP 2000-220719 A JP 2002-139124 A JP 2004-84712 A US Pat. No. 5,607,372 US Pat. No. 6,059,658 US Pat. No. 6,099,431 US Pat. No. 6,358,178

In view of the circumstances as described above, the present invention was first invented to prevent fretting wear based on the elastic deformation in the axial direction of the input side disk.
Second, if necessary, a structure that can secure a sufficient amount of lubricating oil to be fed to the radial needle bearing that rotatably supports the planetary gear of the planetary gear type transmission is realized, so that it has sufficient durability. It is also possible to realize a step transmission.

A continuously variable transmission according to the present invention includes an input shaft, an output shaft, a toroidal continuously variable transmission, and a planetary gear transmission, which are concentrically arranged.
The toroidal type continuously variable transmission and the planetary gear type transmission include an input side disk constituting the toroidal type continuously variable transmission and a carrier constituting the planetary gear type transmission, and these input side disks. And the carrier are rotated in a synchronized manner. The carrier is disposed with a support plate supported and fixed to the input shaft, concentric with the support plate and spaced apart in the axial direction, with the side surface facing the outer surface of the input side disk. In addition, a connecting plate having an annular shape and a plurality of planetary shafts supported at both ends by the connecting plate and the support plate are provided.
And the planetary gear which comprises the said planetary gear type transmission is rotatably supported around each said planetary shaft.
In particular, in the continuously variable transmission according to the present invention, a lubricating oil flow path is provided inside the carrier, and a downstream end of the lubricating oil flow path is opened on one side surface of the connecting plate. Lubricating oil is supplied to a portion between the side surface and the outer surface of the input side disk.

  According to the continuously variable transmission of the present invention configured as described above, fretting wear due to elastic deformation in the axial direction of the input side disk can be prevented. That is, in the continuously variable transmission according to the present invention, a lubricating oil film is formed between one side surface of the connecting plate and the outer side surface of the input side disk. For this reason, even when these both side surfaces are rubbed with each other due to elastic deformation of the input side disk, it is possible to prevent the occurrence of significant fretting wear on these both side surfaces.

Preferably, when carrying out the present invention, as described in claim 2, a concave portion that is long in the circumferential direction of the connecting plate is formed on one side surface of the connecting plate, and the downstream end of the lubricating oil passage is connected to the concave portion. Open in a part of.
With this configuration, a lubricating oil film can be formed in a wide range between one side of the connecting plate and the outer side of the input side disk, and the effect of preventing fretting wear on both sides is better. become.

In carrying out the invention described in claim 2 as described above, more preferably, as described in claim 3, a thrust plate sandwiched between the outer side surface of the input side disk and one side surface of the connecting plate. (Sliding plate) covers the opening of the recess formed on one side surface of the connecting plate. Then, the lubricating oil discharged from the lubricating oil flow path into the recess is oozed out between the outer side surface of the thrust plate and one side surface of the connecting plate to lubricate the contact portion between these both sides.
In this case, preferably, at least the outer surface of the thrust plate is made of a material having wear resistance.
For example, as described in claim 5, when the input side disk and the connecting plate are made of an iron-based alloy, the thrust plate is made of copper or a copper-based alloy.
With this configuration, it is possible to prevent fretting wear on both surfaces more effectively by preventing the outer surface of the input side disk from directly rubbing against one side surface of the connecting plate.
Further, when carrying out the invention described in claims 3 to 5 as described above, as described in claim 6, a large number of minute recesses are formed on the outer surface of the thrust plate.
If comprised in this way, it will become easy to form a favorable oil film between the outer side surface of this thrust plate, and the one side surface of the said connection plate, and lubrication of the contact part of these both surfaces can be achieved more effectively.

Further, when carrying out the invention described in claims 2 to 6 as described above, preferably, as described in claim 7, each planetary gear is rotatable around each planetary shaft by a radial needle bearing. To support. In addition, the lubricating oil flow path is provided inside a pillar portion provided between the planetary shafts adjacent in the circumferential direction in the carrier, so that a base lubricating oil flow provided inside the input shaft is provided. Lubricating oil can be fed freely from the road. Further, an upstream end of a second lubricating oil passage provided inside each of the planetary shafts and having both end portions opened to an axial end surface of each of the planetary shafts and an intermediate outer peripheral surface of each of the planetary shafts. The opening is communicated with a recess formed on one side of the connecting plate. Then, the remaining lubricating oil that has been discharged from the lubricating oil flow path into the recess and did not ooze between the outer side surface of the thrust plate and one side surface of the connecting plate is disposed downstream of the second lubricating oil flow path. The radial needle bearings are lubricated by discharging from the end openings.
If comprised in this way, the quantity of the lubricating oil sent to each said radial needle bearing is fully ensured, and the durability of a continuously variable transmission can fully be ensured.

FIGS. 1-2 has shown Example 1 of this invention corresponding to Claims 1-5, 7-10. The features of this embodiment are the following two points (1) and (2) (see FIGS. 4, 6, and 8 for some symbols).
(1) The outer side surface (right side surface in FIG. 1) of the input side disk 8a adjacent to the first planetary gear type transmission 2 and the first carrier 21 that is incorporated in the first planetary gear type transmission 2 By devising the structure of the engaging portion with one side surface (left side surface in FIG. 1) of one connecting plate 23, fretting wear between the outer side surface of these input side disks 8a and one side surface of the first connecting plate 23 is prevented. To do.
(2) By devising a structure for feeding lubricating oil to the radial needle bearings 31a to 31c that rotatably support the planetary gears 28 to 30 around the planetary shafts 25 to 27, each of these radial gears is devised. A sufficient amount of lubricating oil is supplied to the needle bearings 31a to 31c.
Since the structure and operation of the parts other than (1) and (2) are the same as those of the conventional structure shown in FIGS. 4 to 8 described above, the illustration and explanation of the equivalent parts are omitted or simplified. The description will focus on the features of the example.

  In the case of the present embodiment, a plurality of lubricating oil flow paths 53 and 53 are provided inside the first carrier 21. Each of these lubricating oil flow paths 53, 53 is formed in an L shape by communicating the downstream end of the radial portion 54 and the upstream end of the axial portion 55. Of these, the radial portion 54 extends from the intermediate support plate 22 constituting the first carrier 21 to the radial intermediate portion of the column portion 37, and is formed in the radial direction of the first carrier 21. (The lower end in FIG. 1) is opened on the inner peripheral surface of the cylindrical portion 34 provided on the inner peripheral edge of the first carrier 21. On the other hand, the axial portion 55 extends from the intermediate portion in the axial direction of the column portion 37 to one side surface of the first connecting plate 23 and is formed in the axial direction of the first carrier 21, and its downstream end. (Left end in FIG. 1) is opened on one side surface (left side surface in FIG. 1) of the first connecting plate 23.

  The cylindrical portion 34 is spline-engaged with a portion near the tip of the intermediate portion of the input shaft 5 (near the right end in FIG. 1) and further held down by the loading nut 35, and the upstream end of the radial portion 54 is The base lubricating oil flow path 50 provided at the center of the shaft 5 communicates with an oil passage hole 56 formed in the input shaft 5. During operation of the continuously variable transmission, the lubricating oil discharged from the oil pump provided inside the partition wall 57 (see FIG. 4) provided at the front end of the casing 14 and fed into the base lubricating oil flow path 50 is It is fed into each of the lubricating oil flow paths 53 described above.

  On the other hand, concave portions 58 and 58 that are long in the circumferential direction of the first connecting plate 23 are formed on a portion of one side of the first connecting plate 23 that is aligned with the downstream end opening of each of the lubricating oil passages 53 and 53. is doing. The downstream end openings of the lubricating oil flow paths 53 and 53 are in a state of opening at the bottom surfaces of the intermediate portions of the concave portions 58 and 58. In addition, both ends in the circumferential direction of the concave portions 58 and 58 have circular support holes 59a formed in the first connecting plate 23 in order to support one end portions of the first and third planetary shafts 25 and 27, respectively. It opens to the inner peripheral surface of 59b. Therefore, the lubricating oil that has flowed into the recesses 58 and 58 from the lubricating oil flow paths 53 and 53 is sent into the support holes 59a and 59b.

Of these support holes 59a and 59b, one end (the left end in FIG. 1) of the third planetary shaft 27 is fitted and fixed to one of the support holes 59b and 59b (downward in FIG. 1) by an interference fit. Has been. In this state, one end surface (the left end surface in FIG. 1) of the third planetary shaft 27 exists at a position slightly recessed from one side surface of the first connecting plate 23 (to the right in FIG. 1). A second lubricating oil passage 60 is provided on the inner side of the third planetary shaft 27 so that the one end surface of the third planetary shaft 27 communicates with the outer peripheral surface of the intermediate portion in the axial direction. The second lubricating oil passage 60 includes a central hole 61 that extends from one end surface of the third planetary shaft 27 to the axially intermediate portion, and a radial hole that extends from the central hole 61 to the outer peripheral surface of the axially intermediate portion. 62, 62.
With this configuration, the lubricating oil that has flowed into the recesses 58 and 58 from the lubricating oil flow paths 53 and 53 passes through the support holes 59b and 59b and the second lubricating oil flow path 60, and the third planetary planets. It can be fed to a radial needle bearing 31 c provided between the outer peripheral surface of the shaft 27 and the inner peripheral surface of the planetary gear 30.

  Even in the case of the radial needle bearings 31a and 31b for rotatably supporting the planetary gears 28 and 29 around the first and second planetary shafts 25 and 26, the above-described lubricating oil flow paths 53 and 53 are used. Lubricating oil that has flowed into the recesses 58 and 58 can be fed through the second lubricating oil passages provided in the first and second planetary shafts 25 and 26. In order to provide a second lubricating oil flow path inside the first and second planetary shafts 25 and 26, both axial end surfaces are provided at the center of the first planetary shaft 25 provided on the first connecting plate 23 side. A through hole is formed to communicate with each other (as formed in the central portion of the second planetary shaft 26 in the conventional structure shown in FIG. 8). On the other hand, the central portion of the second planetary shaft 26 provided on the second connecting plate 24 side is opened only on the end face on the side facing the first planetary shaft 25 (the conventional structure shown in FIG. A central hole is formed (as formed at the center of the planetary axis 25). Then, the upstream end opening of the center hole and the downstream end opening of the through hole are communicated with each other at the inner portion of the support hole formed in the intermediate support plate 22 (similar to the conventional structure shown in FIG. 8). Further, the central hole and the through hole are communicated with the outer peripheral surfaces of the first and second planetary shafts 25 and 26 through a radial hole. The lubricating oil flowing into the recesses 58, 58 from the lubricating oil passages 53, 53 passes through the support holes 59a, 59a, the second lubricating oil passage (not shown), and the first, first, It can be fed freely into radial needle bearings 31 a and 31 b provided between the outer peripheral surfaces of the two planetary shafts 25 and 26 and the inner peripheral surfaces of the planetary gears 28 and 29.

  In the case of the present embodiment, as described above, the lubricating oil can be surely fed into the radial needle bearings 31a, 31b, 31c, but a part of this lubricating oil is used. Thus, fretting wear between the outer side surface of the input side disk 8a and one side surface of the first connecting plate 23 is prevented. Therefore, in this embodiment, a thrust plate (sliding plate) 63 is attached to the outer surface of the input side disk 8a. The thrust plate 63 is preferably made of a material having wear resistance in order to prevent the thrust plate 63 from being worn due to friction with the mating surface. In the present embodiment, the thrust plate 63 is self-lubricating when it is rubbed against the input side disk 8a and the first connecting plate 23, both of which are made of a ferrous alloy such as bearing steel and carbon steel. It is made of copper or a copper-based alloy. Such a thrust plate 63 is fixed to the outer surface portion of the input side disk 8a by bonding, screwing, crimping or the like so as not to be displaced with respect to the input side disk 8a.

  On the other hand, the outer side surface (the right side surface in FIG. 1) of the thrust plate 63 is simply brought into contact with one side surface of the first connecting plate 23. In this state, the thrust plate 63 covers the openings of the recesses 58 and 58 formed on one side surface of the first connecting plate 23. Accordingly, the lubricating oil discharged into the recesses 58, 58 from the downstream end openings of the lubricating oil flow paths 53, 53 provided in the first carrier 21 is separated from the outer surface of the thrust plate 63 and the Except for a part that oozes into a minute gap between the contact surfaces of the first connecting plate 23 and one side surface, it is fed to the radial needle bearings 31a, 31b, 31c through the second lubricating oil passages 60. The radial needle bearings 31a, 31b, 31c are sufficiently lubricated.

  On the other hand, a part of the lubricating oil flowing through the recesses 58 and 58 from the lubricating oil flow paths 53 and 53 toward the second lubricating oil flow path 60 is formed on the outer surface of the thrust plate 63. The first connecting plate 23 oozes out into a minute gap between the contact surfaces with one side surface, and lubricates the contact portions between these both surfaces. In particular, in the case of the present embodiment, each of the concave portions 58, 58 is formed on one side surface of the first connecting plate 23 in the circumferential direction of the first connecting plate 23. A good (strong) oil film can be formed over a range (almost the entire surface). As a result, as described above, as the toroidal type continuously variable transmission 1 is operated, the input side disk 8a is elastically deformed as shown exaggeratedly in FIG. 9, and the outer surface of the thrust plate 63 and the first surface are Even if the contact surfaces with one side surface of the connecting plate 23 are slightly displaced, it is possible to effectively prevent fretting wear from occurring on both surfaces.

  Since the ratio of the lubricating oil flowing through the recesses 58 and 58 to the minute gap is very small, the amount of lubricating oil fed into the radial needle bearings 31a, 31b and 31c can be sufficiently secured. Therefore, in the case of the present embodiment, fretting wear of the engaging portion between the outer side surface of the input side disk 8a and one side surface of the first connecting plate 23 is prevented, and the radial needle bearings 31a, 31b, The durability of 31c can be sufficiently ensured.

  In the case of the above-described embodiment, the thrust plate 63 is allowed to ooze out part of the lubricating oil between the contact surfaces of the outer surface of the thrust plate 63 and one side surface of the first connecting plate 23. Is employed on the outer surface side of the input side disk 8a in a state where displacement with respect to the input side disk 8a is prevented. However, when the thrust plate 63 is made of a material having self-lubricating properties such as copper or a copper-based alloy, the lubricating oil is not necessarily allowed to ooze out in the frictional portion between the thrust plate 63 and the mating surface. There is no need. Accordingly, contrary to the above-described embodiment, the thrust plate 63 is attached and fixed to the first connecting plate 23 side by screwing or the like, and the inner surface of the thrust plate 63 and the input side disk 8a are fixed. It is also possible to rub against the outer surface of each of the above (claims 9, 10). In this case, the friction surface between the inner side surface of the thrust plate 63 and the outer side surface of the input side disk 8 a is between the inner peripheral surface of the input side disk 8 a and the outer peripheral surface of the input shaft 5. After the provided radial needle bearing 64 is lubricated, the lubricating oil sent radially outward by centrifugal force enters and forms an oil film.

FIG. 3 shows a second embodiment of the present invention corresponding to claim 6. In the case of the present embodiment, a large number of minute recesses 65, 65 are formed on the outer surface (or inner surface) of the thrust plate 63a that is slightly displaced relative to the mating surface.
In the case of the present embodiment, by adopting such a configuration, between the outer side surface of the thrust plate 63a and one side surface of the first connecting plate 23 (see FIG. 1) {or the inner side of the thrust plate 63a. A good oil film is easily formed between the side surface and the outer side surface of the input side disk 8a (see FIG. 1) so that the abutment portion between these both sides can be more effectively lubricated. Since the configuration and operation of the other parts are the same as those in the first embodiment described above, the illustration and description regarding the equivalent parts are omitted.

  In the case of the present embodiment, when the minute recesses 65, 65 are formed on the outer surface of the thrust plate 63a facing one side surface of the first connecting plate 23, the minute recesses 65, 65 is extremely small. The reason for this is that among the lubricating oil fed to the radial needle bearings 31a, 31b, 31c (see FIGS. 1, 4, 6) through the recesses 58, 58 (see FIG. 2) formed in the first connecting plate 23, This is for preventing an excessive increase in the rate of oozing out from the recesses 58, 58 through the micro recesses 65, 65. On the other hand, when the minute recesses 65 are formed on the inner surface of the thrust plate 63a facing the outer surface of the input disk 8a (see FIG. 1), the minute recesses 65 are formed. 65 may be increased to some extent.

  Further, in any of the embodiments, a contact portion (see FIG. 1) between one side surface of the first connecting plate 23 and the outer side surface of the input side disk 8a from each of the recesses 58 and 58 (see FIG. 2). If a sufficiently strong oil film can be formed on the contact portion by the lubricating oil that oozes out, the two surfaces can be brought into direct contact with each other (the thrust plate is omitted). In this case, in order to strengthen the oil film between the two surfaces, the surface roughness of both surfaces is improved (made smooth), and the above-described minute concave portions are appropriately formed. The surface on which the concave portions 58 and 58 are formed may be one side surface of the first connecting plate 23 or the outer side surface of the input side disk 8a. In any case, the mating surface blocks the openings of the recesses 58, 58, and the lubricating oil flowing in the recesses 58, 58 toward the radial needle bearings 31a, 31b, 31c is abutted between the two surfaces. Prevent excessive drainage through the department. Then, a sufficient amount of lubricating oil is fed into each of the radial needle bearings 31a, 31b, 31c. When such a structure is employed, a copper or copper alloy plating layer may be formed on one side surface of the first connecting plate 23 or the outer side surface of the input side disk.

  Further, regarding the second carrier 40 (see FIG. 4) constituting the third planetary gear type transmission 4, it is not necessary to consider fretting wear prevention accompanying the elastic deformation of the input side disk 8a. However, a lubricating oil flow path is formed in the second carrier 40 and a base provided in the input shaft 5 so that sufficient lubricating oil can be fed into the radial needle bearings supporting the planetary gears 45 and 46. It is effective from the viewpoint of improving the durability of the radial needle bearing to feed the lubricating oil in the lubricating oil passage 50 into the radial needle bearing through the lubricating oil passage.

  The illustrated example has been described for the case where a half toroidal type continuously variable transmission constituting the present invention is used. However, the present invention is not limited to a half toroidal type continuously variable transmission. Not only the toroidal type but also a full toroidal type toroidal continuously variable transmission can be implemented.

The expanded sectional view equivalent to the A section of FIG. 4 which shows Example 1 of this invention. The perspective view which takes out and shows a carrier. The perspective view of the thrust plate integrated in Example 2 of this invention. Sectional drawing which shows the 1st example of the conventional continuously variable transmission. BB sectional drawing of FIG. The A section enlarged view of FIG. The perspective view which takes out and shows a carrier. The figure similar to FIG. 6 which shows the 2nd example of conventional structure. FIG. 3 is a schematic cross-sectional view exaggeratingly showing a deformation state of an input side disk.

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 Post 18 Thrust angular ball bearing 19 Hollow rotary shaft 20 First sun gear 21 First carrier 22 Intermediate support plate 23 First connection plate 24 Second connecting plate 25 First planetary shaft 26 Second planetary shaft 27 Third planetary shaft 28 Planetary gear 29 Planetary gear 30 Planetary gear 31a, 31b, 31c Radial needle bearing 32 Second sun gear 33 First ring gear 34 Cylindrical portion 35 Loading nut 36 Ring portion 37 Column portion 38 Convex portion 39 Notch 40 Second carrier 41 Low speed clutch 42 Third sun gear 43 Second ring gear 44 High speed clutch 45 Planetary gear 46 Planetary gear 47 Drive shaft 48 Pressing device 49a, 49b Hydraulic chamber 50 Base lubricating oil channel 51a, 51b, 51c Oil supply Passage 52a, 52b, 52c Second oil supply passage 53 Lubricating oil flow path 54 Radial part 55 Axial part 56 Oil passage hole 57 Bulkhead 58 Recessed part 59a, 59b Support hole 60 Second lubricating oil flow path 61 Central hole 62 Radial hole 63, 63a Thrust plate 64 Radial needle bearing 65 Micro recess

Claims (10)

  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 input side disk constituting the continuously variable transmission and the carrier constituting the planetary gear type transmission are adjacent to each other, and the input side disk and the carrier are combined in a state of rotating synchronously. A support plate supported and fixed to the input shaft, and an annular shape arranged concentrically with the support plate and spaced apart in the axial direction, with one side surface facing the outer surface of the input side disk. A connecting plate, and a plurality of planetary shafts supported at both ends by the connecting plate and the support plate, and the planetary gears constituting the planetary gear type transmission are connected to each planetary shaft. Rotate around In the continuously variable transmission supported by this, a lubricating oil flow path is provided inside the carrier, and the downstream end of the lubricating oil flow path is opened to one side of the connecting plate. A continuously variable transmission characterized in that lubricating oil is supplied to a portion between the outer surface of the input side disk.   The continuously variable transmission according to claim 1, wherein a concave portion that is long in the circumferential direction of the connecting plate is formed on one side surface of the connecting plate, and a downstream end of the lubricating oil passage is opened in a part of the concave portion.   The thrust plate sandwiched between the outer surface of the input side disk and one side surface of the connecting plate covers the opening of the concave portion formed on one side surface of the connecting plate, and lubrication discharged from the lubricating oil flow path into the concave portion The continuously variable transmission according to claim 2, wherein oil oozes between an outer side surface of the thrust plate and one side surface of the connecting plate to lubricate a contact portion between the two surfaces.   The continuously variable transmission according to claim 3, wherein the thrust plate is made of a material having wear resistance.   The continuously variable transmission according to claim 4, wherein the input disk and the connecting plate are made of an iron-based alloy, and the thrust plate is made of copper or a copper-based alloy.   The continuously variable transmission according to any one of claims 3 to 5, wherein a large number of minute recesses are formed on the outer surface of the thrust plate.   Each planetary gear is rotatably supported by a radial needle bearing around each planetary shaft, and a lubricating oil passage is provided between the planetary shafts adjacent in the circumferential direction in the carrier. Provided inside the column portion, the lubricating oil can be freely fed from a base lubricating oil flow path provided inside the input shaft, and provided in each of the planetary shafts. The upstream end opening of the second lubricating oil passage having both end portions opened to the direction end surface and the outer peripheral surface of the intermediate portion of each planetary shaft is communicated with the concave portion, and the lubricating oil passage into the concave portion. The remaining lubricating oil discharged and not exuded between the outer surface of the thrust plate and one side surface of the connecting plate is discharged from the downstream end opening of the second lubricating oil flow path, and each of the radial needle bearings Any one of claims 2 to 6, wherein Continuously variable transmission described.   Instead of omitting the concave portion on one side of the connecting plate, a long concave portion is formed in the circumferential direction of the thrust plate on a part of the outer surface of the thrust plate, and the downstream end of the lubricating oil passage is connected to a part of the concave portion. The continuously variable transmission according to any one of claims 3 to 7, wherein the continuously variable transmission is opposed to the first gear.   An input shaft, an output shaft, a toroidal-type continuously variable transmission, and a planetary gear-type transmission arranged concentrically with each other. The input side disk constituting the continuously variable transmission and the carrier constituting the planetary gear type transmission are adjacent to each other, and the input side disk and the carrier are combined in a state of rotating synchronously. A support plate supported and fixed to the input shaft, and an annular shape arranged concentrically with the support plate and spaced apart in the axial direction, with one side surface facing the outer surface of the input side disk. A connecting plate, and a plurality of planetary shafts supported at both ends by the connecting plate and the support plate, and the planetary gears constituting the planetary gear type transmission are connected to each planetary shaft. Around, raji In a continuously variable transmission that is rotatably supported by a needle needle bearing, a lubricating oil flow path is provided inside a column portion provided between the planetary shafts adjacent in the circumferential direction in the carrier. A second lubricating oil passage is formed inside each planetary shaft, and the lubricating oil is fed into the radial needle bearings through the lubricating oil passage and the second lubricating oil passage. Continuously variable transmission.   Lubricating oil can be freely fed into the lubricating oil flow path from a base lubricating oil flow path provided inside the input shaft, and both ends of the second lubricating oil flow path are axial end surfaces of the planetary shafts and the planets. Opened to the outer peripheral surface of the intermediate portion of the shaft, a thrust plate is sandwiched between the input side disk and the connecting plate, and at least one of the opposing surfaces of the connecting plate and the thrust plate The continuously variable transmission according to claim 9, wherein a concave portion is formed on the surface, and the lubricating oil passage and the second lubricating oil passage communicate with each other through the concave portion.

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