JP2001141015A - Method fo packing power roller unit for toroidal type continuously variable transmission - Google Patents

Abstract

PROBLEM TO BE SOLVED: To prevent an inner race track 34 and an outer race track 35 from being damaged such as impressions regardless of oscillation applied during transportation. SOLUTION: A trunnion 6 and a power roller 8 are elastically pressed with pressure in the direction mutually approached in a state that the power roller unit 43 of a toroidal type continuously variable transmission is packed. And the above trouble can be solved by preventing the rotating surfaces of balls 31 and 31 from being hit against the above inner race track 34 and the outer race track 35 while preload is being applied to a thrust ball bearing 29.

Description

DETAILED DESCRIPTION OF THE INVENTION

[0001]

BACKGROUND OF THE INVENTION The method of packing a power roller unit for a toroidal-type continuously variable transmission according to the present invention is used, for example, as a transmission unit of a transmission for an automobile or as a transmission for various industrial machines. The power roller unit of the toroidal type continuously variable transmission is used for packing the power roller unit in order to transport the power roller unit from the power roller unit assembly factory to the toroidal type continuously variable transmission assembly factory.

[0002]

2. Description of the Related Art Toroidal-type continuously variable transmissions as schematically shown in FIGS. 11 to 12 are used as transmissions for automobiles. This toroidal type continuously variable transmission is, for example,
As disclosed in JP-A-71465, the input disk 1 is supported concentrically with the input shaft 1, and the output disk 4 is fixed to the end of the output shaft 3 concentric with the input shaft 1. I have. Inside the casing containing the toroidal-type continuously variable transmission, trunnions 6, 6 that swing about pivots 5, 5 that are twisted with respect to the input shaft 1 and the output shaft 3, are provided.

That is, each of the trunnions 6, 6 has the pivots 5, 5 concentrically provided on the outer surfaces of both ends. In addition, a base end of the displacement shafts 7, 7 is supported at an intermediate portion between the trunnions 6, 6, and the trunnions 6, 6 are pivoted about the pivots 5, 5, whereby
The tilt angles of the displacement shafts 7, 7 can be adjusted freely. Power rollers 8 are rotatably supported around the displacement shafts 7 supported by the trunnions 6 respectively. And each of these power rollers 8, 8 is
The input side and output side disks 2 and 4 are sandwiched between inner surfaces 2a and 4a facing each other. Each of the inner side surfaces 2a, 4a has a concave section obtained by rotating an arc around the pivot 5 as described above.
Each of the power rollers 8, 8 formed on a spherical convex surface
Are brought into contact with the inner side surfaces 2a, 4a.

[0004] A loading device 9 of a loading cam type is provided between the input shaft 1 and the input disk 2, and the input disk 2 is directed toward the output disk 4 by this pressing device 9 so as to be elastic. It can be pressed freely. The pressing device 9 includes a cam plate 10 that rotates together with the input shaft 1, and a plurality (for example, four) of rollers 12, which are rotatably held by a holder 11. The cam plate 10
On one side surface (the left side surface in FIGS. 11 to 12), a drive side cam surface 13 which is an uneven surface extending in the circumferential direction is formed, and the outer side surface of the input side disk 2 (the right side surface in FIGS. 11 to 12). Also, a driven cam surface 14 having a similar shape is formed.
The plurality of rollers 12 are rotatably supported about a radial axis with respect to the center of the input shaft 1.

When the cam plate 10 rotates with the rotation of the input shaft 1 during use of the toroidal-type continuously variable transmission configured as described above, the driving-side cam surface 13 has a plurality of rollers 12, 12.
Is pressed against the driven cam surface 14 formed on the outer surface of the input disk 2. As a result, the input side disk 2
Is pressed by the plurality of power rollers 8, 8, and at the same time, the input side disk is pressed based on the pressing between the driving side and driven side cam surfaces 13, 14 and the plurality of rollers 12, 12. 2 rotates. Then, the rotation of the input side disk 2 is transmitted to the output side disk 4 via the plurality of power rollers 8, 8, and the output side disk 4
, The fixed output shaft 3 rotates.

When the rotational speed ratio (speed change ratio) between the input shaft 1 and the output shaft 3 is changed, and when deceleration is first performed between the input shaft 1 and the output shaft 3, each of the pivots 5 The trunnions 6, 6 are swung in a predetermined direction as a center. The peripheral surfaces 8a, 8a of the power rollers 8, 8 are shown in FIG.
As shown in FIG. 1, each of the displacement shafts 7 is inclined so as to abut against the center portion of the inner surface 2a of the input side disk 2 and the outer portion of the inner side surface 4a of the output side disk 4, respectively. Conversely, when increasing the speed, the above-mentioned pivot 5,
Each of the trunnions 6 and 6 is swung in the opposite direction about 5. The peripheral surface 8 of each of the power rollers 8
As shown in FIG. 12, a and 8a are portions of the inner surface 2a of the input disk 2 near the outer periphery and the inner surface 4a of the output disk 4.
The above-mentioned displacement shafts 7, 7 are inclined so as to abut against the portion near the center. If the inclination angle of each of the displacement shafts 7, 7 is set between those in FIGS. 11 and 12, an intermediate speed ratio can be obtained between the input shaft 1 and the output shaft 3.

FIGS. 13 and 14 show Japanese Utility Model Application No. 63-692.
1 shows an example of a more specific toroidal-type continuously variable transmission described in the microfilm of No. 93 (Japanese Utility Model Laid-Open No. 1-173552). The input side disk 2 and the output side disk 4 are rotatably supported around a cylindrical input shaft 15 via needle bearings 16, 16, respectively. The cam plate 10 is connected to one end of the input shaft 15 (FIG. 13).
(Left end) is spline-engaged with the outer peripheral surface, and the flange 17 prevents movement in the direction away from the input side disk 2. The cam plate 10 and the rollers 12, 12
Thus, a loading cam type pressing device 9 for rotating the input side disk 2 while pressing the input side disk 2 toward the output side disk 4 based on the rotation of the input shaft 15 is constituted. An output gear 18 is connected to the output disk 4 by keys 19, 19 so that the output disk 4 and the output gear 18 rotate in synchronization.

[0008] Both ends of the pair of trunnions 6, 6 are pivoted on a pair of support plates 20, 20 and the axial direction of the pivots 5, 5 described below (front and back in FIG. 13, left and right in FIG. 14). Is displaceably supported. That is, the outer peripheral surfaces of the pivots 5 and 5 fixed to both ends of the trunnions 6 and 6 and the support plates 2 and
Radial needle bearings 22, 22, which are the first radial bearings, are provided between the inner peripheral surfaces of the circular holes 21, 21 formed at both ends of 0, 20, respectively. The outer peripheral surfaces of the outer rings 23 constituting the radial needle bearings 22 are spherical convex surfaces, and are fitted in the respective circular holes 21, so as to swing and displace in the axial direction.

In this manner, the pair of support plates 20, 2
Displacement shafts 7, 7 are supported by circular holes 24, 24 formed in the middle of the trunnions 6, 6, which are supported between the trunnions 6, 6 so as to freely swing and displace in the axial direction. Each of these displacement shafts 7 has a support shaft 25, 25 and a pivot shaft 26, 26 which are parallel and eccentric to each other. Each of the support shaft portions 25, 25 is connected to each of the circular holes 2 described above.
It is rotatably supported inside 4 and 24 via radial needle bearings 27 and 27 which are second radial bearings. Power rollers 8, 8 are rotatably supported around the pivot shafts 26, 26 via radial needle bearings 28, 28, which are third radial bearings.

Note that the pair of displacement shafts 7 are provided at positions 180 ° opposite to the input shaft 15. or,
The direction in which the respective pivot shafts 26, 26 of the respective displacement shafts 7, 7 are eccentric with respect to the respective support shafts 25, 25 is the same as the rotation direction of the input side and output side disks 2, 4. In FIG. 14, the left and right directions are opposite. The eccentric direction is
The direction is substantially perpendicular to the direction in which the input shaft 15 is provided. Accordingly, the power rollers 8 are supported to be slightly displaceable in the direction in which the input shaft 15 is provided. As a result, the power rollers 8, 8 move in the axial direction of the input shaft 15 (see FIG. 13) due to the elastic deformation of the constituent members based on the large load applied to the constituent members in the transmission state of the rotational force. Even in the case of displacement in the left-right direction (the front-back direction in FIG. 14), this displacement can be absorbed without applying excessive force to each part.

A first thrust bearing is provided between the outer surface of each of the power rollers 8, 8 and the inner surface of the intermediate portion of each of the trunnions 6, 6 in order from the outer surface of the power rollers 8, 8. Thrust ball bearings 29 and 29, and thrust needle bearings 30 and 30 as a second thrust bearing,
They are provided in series with each other with respect to the direction of application of the thrust load (vertical direction in FIGS. 13 and 14). Of these, the thrust ball bearings 29, 29 allow rotation of the power rollers 8, 8 while supporting the load in the thrust direction applied to the power rollers 8, 8. Each of such thrust ball bearings 29, 29 has a plurality of balls 31, 31, which are rolling elements, an annular retainer 32, which holds each of the balls 31, 31 in a freely rolling manner, and an annular holder 32, An outer ring 33 is provided. Each of these thrust ball bearings 29, 29
The inner ring raceway 34 is formed on the outer surface of each power roller 8, and the outer ring raceway 35 is formed on the inner surface of each outer ring 33.

The thrust needle bearings 30, 3
Numeral 0 includes a race 36, a retainer 37, and needles 38, 38. Race 36 and cage 37 of these
And are combined so as to be slightly displaceable with respect to the rotation direction. Such a thrust needle bearing 30, 30 has a structure in which the races 36, 36 are in contact with the inner surfaces of the trunnions 6, 6, respectively.
3 is sandwiched between the outer surface and the outer surface. Such thrust needle bearings 30, 30 support the thrust loads applied to the outer races 33, 33 from the power rollers 8, 8 while supporting the pivot shafts 26, 26 and the outer races 33, 3.
3 is allowed to swing about the support shaft portions 25, 25.

Further, drive rods 39, 39 are provided at one end (the left end in FIG. 14) of each of the trunnions 6, 6, respectively.
And drive pistons 40, 40 are fixedly mounted on the outer peripheral surface of the intermediate portion of each of the drive rods 39, 39. And
These drive pistons 40, 40 are oil-tightly fitted in drive cylinders 41, 41, respectively.

In the case of the toroidal type continuously variable transmission configured as described above, the rotation of the input shaft 15 is transmitted to the input side disk 2 via the pressing device 9. Then, the rotation of the input side disk 2 is transmitted to the output side disk 4 via the pair of power rollers 8, 8, and further, the output side disk 4
Is taken out from the output gear 18. Input shaft 15
When changing the rotation speed ratio between the output gear 18 and
The pair of drive pistons 40, 40 are displaced in directions opposite to each other. The pair of trunnions 6, 6 are displaced in opposite directions with the displacement of the drive pistons 40, 40. For example, the lower power roller 8 in FIG. Power roller 8 on the left side of FIG.
Each is displaced. As a result, the direction of the tangential force acting on the contact portions between the peripheral surfaces 8a, 8a of the power rollers 8, 8 and the inner surfaces 2a, 4a of the input disk 2 and the output disk 4 changes. I do. Then, with the change in the direction of the force, each of the trunnions 6, 6 is pivoted about the pivots 5, 5 supported by the support plates 20, 20.
Swing in opposite directions. As a result, the aforementioned FIGS.
As shown in FIG. 2, the peripheral surface 8 of each of the power rollers 8
The contact positions of the inner shafts a, 8a and the inner surfaces 2a, 4a change, and the rotational speed ratio between the input shaft 15 and the output gear 18 changes.

Adjustment of the rotational speed ratio between the input shaft 15 and the output gear 18 to a desired value is performed by regulating the amount of movement of the driving pistons 40, 40.
The amount of movement of each of the drive pistons 40, 40 is regulated by a precess cam (not shown) fixed to an end or an intermediate portion of each of the drive rods 39, a spool or a sleeve of a spool valve (also not shown). Is performed by the engagement of. Further, as described above, when transmitting the rotational force between the input shaft 15 and the output gear 18, each of the power rollers 8,
8 is displaced in the axial direction of the input shaft 15, and the displacement shafts 7, which pivotally support the power rollers 8, are slightly rotated about the support shaft portions 25, 25. I do.
As a result of this rotation, the outer surfaces of the outer rings 33, 33 of the thrust ball bearings 29, 29 and the inner surfaces of the trunnions 6, 6 are relatively displaced. Since the thrust needle bearings 30, 30 exist between the outer surface and the inner surface, the force required for the relative displacement is small. Therefore, the force for changing the inclination angle of each of the displacement shafts 7 can be small as described above.

Further, in order to increase the transmittable torque, two input disks 2A and 2B and two output disks 4 and 4 are provided around the input shaft 15 as shown in FIGS. A structure in which two input disks 2A and 2B and two output disks 4 and 4 are arranged in parallel with respect to the power transmission direction is also disclosed in, for example, JP-A-11-210853.
As described in Japanese Unexamined Patent Publication (Kokai) No. HEI 10-301, it has been widely known.

In each of the structures shown in FIGS. 15 and 16, an output gear 18 is supported around an intermediate portion of the input shaft 15 so as to be rotatable with respect to the input shaft 15. The output side disks 4, 4 are spline-engaged with both ends of the provided cylindrical portion. Needle bearings 16 and 16 are provided between the inner peripheral surface of each of the output side disks 4 and 4 and the outer peripheral surface of the input shaft 15, and these output side disks 4 and 4 are provided around the input shaft 15. The rotation of the input shaft 15 and the displacement of the input shaft 15 in the axial direction are freely supported. or,
The input side disks 2A and 2B are connected to both ends of the input shaft 15 via splines or ball splines.
The input shaft 15 is rotatably supported together with the input shaft 15. The input shaft 15 is rotationally driven by a driving shaft 42 via a loading device 9 of a loading cam type and one input side disk 2A.

The input disks 2A, 2B rotate in synchronism with the input shaft 15, and the rotation of the input disks 2A, 2B is controlled via a plurality of power rollers 8, 8 respectively. It is transmitted to each output side disk 4,4. As described above, since the transmission of power is performed in two systems, large power can be transmitted.

Conventionally, when assembling a toroidal-type continuously variable transmission configured and operating as described above, a housing 81 (FIG. 1) for accommodating the main body of the toroidal-type continuously variable transmission is provided.
Each component is assembled in order inside 4). Therefore, the deviation of the positional relationship of each part based on the integration of the dimensional errors of the constituent parts, and whether or not the constituent parts function properly, is determined after all the constituent parts are assembled in the housing 81. I could only confirm. On the other hand, in order to ensure the efficiency and durability of the toroidal-type continuously variable transmission, the positional relationship between the components must be maintained with high accuracy. For this reason, when the deviation of the positional relationship of each part becomes large based on the integration of the dimensional errors of the components, the components are assembled in the housing 81 in order to reduce the deviation by combining with other components. The toroidal CVT must be disassembled and reassembled. When the assembling work of the toroidal type continuously variable transmission is performed in this way, the manufacturing operation of the toroidal type continuously variable transmission is troublesome, and the cost cannot be reduced.

In view of such circumstances, Japanese Patent Laid-Open No. 11-15 / 1999
No. 3203 discloses a power roller unit 43 for a toroidal type continuously variable transmission as shown in FIGS.
JP-A-210853 discloses an input-side disk power roller unit 44 for a toroidal-type continuously variable transmission as shown in FIG. 19, and JP-A-11-166605 discloses a toroidal-type continuously variable transmission as shown in FIG. Output disk units 45 are described.

The power roller unit 43 for a toroidal-type continuously variable transmission shown in FIGS. 17 and 18 is provided with first shafts 5 and 5 around the pivots 5 and 5 concentrically fixed to both end surfaces of the trunnion 6, respectively. Radial needle bearings 22 are provided. In the middle of the trunnion 6, a circular hole 24 formed in a direction perpendicular to the axial direction of each of the pivots 5, 5 is displaced by a support shaft 25 and a pivot 26, which are parallel and eccentric to each other. The support shaft portion 25 of the shaft 7 is rotatably supported via a radial needle bearing 27 which is a second radial bearing.

A power roller 8 is rotatably supported around the pivot 26 via a radial needle bearing 28 as a third radial bearing. Between the outer surface of the power roller 8 and the inner surface of the middle part of the trunnion 6, a thrust ball bearing 29 and a thrust needle bearing 30, which are first and second thrust bearings, are moved in the thrust load acting direction. Are provided in series with each other.
The trunnion 6 and the radial needle bearings 22, 27, 28, which are separate parts from each other, are used.
Before the assembling of the displacement shaft 7, the power roller 8, the thrust ball bearing 29 and the thrust needle bearing 30 to the toroidal type continuously variable transmission, and after the assembly of the toroidal type continuously variable transmission is completed. Are pre-assembled in the positional relationship.

The input-side disc power roller unit 44 for the toroidal-type continuously variable transmission shown in FIG. 19 is a component that is separate from the input shaft 15, the cam plate 10, the input-side disc 2A, Rollers 12, 12 and retainer 11
The preload spring 49 and the preload spring 49 are assembled in advance in a positional relationship after the assembly of the toroidal-type continuously variable transmission before assembling to the toroidal-type continuously variable transmission. In order to constitute such an input-side disk unit 44 for a toroidal-type continuously variable transmission, the cam plate 10 is mounted on the inner surface of a flange 46 fixed to one end (the left end in FIG. 19) of the input shaft 15 by a ball bearing. By 47
The input shaft 15 is supported rotatably. or,
The input side disk 2A is supported via a ball spline 48 around an intermediate portion of the input shaft 15 near one end. Accordingly, the input side disk 2A freely supports the input shaft 15 with respect to the displacement in the axial direction with respect to the input shaft 15 and the rotation synchronized with the input shaft 15.
Further, the driving cam surface 1 formed on the inner surface of the cam plate 10
A plurality of rollers 12, 12 are sandwiched between the driven side 3 and the driven side cam surface 14 formed on the outer side of the input side disk 2A to constitute a loading cam type pressing device 9. The rollers 12, 12 are rotatably held by a retainer 11, which is formed in a ring shape as a whole.
A preload spring 4 is provided between a step formed on the outer peripheral surface of one end of the input shaft 15 and the outer surface of the input side disk 2A.
9 are provided. The preload spring 49 presses the input-side disc 2A against the power rollers 8, 8 (see FIGS. 11 to 16) before the pressing device 9 generates a pressing force.

The input side disk unit 44 for a toroidal type continuously variable transmission constructed as described above is a separate component from the input shaft 15, the ball bearing 47, and the cam plate 10
, The input side disk 2A, the rollers 12, 12, the retainer 11, and the preload spring 49, for example,
Before assembling to the toroidal-type continuously variable transmission as shown in FIG. 6, the toroidal-type continuously variable transmission is assembled in a positional relationship after assembly is completed.

Further, the output side disk unit 45 for a toroidal type continuously variable transmission shown in FIG. 20 includes an output side disk 4, a through hole 50 formed in the center of the output side disk 4, and a through hole 50. And a locking groove 51 formed in the inner peripheral surface of the through hole 50.
And a retaining ring 52 for preventing the needle bearing 16 from slipping out of the through hole 50 before the toroidal-type continuously variable transmission is assembled. Assembled in advance in the positional relationship.

As described above, if the power roller unit 43 for the toroidal type continuously variable transmission, the input side disk unit 44 for the toroidal type continuously variable transmission, and the output side disk unit 45 for the toroidal type continuously variable transmission are constructed, Before assembling these components in the housing, it is necessary to determine whether or not the positional relationship between the components is correct based on the sum of the dimensional errors of the components of the units 43 to 45, and whether the components function correctly. You can check. Accordingly, the positional relationship between the constituent members is increased to secure the efficiency and durability of the toroidal-type continuously variable transmission without requiring troublesome work such as disassembling and reassembling the entire toroidal-type continuously variable transmission. Accuracy can be maintained.

[0027]

As described above, Japanese Patent Laid-Open No.
Japanese Patent Application Publication No. 1-153203 discloses a power roller unit 43 for a toroidal type continuously variable transmission which can efficiently assemble a high performance toroidal type continuously variable transmission. It does not describe a method for transporting the power roller unit 43 without damaging it. On the other hand, the power roller unit 43 for the toroidal type continuously variable transmission is similar to the power roller unit 4.
Conveyed from the assembly plant of No. 3 to the assembly plant of the toroidal type continuously variable transmission. During this transfer operation, fine vibrations are repeatedly applied to the power roller unit 43 for the toroidal type continuously variable transmission. By this vibration, the thrust ball bearing 29 as the first thrust bearing incorporated in the power roller unit 43 for the toroidal-type continuously variable transmission constitutes the thrust ball bearing 29. 34 and the outer ring raceway 35, and these two raceways 34,
There is a possibility that damage such as an indentation may be caused to the thrust ball bearing 29 to shorten the life of the thrust ball bearing 29.

In order to prevent the life of the thrust ball bearing 29 from being shortened due to such a cause, an elastic ring such as a rubber band such as an O-ring is externally fitted to the power roller unit 43 for the toroidal type continuously variable transmission. It is conceivable to convey the thrust ball bearing 29 in a state where a preload is applied.
However, in such a method, an operation of fitting an elastic ring to each of the power roller units 43 for the toroidal-type continuously variable transmission is required, which deteriorates workability and causes an increase in cost. In addition, it is difficult to stably apply the preload by the elastic ring, and it may not be possible to reliably prevent damage due to conveyance. In view of such circumstances, the present invention has been devised to realize a packing method in which the inner raceway 34 and the outer raceway 35 are less likely to be damaged when the power roller unit 43 for the toroidal type continuously variable transmission is transported. is there.

[0029]

SUMMARY OF THE INVENTION A power roller unit for a toroidal type continuously variable transmission that is packed by the method for packing a power roller unit for a toroidal type continuously variable transmission according to the present invention is a conventional power roller unit shown in FIGS. Like the structure, a trunnion in which concentric pivots are fixed to both end surfaces, a pair of first radial bearings provided around these two pivots, and an intermediate portion of the trunnion in an axial direction of each of the pivots. It consists of a circular hole formed at right angles to the hole, a supporting shaft portion and a pivot shaft portion which are parallel to each other and eccentric to each other, and the supporting shaft portion is rotatable inside the circular hole via a second radial bearing. And a power roller rotatably supported via a third radial bearing around the pivot shaft portion, between an outer surface of the power roller and an inner surface of an intermediate portion of the trunnion. , First it provided in series with each other with respect to the direction of action of the strike force, and a second thrust bearing. Then, the trunnion, the first, second, and third radial bearings, the displacement shaft, the power roller, and the first and second thrust bearings, which are separate components, are assembled to a toroidal-type continuously variable transmission. Previously, the toroidal-type continuously variable transmission is assembled in the positional relationship after the assembly is completed. In order to convey such a power roller unit for a toroidal type continuously variable transmission, in the method of packing a power roller unit for a toroidal type continuously variable transmission according to the present invention, the trunnion and the power roller are separated by an elastic cushioning material. Then, the power roller unit for a toroidal-type continuously variable transmission is packed with the first and second thrust bearings being sandwiched from both sides in the axial direction of the displacement shaft and preloaded.

[0030]

According to the method of packing the power roller unit for a toroidal type continuously variable transmission of the present invention configured as described above, the first thrust bearing incorporated in the power roller unit for a toroidal type continuously variable transmission is configured. The rolling surface of the rolling element and the inner raceway and the outer raceway can be kept pressed against each other. Therefore, the rolling elements do not collide with the inner raceway and the outer raceway, so that there is no damage such as dents on both raceways, and the life of the first thrust bearing can be secured. Moreover, it is possible to easily and reliably apply preload to the first and second thrust bearings constituting the power roller unit for the toroidal type continuously variable transmission.

[0031]

1 and 2 show an embodiment of the present invention. This example shows four sets of power roller units for a toroidal-type continuously variable transmission that are necessary to constitute one toroidal-type continuously variable transmission in a packing box 53 made of metal, synthetic resin, cardboard, or the like. The case where 43 and 43 are packed is shown. A first buffer receiving member 54 is provided at one end (upper end side in FIG. 1) of the packing box 53, a second buffer receiving member 55 is provided at an intermediate bottom, and a bottom end is provided at the other end (lower end in FIG. 1). Is provided with a third buffer receiving member 56, respectively.

Each of the buffer receiving members 54 to 56 is made of an elastic material such as hard urethane.
Sets of power roller unit 4 for toroidal type continuously variable transmission
In order to support 3, 43, receiving portions 57a, 57b,
57c is provided. First, four receiving portions 57a, 57b are provided on the first and second buffer receiving members 54, 55 provided on the one end side bottom portion and the intermediate side bottom portion, respectively, in a state where the phases are matched with each other. . These receiving portions 57a, 57b
The trunnions 6 and 6 constituting the power roller units 43 and 43 for the toroidal-type continuously variable transmissions are respectively provided.
The outer rings 23, 23 constituting the radial needle bearings 22, 22 provided around the pivots 5, 5 at both ends of the outer ring 23 can be fitted inside without play. The receiving portion 57c provided on the third buffer receiving member 56 provided on the bottom portion on the other end side is provided with a drive attached to any of the power roller units 43 for the toroidal type continuously variable transmission (the left end portion in FIG. 1). The distal end (lower end in FIG. 1) of the rod 39 is freely fit inside without rattling.

At the bottom of the packing box 53, between the first buffer receiving member 54 and the second buffer receiving portion 55, a lower fixing jig 58 is provided. This lower fixing jig 58
Is formed by supporting and fixing a lower cushioning member 60 made of an elastic material such as hard urethane on the upper surface of a lower frame 59 made of a metal plate. At the four positions on the upper surface of the lower cushioning material 60 where the phases coincide with the receiving portions 57a and 57b, the power rollers 8 (constituting the power roller units 43 and 43 for the toroidal type continuously variable transmissions, respectively) are provided. 17 and 18) are provided.

An upper fixing jig 62 is disposed above the lower fixing jig 58. This upper fixing jig 62
Is formed by supporting and fixing an upper cushioning member 64 made of an elastic material such as hard urethane on the lower surface of an upper frame 63 made of a metal plate. The receiving portions 57a, 57b, 61
The power roller units 43, 43 for the toroidal-type continuously variable transmissions are respectively located at four positions where the phases match.
The upper receiving portions 65, 65 capable of freely holding the intermediate portions of the trunnions 6, 6, which constitute the above, are provided.

The lower fixing jig 58 and the upper fixing jig 62 described above are connected in a state where both ends thereof are connected to each other.
The trunnions 6, 6 and the power rollers 8, 8 constituting the power roller units 43, 43 for the toroidal-type continuously variable transmission are sandwiched from both axial sides of the displacement shafts 7, 7. . And each of these trunnions 6,
A preload is applied to thrust ball bearings 29 and 29 and thrust needle bearings 30 and 30 (see FIGS. 13, 14 and 17) existing between the power rollers 6 and the power rollers 8 and 8.

For this purpose, a hook 66 formed by forming a bar or a plate into a U-shape is provided at one end (the left end in FIGS. 1 and 2) of the lower frame 59 constituting the lower fixing jig 58. Both lower ends are pivotally supported by bolts 67 and nuts 68.
A locking recess 69 for locking the upper end of the hook 66 is provided on the upper surface of one end of the upper frame 63 constituting the upper fixing jig 62. When the power roller units 43 for the toroidal-type continuously variable transmission are pressed down, the upper end of the hook 66 is locked in the locking recess 69, and one end of the upper fixing jig 62 is fixed. Do not separate from the lower fixing jig 58.

Further, a toggle-type clamp device 70 is provided between the other end of the lower fixing jig 58 (the right end in FIGS. 1 and 2) and the other end of the upper fixing jig 62. Thus, the other end of the upper fixing jig 62 can be strongly pressed downward. That is, the lower bracket 71 is connected and fixed to the other end of the lower fixing jig 58, and the clamp device 70 is provided on the upper surface of the lower bracket 71.
An upper bracket 73 is fixedly connected to the other end of the upper fixing jig 62. The clamp device 70 is a commercially available product having a well-known structure, and causes the pressing arm 74 to swing by a toggle mechanism that expands and contracts with the rotation of the handle 72,
The upper surface of the upper bracket 73 can be pressed freely by a pressing member 75 supported at the tip of the pressing arm 74. The pressing member 75 is screwed to the tip of the pressing arm 74 so that the vertical position can be adjusted freely.

The operation of storing the power roller units 43 for the toroidal type continuously variable transmission in the packing box 53 as described above is performed as follows. In the following description, the case where each of the toroidal-type continuously variable transmission power roller units 43, 43 is double-packed with an inner packing bag and an outer packing bag (not shown) will be described. . First, an outer packing bag is laid in the packing box 53 before the first to third buffer receiving members 54 to 56 and the lower fixing jig 58 are stored in the packing box 53. Then, the first to third buffer receiving members 54 to 56 and the lower fixing jig 58 are arranged in the outer packing bag as shown in FIG.

Next, an inner packing bag (not shown) is laid on the first to third buffer receiving members 54 to 56 and the lower fixing jig 58, and then the inner packing bag is placed in the inner packing bag. Power roller unit 4 for each of the above toroidal type continuously variable transmissions
3 and 43 are placed as shown in FIG. In this state,
The power roller units 43 for these toroidal-type continuously variable transmissions have completed operations such as inspection, cleaning, and application of rust preventive oil. Then, after closing the inner packing bag,
The upper fixing jig 62 is placed over the power roller units 43 for the toroidal type continuously variable transmission (from above the inner packing bag), and a locking recess provided at one end of the upper fixing jig 62 is provided. The upper end of the hook 66 is locked to 69. Then, the upper bracket 7 fixedly connected to the other end of the upper fixing jig 62 by the clamp device 70.
Press 3 down. Thereafter, the outer packing bag is closed, and then the packing box 53 is closed, thereby completing the packing operation.

After the packing operation is completed, the power roller unit 4 for each of the toroidal type continuously variable transmissions described above is used.
The trunnions 6, 6 constituting the upper and lower fixing jigs 62 are elastically pressed downward by the upper cushioning material 64 constituting the upper fixing jig 62. As a result, a preload is applied to the thrust ball bearings 29, 29 and the thrust needle bearings 30, 30 incorporated in the power roller units 43, 43 for the toroidal type continuously variable transmission. Then, the rolling surfaces of the balls 31, 31 constituting the respective thrust ball bearings 29, 29, the inner raceway 34 and the outer raceway 35 are kept pressed against each other. Therefore, regardless of the vibration applied during the conveyance, the balls 31, 31 do not collide with the inner raceway 34 and the outer raceway 35.
Damage such as indentation does not occur on the 35, and the life of the thrust ball bearings 29 can be secured.

The thrust ball bearing 2 incorporated in each of the power roller units 43 for the toroidal type continuously variable transmission.
9 and 29 and the thrust needle bearings 30 and 30 are simultaneously and reliably applied to the four toroidal-type continuously variable transmission power roller units 43 and 43 accommodated in one packing box 53. I can do it. Accordingly, as in the case where the power roller units 43 for the toroidal-type continuously variable transmission are suppressed one by one by the elastic ring, the preloading work becomes troublesome and causes an increase in cost. The application is not reliable, and does not cause the occurrence of defective products due to conveyance.

Next, FIGS. 3 to 10 are not directly related to the present invention, but the input side disk unit 44 for a toroidal type continuously variable transmission as shown in FIG. This figure shows a state in which the output side disk unit 45 for the toroidal type continuously variable transmission and the input side disk 2B are packed. FIGS. 3 and 4 show an input-side disk unit 44 for a toroidal-type continuously variable transmission, an output-side disk unit 45 for a toroidal-type continuously variable transmission, and a disk unit 45 required to constitute one toroidal-type continuously variable transmission. Input side disk 2B
Is made of an elastic material such as hard urethane.
3 shows a state in which it is housed in a buffer unit 76 as shown in FIG. This buffer unit 76 has a main part 77 as shown in FIG.
And first to third sub-sections 78 to 80 as shown in FIGS.

The four toroidal type continuously variable transmission power roller units 43, 43 packed by the packing method of the present invention as described above, and the toroidal type continuously variable transmission stored as shown in FIGS. The input disk unit 44 for the transmission, the output disk units 45 and 45 for the toroidal-type continuously variable transmission, and the input disk 2B are combined into one set to assemble one toroidal-type continuously variable transmission.
The units 43 to 45, etc., which are set as one set in this way,
By assembling these units 43 to 45 and the like having uniform dimensions and characteristics, a toroidal type continuously variable transmission having desired performance can be obtained.

[0044]

The packing method of the power roller unit for a toroidal-type continuously variable transmission according to the present invention is constructed as described above, so that the components are damaged due to the vibration during transportation without increasing the cost. And a toroidal type continuously variable transmission having excellent durability can be obtained.

[Brief description of the drawings]

FIG. 1 is a plan view partially showing an example of an embodiment of the present invention;

FIG. 2 is a perspective view showing a main part taken out.

FIG. 3 is a plan view showing a state in which an input side disk unit for a toroidal type continuously variable transmission, an output side disk unit for a toroidal type continuously variable transmission, and an input side disk are packed.

FIG. 4 is a view as viewed from below in FIG. 3;

FIG. 5 is a plan view of the buffer unit.

FIG. 6 is a view seen from the left side of FIG. 5;

FIG. 7 is a plan view of a main part of the buffer unit.

FIG. 8 is a perspective view of the first sub-part.

FIG. 9 is a perspective view of the second sub-part.

FIG. 10 is a perspective view of the third sub part.

FIG. 11 is a side view showing a basic configuration of a conventionally known toroidal type continuously variable transmission in a state of maximum deceleration.

FIG. 12 is a side view showing a state at the time of maximum speed increase.

FIG. 13 is a sectional view showing a first example of a conventional specific structure.

FIG. 14 is a sectional view taken along line AA of FIG. 13;

FIG. 15 is a cross-sectional view of a principal part showing a second example of a conventional specific structure.

FIG. 16 is an essential part cross-sectional view showing the third example.

FIG. 17 is a cross-sectional view of a conventionally known power roller unit for a toroidal-type continuously variable transmission.

FIG. 18 is a view seen from the right side of FIG. 17;

FIG. 19 is a cross-sectional view of a conventionally known input side disk unit for a toroidal type continuously variable transmission.

FIG. 20 is a sectional view of the output side disk unit for the toroidal type continuously variable transmission.

[Description of Signs] 1 Input shaft 2, 2A, 2B Input side disk 2a Inner surface 3 Output shaft 4 Output side disk 4a Inner surface 5 Pivot shaft 6 Trunnion 7 Displacement shaft 8 Power roller 8a Peripheral surface 9 Pressing device 10 Cam plate 11 Holding Container 12 Roller 13 Drive side cam surface 14 Driven side cam surface 15 Input shaft 16 Needle bearing 17 Flange 18 Output gear 19 Key 20 Support plate 21 Circular hole 22 Radial needle bearing 23 Outer ring 24 Circular hole 25 Support shaft 26 Pivot Shaft 27 Radial needle bearing 28 Radial needle bearing 29 Thrust ball bearing 30 Thrust needle bearing 31 Ball 32 Cage 33 Outer ring 34 Inner ring raceway 35 Outer raceway 36 Race 37 Cage 38 Needle 39 Drive rod 40 Drive piston 41 Drive cylinder 42 Drive shaft 43 Toroidal-type continuously variable transmission Power roller unit 44 Input side disk unit for toroidal type continuously variable transmission 45 Output side disk unit for toroidal type continuously variable transmission 46 Flange 47 Ball bearing 48 Ball spline 49 Preload spring 50 Through hole 51 Locking groove 52 Retaining ring 53 Packing box 54 First buffer receiving material 55 Second buffer receiving material 56 Third buffer receiving material 57a, 57b, 57c Receiving part 58 Lower fixing jig 59 Lower frame 60 Lower buffer material 61 Lower receiving part 62 Upper fixing jig 63 Upper frame 64 Upper cushioning material 65 Upper receiving part 66 Hook 67 Bolt 68 Nut 69 Locking concave part 70 Clamping device 71 Lower bracket 72 Handle 73 Upper bracket 74 Pressing arm 75 Pressing member 76 Buffer unit 77 Main part 78 First sub-part 79 Second sub-part 80 Third sub-part 81 Housing

Continued on the front page F-term (reference) 3E068 AA34 AB04 BB06 BB11 BB12 BB16 DD14 DD40 EE01 3J051 AA03 BA03 BD02 BE09 CA05 CB07 EC03 ED20 FA02

Claims (1)

[Claims] 1. A trunnion having concentric pivots fixed to both end surfaces, a pair of first radial bearings provided around the two pivots, and an axial portion of each of the pivots at an intermediate portion of the trunnion. And a support shaft and a pivot shaft parallel to each other and eccentric to each other, and the support shaft is rotated inside the hole through a second radial bearing. A displacement shaft freely supported, a power roller rotatably supported via a third radial bearing around the pivot shaft portion, and an outer surface of the power roller and an inner surface of an intermediate portion of the trunnion. The first and second thrust bearings provided in series with each other with respect to the direction in which the thrust load acts, and the trunnions and the first, second, and third radial bearings and the displacement shafts, which are separate components, are provided. Power roller and first and second Before assembling the second thrust bearing to the toroidal type continuously variable transmission, the power roller unit for the toroidal type continuously variable transmission is transported in a positional relationship after assembly of the toroidal type continuously variable transmission. Therefore, the trunnion and the power roller are sandwiched between both sides of the displacement shaft in the axial direction by an elastic cushioning material, and the toroidal-type continuously variable transmission is applied in a state where a preload is applied to the first and second thrust bearings. For packing a power roller unit for a toroidal type continuously variable transmission that packs a power roller unit for a vehicle.