JPH07259947A - Toroidal type continuously variable transmission - Google Patents

Abstract

PURPOSE:To realize the miniaturization and reduction of the weight, and simplify the hydraulic pipings by making a plurality of trunnions displaceable in the axial direction by one hydraulic cylinder. CONSTITUTION:The movement of a driving piston 37 of a hydraulic cylinder 38 is transmitted to a lower trunnion 6 through a driving rod 36. The movement of this trunnion 6 is transmitted to an upper trunnion 6 through a link mechanism 50. The thrust load in the direction of the arrows alpha and beta is applied to the respective trunnions 6, 6 from power rollers 8, 8 during the operation. When the quantity of the pressurized oil to be fed into a pressure chamber 60 is changed, the respective trunnions 6, 6 are simultaneously displaced in the axial direction.

Description

Detailed Description of the Invention

[0001]

BACKGROUND OF THE INVENTION The toroidal type continuously variable transmission according to the present invention is used, for example, as a transmission for automobiles or as a transmission for various industrial machines.

[0002]

2. Description of the Related Art As a transmission for an automobile, the use of a toroidal type continuously variable transmission as schematically shown in FIGS. This toroidal type continuously variable transmission supports an input side disk 2 concentrically with the input shaft 1 as disclosed in, for example, Japanese Utility Model Laid-Open No. 62-71465, and the input shaft 1
At the end of the output shaft 3 arranged concentrically with the output side disk 4
Is fixed. Inside the casing in which the toroidal type continuously variable transmission is housed, there are provided trunnions 6 and 6 which swing around a pivot shaft 5 and 5 which are twisted with respect to the input shaft 1 and the output shaft 3. .

The trunnions 6, 6 are provided with the pivots 5, 5 on the outer surfaces of both ends. Further, the base ends of the displacement shafts 7, 7 are supported on the central portions of the trunnions 6, 6 and the trunnions 6, 6 are swung about the pivot shafts 5, 5, so that the displacement shafts 7, The inclination angle of 7 can be freely adjusted. Power rollers 8, 8 are rotatably supported around displacement shafts 7, 7 supported by the trunnions 6, 6, respectively. The power rollers 8, 8 are sandwiched between the input side and output side disks 2, 4.

The inner surfaces 2a, 4a of the input-side and output-side disks 2, 4 facing each other have a cross-section of a concave surface obtained by rotating an arc about the pivot 5. The peripheral surfaces 8a, 8a of the power rollers 8, 8 formed in the spherical convex surface are in contact with the inner side surfaces 2a, 4a.

A loading cam type pressing device 9 is provided between the input shaft 1 and the input side disk 2, and the pressing device 9 causes the input side disk 2 to face the output side disk 4 and elastically moves. Pressing. This pressing device 9
Is a cam plate 10 that rotates together with the input shaft 1, and a retainer 11.
A plurality of (for example, four) rollers 12 held by
It is composed of 12 and. On one side surface (left side surface of FIGS. 4 to 5) of the cam plate 10, a cam surface 13 which is a concavo-convex surface extending in the circumferential direction is formed, and the outer surface of the input side disk 2 (right side of FIGS. 4 to 5). The same cam surface 14 is also formed on the surface). Then, the plurality of rollers 12, 12 are rotatably supported about a shaft in the radial direction with respect to the center of the input shaft 1.

When the toroidal type continuously variable transmission constructed as described above is used, when the cam plate 10 rotates as the input shaft 1 rotates, the cam surface 13 causes the plurality of rollers 12, 1 to rotate.
2 is pressed against the cam surface 14 on the outer surface of the input side 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, based on the meshing between the pair of cam surfaces 13, 14 and the plurality of rollers 12, 12. The input side disk 2 rotates. And
The rotation of the input side disk 2 is transmitted to the output side disk 4 through the plurality of power rollers 8 and the output shaft 3 fixed to the output side disk 4 rotates.

When the rotational speeds of the input shaft 1 and the output shaft 3 are changed, and when deceleration is first performed between the input shaft 1 and the output shaft 3, the trunnions 6, 6 centering on the pivot shafts 5, 5 are used.
As shown in FIG. 4, the peripheral surfaces 8a, 8a of the power rollers 8, 8 are moved toward the center of the inner side surface 2a of the input side disk 2 and the outer side of the inner side surface 4a of the output side disk 4. The displacement shafts 7, 7 are tilted so as to abut with and respectively.

On the other hand, when increasing the speed, the trunnions 6, 6 are swung so that the peripheral surfaces 8a, 8a of the power rollers 8, 8 are located inside the input side disk 2 as shown in FIG. The outer peripheral portion of the side surface 2a and the inner side surface 4a of the output side disk 4
The displacement shafts 7, 7 are tilted so that they are brought into contact with the central portions of the displacement shafts 7, 7, respectively. The inclination angles of the displacement axes 7 and 7 are shown in FIG.
5 and FIG. 5, an intermediate gear ratio can be obtained between the input shaft 1 and the output shaft 3.

Further, FIGS. 6 to 7 show Japanese Patent Application No. 63-6929.
3 shows a more specific toroidal-type continuously variable transmission described in the microfilm of No. 3 (Actual Kaihei No. 1-173552). Input side disk 2 and output side disk 4
Is rotatably supported around a cylindrical input shaft 15 via needle bearings 16 and 16, respectively. The cam plate 10 is spline-engaged with the outer peripheral surface of the end portion (the left end portion in FIG. 6) of the input shaft 15, and is prevented from moving in the direction away from the input side disk 2 by the collar portion 17. Then, the cam plate 10 and the rollers 12 and 12 cause the input side disk 2 to rotate based on the rotation of the input shaft 15.
Is rotated while being pressed toward the output side disk 4,
A loading cam type pressing device 9 is configured. An output gear 18 is provided on the output side disk 4 with keys 19, 19
And the output side disk 4 and the output gear 18
It is designed so that and rotate in synchronization.

Both ends of the pair of trunnions 6, 6 are oscillated and axially (front and back direction in FIG. 6, left and right direction in FIG. 7) on a pair of support plates 20 and 20 which are support members. It is supported so that it can move freely. The displacement shafts 7, 7 are supported in the circular holes 23, 23 formed in the intermediate portions of the trunnions 6, 6. The displacement shafts 7, 7 are parallel to each other and eccentric to the support shaft portions 21, 21 and the pivot shaft portion 22,
22 and 22 respectively. Each support shaft part 2
1, 21 are rotatably supported inside the circular holes 23, 23 via radial needle bearings 24, 24. Further, the power rollers 8, 8 are rotatably supported around the respective pivot shaft portions 22, 22 via radial needle bearings 25, 25.

The pair of displacement shafts 7, 7 are provided at positions opposite to the input shaft 15 by 180 degrees. or,
The direction in which the pivot shafts 22, 22 of the displacement shafts 7, 7 are eccentric with respect to the support shafts 21, 21 is the same as the rotation direction of the input side and output side disks 2, 4. In FIG. 7, the left and right directions are reversed. Further, the eccentric direction is a direction substantially orthogonal to the arrangement direction of the input shaft 15. Therefore, each of the power rollers 8 and 8 is supported so as to be slightly displaceable in the arrangement direction of the input shaft 15.
As a result, even if the power rollers 8, 8 tend to be displaced in the axial direction of the input shaft 15 due to the dimensional accuracy of the components, etc., without applying an unreasonable force to the components, This displacement can be absorbed.

Between the outer surface of each of the power rollers 8 and 8 and the inner surface of the intermediate portion of each of the trunnions 6, 6, there are thrust ball bearings 26, in order from the outer surface of the power rollers 8, 8. 26 and thrust needle bearings 27, 27 are provided. The thrust ball bearings 26, 26 support the loads in the thrust direction applied to the power rollers 8, 8 and allow the power rollers 8, 8 to rotate. Such thrust ball bearings 26, 26 have a plurality of balls 29, 29 and balls 29, 2 respectively.
An annular retainer 28, 28 for holding 9 in a rollable manner,
It is composed of an annular outer ring 30, 30. The inner ring raceways of the thrust ball bearings 26, 26 are formed on the outer side surfaces of the power rollers 8, 8 and the outer ring raceways are formed on the inner side surfaces of the outer races 30, 30 respectively.

Further, the thrust needle bearings 27, 27
Is composed of a race 31, a retainer 32, and needles 33, 33. Of these, the race 31 and the cage 32 are combined so as to be slightly displaceable in the rotational direction. Such thrust needle bearings 27, 27 are provided between the inner surfaces of the trunnions 6 and 6 and the outer surfaces of the outer rings 30, 30 in a state where the races 31, 31 are in contact with the inner surfaces of the trunnions 6, 6. It is sandwiched. The thrust needle bearings 27, 27 as described above support the thrust load applied to the outer rings 30, 30 from the power rollers 8, 8 while the pivot shafts 22, 22 and the outer rings 30, 30 are in contact with each other. It is allowed to swing around the support shaft portions 21, 21.

Further, drive rods 36, 36 are connected to one end portions (the left end portions in FIG. 7) of the trunnions 6, 6 respectively, and drive pistons 37, 37 are provided on the outer peripheral surfaces of the intermediate portions of the drive rods 36, 36. Is fixed. The drive pistons 37, 37 are oil-tightly fitted in the drive hydraulic cylinders 38, 38, 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 the rotation of the output side disk 4 is taken out from the output gear 18.

When changing the rotational speed ratio between the input shaft 15 and the output gear 18, the pair of drive pistons 37,
37 is displaced in opposite directions. As the drive pistons 37, 37 are displaced, the pair of trunnions 6,
6 are displaced in opposite directions, for example, the lower power roller 8 in FIG. 7 is displaced to the right side in FIG. 7, and the upper power roller 8 in FIG. 7 is displaced to the left side in FIG. As a result, the peripheral surfaces 8a, 8a of the power rollers 8, 8 and the inner side surfaces 2a, 4a of the input side disk 2 and the output side disk 4 are described.
The direction of the tangential force acting on the contact portion with and changes. The trunnions 6, 6 are pivotally supported by the support plates 20, 20 according to the change in the direction of the force.
It swings in directions opposite to each other with 5 as the center. As a result,
As shown in FIGS. 4 to 5, the power rollers 8,
The abutting positions of the peripheral surfaces 8a, 8a of 8 and the respective inner side surfaces 2a, 4a change, and the rotation speed ratio between the input shaft 15 and the output gear 18 changes.

In this way, in order to change the rotation speed ratio between the input shaft 15 and the output gear 18, the displacement shafts 7, 7 are
When the inclination angle of is changed, the displacement shafts 7, 7 slightly rotate about the support shaft portions 21, 21.
As a result of this rotation, the outer side surfaces of the outer rings 30, 30 of the thrust ball bearings 26, 26 and the inner side surfaces of the trunnions 6, 6 are relatively displaced. Since the thrust needle bearings 27, 27 are present between the outer side surface and the inner side surface, the force required for this relative displacement is small. Therefore, as described above, a small force is required to change the inclination angles of the displacement shafts 7, 7.

When transmitting the rotational motion from the input side disk 2 to the output side disk 4, the trunnions 6, 6 are connected to the pivot shafts 5, 5 via the power rollers 8, 8. Thrust load is applied in the axial direction. The thrust load applied in this way is the same as the hydraulic cylinder 3
Support by 8 and 38. Incidentally, the hydraulic cylinders 38, 38 for displacing the trunnions 6, 6 in the axial direction of the pivots 5, 5 and supporting the thrust load applied to the trunnions 6, 6 are provided on both sides of each trunnion 6, 6. The structure provided in the above is also conventionally known, for example, as described in Japanese Utility Model Laid-Open No. 62-199562.

Further, in order to increase the power that can be transmitted by the toroidal type continuously variable transmission, it has been conventionally considered to increase the number of power rollers 8, 8. For example, JP-A-3
JP-A-74667 discloses a structure in which three power rollers 8, 8 are provided between an input side disk 2 and an output side disk 4 at equal intervals in the rotation direction. In the case of the structure described in this publication, as shown in FIG. 8, a support piece 40, which is a support member bent at 120 degrees, is provided at three positions on the fixed frame 39 at equal intervals in the circumferential direction. It supports the middle part of 40. The trunnions 6 and 6 are provided between the adjacent support pieces 40 and 40, respectively.
Are supported so as to be swingable and displaceable in the axial direction.

One end of each drive rod 36, 36 is connected to one end of each trunnion 6, 6, and the other end of each drive rod 36, 36 is connected to a drive piston 37, 37 of a hydraulic cylinder 38, 38. Connected to. Each of these hydraulic cylinders 38, 38 has a sleeve 41 and a spool 42 which are respectively displaceable in the axial direction (left and right direction in FIG. 8).
Via a control valve 43 equipped with
It is connected to the discharge port of No. 4.

When changing the inclination angle of the power rollers 8, 8 pivotally supported by the displacement shafts 7, 7 to the trunnions 6, 6, respectively, the sleeve 41 is axially moved by the control motor 45 (see FIG. 8). Left and right). As a result, the pressure oil discharged from the pump 44 is sent to the hydraulic cylinders 38, 38 through hydraulic pipes. As a result, the drive pistons 37, 37 fitted in the hydraulic cylinders 38, 38 are displaced in the same direction with respect to the rotational direction of the input side disc 2 and the output side disc 4 (see FIGS. 4 to 7). In addition, each of the drive pistons 37, 3
The hydraulic oil pushed out from the hydraulic cylinders 38, 38 due to the displacement of 7 is returned to the oil sump 46 through the hydraulic pipe including the control valve 43.

On the other hand, the displacement of the drive piston 37 due to the feeding of the pressure oil causes the spool 4 to move through the link 48.
2 and displaces the spool 42 in the axial direction. As a result, with the drive piston 37 displaced by a predetermined amount, the flow path of the control valve 43 is closed, and the supply and discharge of pressure oil to and from the hydraulic cylinders 38, 38 is stopped. Therefore, the displacement amount of each trunnion 6, 6 in the axial direction, that is, the inclination angle of each power roller 8, 8 is only in accordance with the displacement amount of the sleeve 41 by the motor 45.

[0023]

However, in the case of the conventional toroidal type continuously variable transmission constructed and operated as described above, the number of the power rollers 8 and 8 (or the power rollers 8 and 8).
Since the number of the hydraulic cylinders 38, 38 is twice as many as the number of the hydraulic cylinders 38, the apparatus becomes large in size. For example, when it is used as a transmission for an automobile, it is necessary to install it in a limited space such as under the floor of the automobile or an engine room, and it is necessary to reduce the size as much as possible.

Further, since it is necessary to supply and discharge the pressure oil to and from the plurality of hydraulic cylinders 38 at the same time, it is inevitable that the hydraulic piping becomes complicated. As a result, the production cost of the toroidal type continuously variable transmission is increased in combination with the provision of the plurality of hydraulic cylinders 38. This kind of problem is caused by
The hydraulic cylinders 38, 38 are provided on both sides of each trunnion 6, 6 as in the structure described in Japanese Patent Publication No. 199562, and further, as shown in the above-mentioned Japanese Patent Laid-Open No. 3-74667, the power rollers 8, 8 are provided. It becomes remarkable when the number of is increased.

For example, in the case of the structure described in this publication, a ring portion 49 is provided in the middle of a part of the driving rods 36, and another driving rod 36 is inserted into the ring portion 49 so that they are The drive rods 36, 36 are prevented from interfering with each other. This kind of structure is
It is inevitable that production costs will rise due to complicated assembly work. The toroidal type continuously variable transmission of the present invention was invented in view of such circumstances.

[0026]

The toroidal type continuously variable transmission of the present invention is concentric with each other, with their inner side surfaces facing each other, like the above-described conventional toroidal type continuously variable transmission. First and second discs rotatably supported, support members provided at positions sandwiching the first and second discs, and the first and second discs for pivotally supporting the support members.
A plurality of trunnions that have a pivot in a twisted position with respect to the central axis of the second disk and swing around the pivot, a hydraulic cylinder that displaces the trunnion in the axial direction of the pivot, and the trunnions. And a power roller that is sandwiched between the first and second discs while being rotatably supported around the displacement shaft.

In particular, in the toroidal type continuously variable transmission of the present invention, the hydraulic cylinder has its drive rod connected to one end of one of the plurality of trunnions. Further, one end of a link mechanism is connected to the other end of any one of the trunnions. or,
The other end of this link mechanism is connected to one end of another trunnion. The link mechanism displaces the plurality of trunnions in the same direction with respect to the rotation directions of the first and second disks.

[0028]

The toroidal type continuously variable transmission of the present invention constructed as described above is based on the same action as that of the above-described conventional toroidal type continuously variable transmission, and is based on the operation between the first disk and the second disk. By transmitting the rotational force with, and changing the inclination angle of the trunnion, the rotational speed ratio of these two disks is changed.

In particular, in the case of the toroidal type continuously variable transmission according to the present invention, a plurality of trunnions can be simultaneously displaced in the same direction with respect to the rotational directions of the first and second disks by one hydraulic cylinder. . Therefore, by reducing the number of the hydraulic cylinders and simplifying the hydraulic piping, it is possible to reduce the size and weight of the toroidal continuously variable transmission and simplify the assembling work.

[0030]

FIG. 1 shows, as a first embodiment of the present invention, a structure in which the present invention is applied to a structure in which two power rollers 8 are provided in the circumferential direction. The feature of the present invention is that a plurality of hydraulic cylinders 38 (two hydraulic cylinders in the first embodiment are used.
(1) trunnion 6, 6 is characterized by the portion for displacing the trunnion 6 in the axial direction (left and right direction in FIG. 1), and the structure and action of the other portions are the same as those of the conventional structure shown in FIGS. It is the same. Therefore, illustration and description of the same parts as those of the conventional structure are omitted, and the characteristic parts of the present invention will be mainly described below.

One end (lower end in FIG. 1) of the trunnion 6 is connected to one end (right end in FIG. 1) of the drive rod 36 of the hydraulic cylinder 38. The other end (left end in FIG. 1) of the drive rod 36 is connected to a drive piston 37 fitted in the hydraulic cylinder 38. Therefore, the one trunnion 6 is displaced in the axial direction of the pivots 5 and 5 (left and right direction in FIG. 1) as the pressure oil is supplied to and discharged from the hydraulic cylinder 38.

At the other end of the one trunnion 6 (the right end in FIG. 1), one end of the link mechanism 50 (see FIG. 1) is formed.
(The lower end of) is connected. And this link mechanism 5
The other end of 0 (upper end of FIG. 1) is connected to one end of another trunnion 6 (upper FIG. 1) (right end of FIG. 1).
The link mechanism 50 includes the two trunnions 6, 6
Is displaced in the same direction with respect to the rotation direction of the input side, output side, and both disks 2, 4 (see FIGS. 4 to 7),
Each pair is composed of a transmission rod 51, 51 and a link arm 52, 52, and a connecting rod 53 for connecting both link arms 52, 52.

Of these, the link arms 52, 52 are formed in an L shape and are arranged line-symmetrically to each other. Further, spherical bulges 54, 54 are formed at one end (the left end in FIG. 1) of each of the transmission rods 51, 51.
The ball joints 56 and 56 are formed by fitting the recesses 55 and 55 formed in the axial end surfaces of the trunnions 6 and 6, respectively.

Further, the respective link arms 52, 52 are pivotally supported at their intermediate portions by shafts 57, 57 to a fixed portion in a casing accommodating the toroidal type continuously variable transmission. There is. The other end (right end in FIG. 1) of each transmission rod 51, 51 is swingably connected to one side 58, 58 of each link arm 52, 52. Further, both ends of the connecting rod 53 are swingably connected to the other sides 59, 59 of the link arms 52, 52.

According to the toroidal type continuously variable transmission of the present invention constructed as described above, if the amount of the pressure oil fed into the pressure chamber 60 of the hydraulic cylinder 38 is adjusted, the pair of trunnions 6, 6 can be displaced in the same direction with respect to the rotation direction of the input side, the output side, and both disks 2, 4. For example, when the amount of pressure oil sent into the pressure chamber 60 is increased, the drive rod 36 is pushed rightward in FIG.
The one trunnion 6 to which the end of the drive rod 36 is connected is displaced in the axial direction (rightward in FIG. 1) against the thrust load in the α direction.

When one trunnion 6 is displaced rightward in FIG. 1 in this way, the pair of link arms 52, 52 constituting the link mechanism 50 are rotated about the shafts 57, 57, respectively. Swing clockwise. As a result, the other trunnion 6 is displaced in the axial direction (leftward in FIG. 1) against the thrust load in the arrow β direction.

On the contrary, when the amount of the pressure oil fed into the pressure chamber 60 is reduced, the one trunnion 6 is controlled by the α
1 is displaced to the left in FIG. 1 by the thrust load in the direction, and at the same time, the other trunnion 6 is displaced to the right in FIG. 1 by the thrust load in the direction of the arrow β.

In this way, by changing the amount of pressure oil fed into the pressure chamber 60, the pair of trunnions 6, 6 are
Are displaced in the same direction in the circumferential direction. As a result, the power rollers 8, 8 pivotally supported by the trunnions 6, 6 swing as shown in FIGS. 4 to 5 with the change in the direction of the force applied in the tangential direction as described above. Displacement changes the gear ratio between the input side disc 2 and the output side disc 4.

Next, FIG. 2 shows a second embodiment of the present invention. The present embodiment has a conventional structure shown in FIG. 8, that is, a structure in which three power rollers 8 are provided between the input side disk 2 and the output side disk 4 (see FIGS. 4 to 7). The present invention is applied. That is, the three trunnions 6, 6 pivotally supporting these three power rollers 8, 8
Can be displaced in each axial direction by one hydraulic cylinder 38. Therefore, in the present embodiment, the ends of the trunnions 6, 6 adjacent to each other in the rotational direction of the disks 2, 4 are connected by the two link mechanisms 50a, 50a.
The disks 2 and 4 are connected in series in the rotating direction.

Each of these link mechanisms 50a, 50a is composed of a pair of transmission rods 51a, 51a and one link arm 52a. Then, each transmission rod 51
a, 51a, one end of the ball joint 56a, 56a
The other end of each of the trunnions 6 and 6 is also connected to one end 58a or the other end 59a of the link arm 52a.
In addition, each is pivoted. In the case of the present embodiment, the intersection angle between the one side 58a and the other side 59a is 120 degrees.

As in this embodiment, three power rollers 8 and 8 are used.
In the case where the toroidal type continuously variable transmission is operated, the trunnions 6 and 6 are provided through the power rollers 8 and 8 even when the toroidal continuously variable transmission is provided.
Is applied with a thrust load in the same direction as the rotation direction, that is, in the directions of arrows α, β, and γ in FIG. When changing the transmission ratio of the toroidal type continuously variable transmission, first, the amount of pressure oil sent into the pressure chamber 60 of the hydraulic cylinder 38 is increased,
When the drive rod 36 connecting the drive piston 37 of the hydraulic cylinder 38 and the end of one trunnion 6 is pushed to the right in FIG. 1, one trunnion 6 to which the end of the drive rod 36 is connected is It is displaced in the axial direction (rightward in FIG. 2) against the thrust load in the α direction. Then, the link arms 52 that form the link mechanisms 50a and 50a.
a and 52a swing about the shafts 57 and 57 in the counterclockwise direction in FIG. As a result, the other two trunnions 6, 6 are displaced in the axial direction against the thrust loads in the directions of the arrows β, γ. On the contrary, when the amount of the pressure oil sent into the pressure chamber 60 is decreased, the trunnions 6, 6 are displaced in the α, β, γ directions by the α, β, γ direction thrust loads.

In this way, by changing the amount of pressure oil sent into the pressure chamber 60, the three trunnions 6, 6 are
Are displaced in the same direction in the circumferential direction. As a result, the power rollers 8, 8 pivotally supported by the trunnions 6, 6 swing as shown in FIGS. 4 to 5 with the change in the direction of the force applied in the tangential direction as described above. Displacement changes the gear ratio between the input side disc 2 and the output side disc 4.

Next, FIG. 3 shows a third embodiment of the present invention. Although the first to second embodiments described above use the ball joints 56 and 56a (see FIGS. 1 and 2) to connect the ends of the trunnion 6 and the ends of the transmission rods 51 and 51a. On the contrary, in the case of the present embodiment, the end portion of the trunnion 6 and the transmission rod 51b are provided by the deep groove type ball bearing 61.
Is connected to the end of. That is, the outer ring 62 of the ball bearing 61 is fitted in the concave hole 63 of the end face of the trunnion 6, and one end portion (the left end portion of FIG. 3) of the transmission rod 51b is fitted in the inner ring 64 of the ball bearing 61. ing. Further, the floating shaft 6 is attached to the other end portion (right end portion in FIG. 3) of the transmission rod 51b.
5 is fixed, and the floating shaft 65 is loosely fitted in a long hole 66 formed in one side 58 of the link arm 52b. With this structure, the trunnion 6 is allowed to swing around the pivot 5, and the force can be transmitted between the link arm 52b and the trunnion 6.

[0044]

The toroidal type continuously variable transmission of the present invention is constructed and operates as described above, but the number of hydraulic cylinders is reduced, and the size and weight of the reduced hydraulic cylinders are reduced by the installation space. At the same time, the assembling work can be simplified by simplifying the hydraulic piping. As a result, it is small and lightweight,
It is possible to provide an inexpensive toroidal type continuously variable transmission that can be easily installed in a limited space.

[Brief description of drawings]

FIG. 1 is a partially cut front view showing a first embodiment of the present invention, in which only essential parts are taken out and viewed from the same direction as FIG.

FIG. 2 is a view similar to FIG. 1, showing a second embodiment of the present invention.

FIG. 3 is a view showing a third embodiment of the present invention and corresponding to a portion A in FIG.

FIG. 4 is a side view showing a basic configuration of a conventionally known toroidal type continuously variable transmission in a state of maximum deceleration.

FIG. 5 is a side view showing the same state at maximum acceleration.

FIG. 6 is a sectional view showing an example of a conventional specific structure.

7 is a sectional view taken along line BB of FIG.

FIG. 8 is a front view of a main part showing another example of the conventional structure in a partially cut state.

[Explanation of symbols]

 1 Input Shaft 2 Input Side Disk (First Disk) 2a Inner Side Surface 3 Output Shaft 4 Output Side Disk (Second Disk) 4a Inner Side Surface 5 Axis 6 Trunnion 7 Displacement Axis 8 Power Roller 8a Circumferential Surface 9 Pressing Device 10 Cam Plate 11 Cage 12 Roller 13, 14 Cam surface 15 Input shaft 16 Needle bearing 17 Collar part 18 Output gear 19 Key 20 Support plate 21 Support shaft part 22 Pivot shaft part 23 Circular hole 24, 25 Radial needle bearing 26 Thrust ball bearing 27 Thrust needle bearing 28 Cage 29 Ball 30 Outer ring 31 Race 32 Cage 33 Needle 36 Drive rod 37 Drive piston 38 Hydraulic cylinder 39 Frame 40 Support piece 41 Sleeve 42 Spool 43 Control valve 44 Pump 45 Control motor 46 Oil sump 47 Cam 48 Link 49 Ring part 50, 0a link mechanism 51, 51a, 51b transmission rod 52, 52a, 52b link arm 53 connecting rod 54 bulging portion 55 recessed portion 56, 56a ball joint 57 shaft 58, 58a one side 59, 59a other side 60 pressure chamber 61 ball Bearing 62 Outer ring 63 Recessed hole 64 Inner ring 65 Floating shaft 66 Long hole

Claims (1)

[Claims] 1. In a state in which the inner surfaces of each other are opposed to each other,
First and second disks that are concentrically and rotatably supported, support members provided at positions sandwiching the first and second disks, and the first and second disks for pivotally supporting the support members. A plurality of trunnions each having a pivot in a twisted position with respect to the central axis of the second disk and swinging about the pivot; a hydraulic cylinder for displacing the trunnion in the axial direction of the pivot; A toroidal type including a displacement shaft projecting from the inner surface of each trunnion and a power roller sandwiched between the first and second disks while being supported rotatably around the displacement shaft. In the continuously variable transmission, the hydraulic cylinder has its drive rod connected to one end of one trunnion of the plurality of trunnions, and the other end of the one trunnion. A link machine Of the link mechanism, the other end of the link mechanism is connected to one end of another trunnion, the link mechanism, the link mechanism, with respect to the rotation direction of the first and second disks A toroidal-type continuously variable transmission characterized by displacing the trunnion in the same direction.