JP2006038131A - Toroidal continuously variable transmission - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To reduce loading hysteresis of hindering pressing force, in a toroidal continuously variable transmission having a toroidal transmission unit composed of input-output discs oppositely arranged on the same axis and a power roller for transmitting traction between these input-output discs, and provided with a loading mechanism for applying the pressing force between the input-output discs for interposingly pressing this power roller. <P>SOLUTION: A ball 24 being a smoothing mechanism for reducing frictional force in the axial O<SB>1</SB>direction such as the ball 24 and a needle 25, is arranged in a rotational engaging part of a cam disc 3 and an input shaft 1. <P>COPYRIGHT: (C)2006,JPO&NCIPI

Description

  The present invention provides a pressing force for increasing the transmission torque when the loading mechanism of the toroidal-type continuously variable transmission presses the input disk against the power roller to clamp the power roller between the input disk and the output disk. The present invention relates to a technique for reducing so-called loading hysteresis, which is different from the pressing force when the transmission torque is reduced.

In the toroidal continuously variable transmission, an input disk and an output disk having a traction transmission surface recessed in an arc shape are coaxially opposed to each other, and a power roller is rotatably provided between the opposed concave curved surfaces. When the outer periphery of the disk contacts the traction transmission surface of the input disk and the traction transmission surface of the output disk, the rotation and torque of the input disk drivingly coupled to the engine side are transmitted to the output disk drivingly coupled to the driving wheel side. Do. Then, during the speed change, the speed change control is performed steplessly by continuously changing the inclination angle of the rotating shaft of the power roller.
Here, in order for the power roller to transmit torque, it is important to sandwich the power roller between the input / output disks so that the friction between the input / output disks and the power roller is not lost. For this purpose, a loading mechanism is provided to apply thrust (axial force) to the input disk and pinch the power roller with a pressing force necessary for torque transmission.

As an invention relating to a loading mechanism of a toroidal-type continuously variable transmission, there is conventionally known an invention as described in Patent Document 1, for example.
In a so-called double-cavity toroidal continuously variable transmission that includes two toroidal transmission units each composed of an input / output disk and a power roller, and each output disk is coaxially arranged so that they are back to back. There is an advantage that the thrust is canceled by the input disk being pressed against each other, and a stress load is not applied to the transmission case or the like. Therefore, this loading mechanism is generally provided in a double cavity type toroidal continuously variable transmission.

  This case will be described with reference to FIG. 1. A disk-shaped pressing disk (a disk-shaped pressing disk) is interposed between an input shaft 1 extending from the engine side and an input disk 8 which is a rotating element of a double cavity type toroidal continuously variable transmission. (Also called a cam disk) 3 and a loading mechanism 5 for generating thrust interposed between the pressing disk 3 and the back surface of the input disk 8.

  As a result, the input disk 8 clamps a power roller (not shown) between the input disk 8 and the output disk 13, and the pressing disk 3 clamps a power roller (not shown) between the input disk 12 and the output disk 14 by the CVT shaft 11.

The loading mechanism 5 can generate a thrust corresponding to the magnitude of torque input from the input shaft 1.
At the same time, the pressing disk 3 transmits rotational torque between the input shaft 1 and the loading mechanism 5 and also transmits rotational torque between the input shaft 1 and the other input disk 12 via the CVT shaft 11. The cam roller 5 transmits rotational torque between the pressing disk 3 and one input disk 8.

The loading mechanism 5 described above generally uses a cam roller, but other than this, a mechanism using a hydraulic piston and a cylinder may be used.
Japanese Patent Application Laid-Open No. 11-118009

However, the conventional toroidal continuously variable transmission has the following problems. In other words, the thrust disk 3 and the input disk 8 move relative to _{each other in the} direction of the rotation axis O ₁ of the input shaft 1 at the same time as the thrust corresponding to the transmission torque is generated.
At this time, the pressing disk 3 approaches the input shaft 1 when the transmission torque is increased, moves away from the input shaft 1 while the transmission torque is decreasing, or moves relatively, so that the engaging portion between the input shaft 1 and the pressing disk 3 direction of friction that resists the relative movement of the rotation axis O ₁ direction occurs. Such friction is caused by the generation of pressing force necessary for torque transmission in both the single cavity toroidal continuously variable transmission including one toroidal transmission unit and the double cavity toroidal continuously variable transmission. Is not preferable.

In addition, in a double-cavity toroidal continuously variable transmission, such friction causes so-called loading hysteresis in which the pressing force when increasing the transmission torque and the pressing force when decreasing the transmission torque are different. Let
The loading hysteresis will be described. As shown in FIG. 1, when the transmission torque is increased, for example, the plurality of cam rollers 5 generate 100 thrust, and if this friction is 10, the pressing force applied to the input disk 12 by the CVT shaft 11 Is subtracted 90.
As described above, when the torque input from the input shaft 1 to the input disk 12 is increased by the friction of the engaging portion between the input shaft 1 and the pressing disk 3, torque transmission by pinching pressure is performed as shown in the graph of FIG. Since the pressing force B is smaller than the necessary pressing force A required for the rotation, and the pressing force C is larger than the necessary pressing A when the torque is reduced, the loading surrounded by the pressing forces B and C is generated. Hysteresis occurs. Since the pressing force must always exceed the required pressing force A, in the loading mechanism in which the loading hysteresis exists, the thrust given by the loading mechanism needs to be raised like D, and the required pressing force A needs to be greatly exceeded. It was.

  Therefore, by applying the thrust as described above, the load applied to each component such as the pressing disk 3 and the CVT shaft 11 in the toroidal-type continuously variable transmission and the rotating elements such as the input / output disks 8 and 13 and the power roller. As a result, the durability of each component was adversely affected.

  In view of the above-described circumstances, the present invention provides a toroidal continuously variable transmission that can reduce the friction generated at the engaging portion between the input shaft and the loading mechanism and reduce the need to add the thrust generated by the loading mechanism. The purpose is to propose.

For this purpose, the toroidal continuously variable transmission according to the present invention is as described in claim 1.
Provided with a toroidal transmission unit consisting of an input / output disk arranged coaxially and a power roller that performs traction transmission between these input / output disks,
On the back surface of the input disk opposite to the toroidal transmission surface, a pressing disk that is rotationally engaged so as to be axially displaceable with respect to the input shaft is disposed coaxially,
Power is transmitted between the pressing disk and the input disk between the pressing disk and the input disk, and a thrust corresponding to the transmission torque is generated between the pressing disk and the input disk, thereby causing power in the direction of mutual approach between the input and output disks. In a toroidal continuously variable transmission with a loading mechanism that applies roller clamping pressure,
A smooth mechanism for reducing a frictional force at the time of relative displacement in the axial direction is provided in a rotationally engaging portion that can be displaced in the axial direction between the input shaft and the pressing disk.

According to such a configuration of the present invention, by providing a smooth mechanism at the engaging portion between the input shaft and the pressing disk, the frictional force in the direction of the rotation axis O ₁ generated at the rotating engaging portion is reduced, and the loading hysteresis is reduced. Can be reduced,
In order to always ensure the necessary pressing force A, it is not necessary to add a decrease due to the loading hysteresis to the thrust provided by the loading mechanism to greatly exceed the necessary pressing force A.
Therefore, the load on each part such as the pressing disk 3 and the CVT shaft 11 in the toroidal-type continuously variable transmission and the rotating elements such as the input / output disks 8, 12, 13, 14 and the power roller is reduced, and the durability of each part is reduced. Can improve sex.

Hereinafter, embodiments of the present invention will be described in detail based on examples shown in the drawings.
FIG. 1 is a longitudinal side view showing a double cavity toroidal continuously variable transmission according to an embodiment of the present invention.
The input shaft 1 for inputting engine torque and engine rotation to the toroidal-type continuously variable transmission is connected to the cam disk 3 which is a pressing disk at the front end inside the toroidal-type continuously variable transmission. To do.
Therefore, the distal end of the input shaft 1, a plurality of pawls 1t projecting in the axial direction O ₁ of the input shaft 1, it is arranged in the circumferential direction of rotation. On the other hand, among the surfaces of the cam disc 3 disc-shaped, in the front surface closer viewed from the input shaft 1, a plurality of pawls 3t projecting axially O _1, it is arranged in the circumferential direction of rotation. Then, the claw 1t and the claw 3t are rotationally engaged with each other.

Of the surface of the disc-shaped cam disk 3 arranged coaxially with the input disk 8, the back surface 6 far from the input shaft 1 is formed with a cam surface 7 in which irregularities are arranged in the rotational circumferential direction. A similar cam surface 10 is also formed on the rear surface 9 of the front input disk 8 facing the rear surface 6. The cam surface 7 and the cam surface 10 extend a plurality of cam rollers 5 constituting a later-described loading cam mechanism (also referred to as a loading mechanism) in a direction (radial direction) perpendicular to the rotational axis O ₁ of the input shaft 1. It is pinched so as to be rotatable about the axis to be rotated.

The cam disk 3 is drivingly coupled to the input disk 8 through the cam roller 5 as described later. The cam disk 3 are drivably connected to as described below the input disk 12 through the CVT shaft 11 extending in the rotation axis O ₁ direction.

  Each of the input disks 8 and 12 is a part of a so-called double cavity type toroidal continuously variable transmission in which two toroidal transmission units (a front side toroidal transmission unit 15 and a rear side toroidal transmission unit 16) are accommodated coaxially. Make.

  These two toroidal transmission units 15 and 16 are respectively provided with the above-described input disks 8 and 12, output disks 13 and 14 disposed coaxially and opposed thereto, and a power roller (not shown) interposed between the opposed input and output disks. And more.

As shown in FIG. 1, the front side toroidal transmission unit 15 and the rear side toroidal transmission unit 16 are arranged coaxially so that the output disks 13 and 14 are back to back, and in this arrangement, the CVT shaft 11 is rotatably supported. The input / output disks 8 and 12 to 14 of the toroidal transmission units 15 and 16 are rotatably supported on the CVT shaft 11.
The input disks 8 and 12 arranged at both ends are respectively slidably engaged with the CVT shaft 11 by the ball spline 17 but can be slid in the direction of the axis O _{1. The} input disk 12 is screwed into the CVT shaft 11 and loaded with a loading nut 18. To prevent it from coming off via the disc spring 19.
The output disks 13 and 14 are integrally coupled to each other via a hollow output shaft 20 and the hollow output shaft 20 is rotatably supported on the CVT shaft 11.

An arc-shaped concave curved surface is formed on both sides of the axis O _{1 on} the input disk 8, and a similar concave curved surface is formed on the output disk 13 facing the input disk 8. A power roller (not shown) is disposed between these concave curved surfaces. An extremely thin oil film is formed on the concave curved surface. The power roller is clamped between the input / output disks so as to obtain the necessary friction by shearing the oil film between the corresponding input / output disks to transmit torque, and sandwich the rotation axis O ₁ of the input / output disks. Opposing to both sides.
The cam roller 5, which is a thrust generating portion of the loading cam mechanism, receives the input disks 8 and 12 as described later so that torque can be transmitted by obtaining necessary friction on the concave curved traction transmission surface and the contact surface of the power roller. Press on.

  As shown in FIG. 1, an output gear 21 is provided between output disks 13 and 14 arranged back to back with each other, and this is integrally formed on the outer periphery of the hollow output shaft 20 to form a toroidal continuously variable transmission (output). The shifting power from the disks 13, 14) is taken out from the output gear 21 via the counter gear 22.

In FIG. 1, transmission input rotation transmitted from the input shaft 1 is transmitted to the input disks 8 and 12 of both toroidal transmission units 15 and 16 via the cam disk 3.
That is, the cam disk 3 transmits the input rotation and torque to the front side input disk 8 via the cam roller 5 and to the rear side input disk 12 via the CVT shaft 11.

At the same time the cam roller 5, and biased toward the output disc 13 an input disc 8 generates a thrust in accordance with the transmission torque by cam action (pressing force in the axial O ₁ direction), the cam disc 3 a reaction force at this time, By transmitting to the input disk 12 through the CVT shaft 11, the loading nut 18 and the disc spring 20, the input disk 12 is biased toward the output disk 14.
Therefore, the power roller is clamped between the corresponding input / output disks with a pressing force corresponding to the transmission torque, and the power can be transmitted between the corresponding input / output disks.

In addition to the cam action of the cam roller 5, when a transmission torque is applied to the input shaft 1 and the input shaft 1 rotates, the cam disk 3 that is drivingly coupled to the input shaft 1 also rotates. When the cam surface 7 of the cam disk 3 and the cam surface 10 of the input disk 8 are displaced so as to be twisted in the circumferential direction, rolling elements (not shown) provided in the plurality of cam rollers 5 stand in the direction of the axis O _1. Then, the input disk 8 is pressed toward the output disk, and the cam disk 3 is pressed toward the rotating shaft 1.
This pressing force is proportional to the magnitude of the transmission torque. That is, as the transmission torque increases, the relative twist increases and the pressing force increases.

  Therefore, even when the transmission torque increases or conversely when the transmission torque decreases, the cam roller 5 has a large transmission torque on the contact surface between the input / output disks 8, 12-14 and the power roller. Torque is transmitted by applying a pressing force according to the height.

FIG. 2 is a longitudinal side view showing a smooth mechanism provided between the input shaft 1 and the cam disk 3. A ball 24 is provided on the engagement surface 2 that actually transmits torque between the claw 1t and the claw 3t. The outer peripheral portion of the axis O ₁ viewed from Te pawl 1t is located inward of the inner periphery of the pawl 3t, ball 24 is accommodated in the pawl 1t and nail 3t, the movement of direction perpendicular to the axis O ₁ is regulated but it is the, it is possible to roll in the axial O ₁ direction, functions as a ball spline of reducing the axis O ₁ direction friction generated engagement surface 2.
Therefore, it becomes possible to reduce the above-mentioned loading hysteresis, and to reduce the load applied to each component in the toroidal continuously variable transmission by reducing the amount of addition (slashed line) of the conventional pressing force in FIG. Can do.

FIG. 3 is a longitudinal sectional side view showing a smooth mechanism according to another embodiment provided between the input shaft 1 and the cam disk 3. In this embodiment, the needle 25 is provided on the engagement surface 2. The needle 25 is accommodated in between the nail 1t and nail 3t, are arranged in parallel to the axis O ₁ direction, the to the axis O ₁ direction perpendicular their axis of rotation. Thus, perform a bearing function of reducing the axis O ₁ direction friction generated engagement surface 2.
Therefore, it becomes possible to reduce the above-mentioned loading hysteresis, and to reduce the load applied to each component in the toroidal continuously variable transmission by reducing the amount of addition (slashed line) of the conventional pressing force in FIG. Can do.
Further, while the ball 24 receives the transmission torque by point contact, the needle 25 of this embodiment receives the transmission torque by line contact. Therefore, the stress applied to the engaging portion is suppressed to a low surface pressure, and the claw 1t. In addition, the burden on the claw 3t can be reduced and the durability can be maintained high.

FIG. 4 is a front view showing a state in which the needle 25 of the present embodiment is provided on the engaging surfaces 2 on both sides that are present across the claw 1t. The distal end of the input shaft 1 that faces the cam disc 3, in the circumferential direction around the axis O _1, erected nails 1t of six. On the other hand, the cam disk 3 is provided with six engagement holes 26 between adjacent claws 3t erected in the circumferential direction around the axis O ₁ , and the input shaft 1 of the input shaft 1 is inserted into these engagement holes 26. The claws 1t are engaged with each other.
Of the side surfaces that define the engagement hole 26, the surface perpendicular to the circumferential direction is the engagement surface 2 that transmits torque to and from the claw 1t.
That is, the engagement surfaces 2 are on both sides of the claw 1t in the circumferential direction, and when transmitting positive torque such as during driving, the claw 1t pushes the claw 3t in the circumferential direction on one of the engagement surfaces 2, thereby Take 3 around. Further, when transmitting reverse torque, such as during coasting or engine braking, the other engaging surface 2 exerts a force that pushes in the circumferential direction between the claw 1t and the claw 3t.

Needles 25 are provided on the engagement surfaces 2 between the claw 1t and the claw 3t, respectively.
As a result, the frictional force in the direction of the axis O ₁ is reduced both when transmitting the positive torque and when transmitting the reverse torque, and as shown by the solid line in the graph of FIG. (Hatched lines) can be reduced.

5 to 7 show a retainer 27 for holding the needle 25, FIG. 5 is an enlarged side view showing the needle 25 in FIG. 3, and FIG. 6 is an enlarged front view showing the claw 1t in FIG. FIG. 7 is a partial cross-sectional view of the state seen from the outside in the direction perpendicular to the axis O ₁ .
Referring to FIG. 5, the retainer 27 has a plurality of rectangular holes 28 for accommodating the needles 25. In this embodiment, there are three rectangular holes. The rectangular hole 28 has substantially the same size as the cross-section of the needle 25 passing through its rotational axis, and the needles 25 are held in parallel with each other in the direction of the axis O _1. This prevents the shift.

On the inner peripheral side and the outer peripheral side of the claw 1t, the bracket 29 integrally couples the retainers 27 provided on the engaging surfaces 2 on both sides in the circumferential direction with the claw 1t interposed therebetween. That is, among the peripheral edges of the retainer 27, the inner edges in the perpendicular direction of the axis O _{1 on} the radially inner peripheral side are coupled to each other by the bracket 29 laid so as to straddle the inner peripheral side of the claw 1 t. Of the periphery of the retainer 27, the perpendicular direction outer edge between the axis O ₁ in the radial direction outer peripheral side, are bonded to each other with a bracket 29 which is bridged so as to cross the outer peripheral side of the claw 1t. Therefore, as shown in FIG. 6, the retainer 27 and the bracket 29 have a “mouth shape” when viewed from the front, and the claw 1 t passes through the central opening.

When the needle 25 performs the rolling motion, the retainer 27 can prevent the rolling resistance from being generated by tilting the individual rotation shafts of the needle 25.
Further, when the input shaft 1 and the cam disk 3 rotate, a centrifugal force acts on the needle 25 that rotates together with the input shaft 1 and the needle 25 tends to escape outward in the direction perpendicular to the axis O ₁ . The retainer 27 also has a function of preventing such disconnection. That is, the bracket 29 for straddling the nail 1t, it is possible to prevent the needles 25 held by the retainer 27 and the retainer 27 is shifted in a right angle outwardly of the axis O _1.
In order to resist the centrifugal force, even if only the inner peripheral bracket 29 is provided among the brackets 29 provided on the inner peripheral side and the outer peripheral side of the claw 1t shown in FIG. Can be played.

Both ends of the bracket 29 are extended until they come into contact with the claw 3t, and the extension portion 30 is protruded from the retainer 27 in the circumferential direction.
When the rotary shaft 1 repeats input of the positive torque and the reverse torque, the retainer 27 is displaced in the circumferential direction between the claw 1t and the claw 3t. Therefore, if no countermeasure is taken, the rotation axis of the needle 25 is inclined.
Providing the extension 30 prevents the retainer 27 from shifting in the circumferential direction and prevents the rotation axis of the needle 25 from tilting.

By the way, according to the above-described embodiment, the cam disk 3 and the input shaft 1 are engaged so as to transmit the rotational torque while allowing relative movement in the direction of the axis O ₁ , and the balls 24 are engaged with these engaging portions. and the needle 25 and the like axis O ₁ direction of the frictional force from the provision of the smooth mechanism to reduce,
A rolling element (not shown) in the cam roller 5 can stand up in the direction of the axis O1 without being interrupted by the frictional force during torque transmission, and can generate a thrust corresponding to the transmission torque.
Therefore, the generation of the pressing force required for torque transmission is not obstructed, and the loading cam mechanism comprising the cam roller 5 can be a double cavity type toroidal type continuously variable transmission, even if it is a single cavity type toroidal type continuously variable transmission. Even a transmission can provide a necessary and sufficient pressing force to the toroidal transmission unit.

Further, in the double cavity type toroidal type continuously variable transmission according to the above-described embodiment, as shown in FIG. 9B, the pressing force of the input disk 12 is reduced when the cam roller 5 generates thrust. Loading hysteresis can be reduced.
Therefore, it is not necessary to add the decrease due to the loading hysteresis as in the prior art and to greatly exceed the required pressing force A, so that each component such as the cam disk 3, the CVT shaft 11 and the variator, and the input / output disks 8, 13 to 15 and The burden on rotating elements such as power rollers can be reduced, and the durability of each component can be improved.

  Further, in another embodiment described above, since the needle 25 functioning as a smooth mechanism receives the transmission torque by line contact, the stress acting on the engaging portion is suppressed to a low surface pressure, and the load on the claw 1t and the claw 3t is reduced. Can be reduced, and durability can be maintained high.

In addition, according to the above-described embodiment, when the input shaft 1 and the toroidal continuously variable transmission are drive-coupled, the plurality of claws 1t are provided in the circumferential direction at the tip of the input shaft 1 to provide a toroidal continuously variable transmission. A plurality of claws 3t are arranged in the circumferential direction on the cam disk 3 of the machine, and these are engaged. The claw 1t can transmit the rotational torque by pushing the claw 3t in the circumferential direction with the engagement surface 2 that is a surface perpendicular to the circumferential direction, and the axis line between the claw 1t and the claw 3t when the rotational torque is transmitted. O ₁ allows the direction of the relative movement.

In this case, the engagement surface 2 which generates a frictional force of the axis O ₁ direction during transmission of positive torque, the engagement surface 2 which generates a frictional force of the axis O ₁ direction during transmission of reverse torque, the circumferential nails 1t Since it is on both sides in the direction, the needles 25 are provided on both sides in the circumferential direction of the claw 1t as shown in FIG.
And since the retainer 27 holding the needle 25 is also provided on both sides in the circumferential direction, the retainer 27 is coupled to each other by a bracket 29 constructed so as to straddle the claw 1t.
The retainer 27 prevents the rolling axis from being caused by tilting of the individual rotation shafts of the needle 25, and
The bracket 29 can prevent the centrifugal force from acting on the needle 25 to prevent the needle 25 from slipping outward in the direction perpendicular to the axis O ₁ together with the retainer 27.
As in the present embodiment, the retainer 27 provided on the engagement surfaces 2 on both sides in the circumferential direction with the claw 1t interposed therebetween.
Are connected to each other between the radially outer edges far from the axis O ₁ and between the radially inner edges close to the axis O ₁ by the bracket 29, either between the radially outer edges or between the radially inner edges. In this case, they may be combined with each other.

When transmission of positive torque and reverse torque between the rotating shaft 1 and the cam disk 3 is repeated, the retainer 27 is displaced in the circumferential direction. Therefore, if no countermeasure is taken, the rotating axis of the needle 25 is inclined and rolling resistance is generated.
Therefore, in the above-described embodiment, both ends of the bracket 29 that couples the retainer 27 between the radially inner edges are extended until they come into contact with the claw 1t, and the extension 30 is projected in the circumferential direction. Providing the extension 30 prevents the retainer 27 from shifting in the circumferential direction and prevents the rotation axis of the needle 25 from tilting.
In addition to the present embodiment, it is needless to say that the same effect can be obtained by extending both ends of the bracket 29 for connecting the retainer 27 between the radially outer edges in the same manner.

It is a vertical side view which shows the double cavity type toroidal type continuously variable transmission which becomes one Example of this invention. It is a longitudinal cross-sectional view which expands and shows the engaging part between the input shaft and cam disk of the Example. It is a longitudinal cross-sectional view which expands and shows the double cavity type toroidal type continuously variable transmission which becomes the other Example of this invention by the engaging part between an input shaft and a cam disk. The the engaging portion is a front view showing as viewed in the axial line O ₁ direction. It is a side view which shows the retainer holding the needle provided in the engaging part. It is a front view which shows the needle and retainer which were provided in the engaging part. It is a top view which shows the needle and retainer which were provided in the engaging part in a partial cross section. It is a characteristic view which shows the relationship between the transmission torque input into the input disk of the Example, and the pressing force given between input-output disks compared with a prior art example. In the conventional double cavity type toroidal-type continuously variable transmission, it is a characteristic view which shows the relationship between the transmission torque input into an input disk, and the pressing force given between input-output disks.

Explanation of symbols

1 Input shaft 1t claw 2 Engagement surface 3 Cam disc 3t Claw 5 Cam roller
8 Input disk 11 CVT shaft 12, 13 Output disk 14 Input disk 15 Front side toroidal transmission unit 16 Rear side toroidal transmission unit 20 Hollow output shaft 21 Output gear 22 Counter gear 24 Ball 25 Needle 27 Retainer 29 Bracket 30 Extension

Claims (6)

Provided with a toroidal transmission unit consisting of an input / output disk arranged coaxially and a power roller that performs traction transmission between these input / output disks,
On the back surface of the input disk opposite to the toroidal transmission surface, a pressing disk that is rotationally engaged so as to be axially displaceable with respect to the input shaft is disposed coaxially,
Power is transmitted between the pressing disk and the input disk between the pressing disk and the input disk, and a thrust corresponding to the transmission torque is generated between the pressing disk and the input disk, thereby causing power in the direction of mutual approach between the input and output disks. In a toroidal continuously variable transmission with a loading mechanism that applies roller clamping pressure,
A toroidal-type continuously variable transmission characterized in that a smooth mechanism for reducing frictional force at the time of axial relative displacement is provided in a rotationally engaging portion that is axially displaceable between the input shaft and the pressing disk. The toroidal continuously variable transmission according to claim 1,
Provided as a set of two toroidal transmission units, these toroidal transmission units are arranged coaxially so that the output disks are back-to-back, and the input disks are rotationally engaged so as to be axially displaceable.
On the back of the input disk of one toroidal transmission unit, a pressing disk that is rotationally engaged so as to be axially displaceable with respect to the input shaft is disposed coaxially,
Power is transmitted between the pressure disk and the input disk between the pressure disk and the input disk, and a thrust corresponding to the transmission torque is generated between the pressure disk and the input disk so that the input / output disks of the two toroidal transmission units are mutually connected. A toroidal-type continuously variable transmission characterized by interposing a loading mechanism for applying a power roller clamping pressure in the approaching direction. The toroidal type continuously variable transmission according to claim 1 or 2,
A toroidal-type continuously variable transmission characterized in that the axial engagement between the pressing disk and the input shaft can be relatively displaced by a ball spline, and the ball spline ball is also used as the smooth mechanism. . In the toroidal continuously variable transmission according to claim 1 or 2,
The rotation direction of the claw projecting in the axial direction so that the rotational engagement between the pressing disk and the input shaft is relatively displaceable in the axial direction is engaged with the pressing disk and the input shaft in the rotational direction. A toroidal-type continuously variable transmission characterized in that the smooth mechanism is constituted by needles that are interengaged and interposed between the mutual engagement surfaces of the claws in the rotational direction. The toroidal type continuously variable transmission according to claim 4,
Of the rotation direction mutual engagement surfaces of the claws, both between the rotation direction mutual engagement surfaces engaged during transmission of positive torque and between the rotation direction mutual engagement surfaces engaged during transmission of reverse torque. And interposing the needle
A retainer for holding a needle interposed between the positive direction torque transmitting rotationally engaging surfaces and a retainer for holding the needle interposed between the reverse torque transmitting rotating direction mutually engaging surfaces, It is characterized by being coupled to each other between the radially outer edges far from the shaft, between the radially inner edges close to the input shaft, or both between these radially outer edges and between the radially inner edges. Toroidal continuously variable transmission. The toroidal-type continuously variable transmission according to claim 5,
The both retainers are extended to contact with the corresponding claws at both ends of the inter-retainer coupling portion for coupling between the radially outer edges of the both retainers and / or the inter-retainer coupling portion for coupling between the radially inner edges. A toroidal-type continuously variable transmission, characterized in that an extension for restricting the position of the input shaft in the direction of rotation of the input shaft is provided.

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