JPH10213201A - Toroidal continuously variable transmission - Google Patents

Abstract

PROBLEM TO BE SOLVED: To reduce the space in a toroidal continuously variable transmission while matching the inclinations of the power rollers of plural toroidal transmission units. SOLUTION: This toroidal continuously variable transmission is constituted of a pair of power rollers arranged face to face between plural input/output cone disks, trunnion 3a∼3d rotably supporting the power rollers and displaceable around the axis and in axial direction. A synchronized means connecting the trunnion 3a∼3d in the rotating direction and matching the inclinations of the power rollers, pinion 6 formed on the trunnion 3a∼3d, rods 7a, 7b having rack 8 meshing in the same speed change direction with the pinion 6 of the opposite trunnion 3a∼3d and the rods 7a, 7d having the rack 8 meshed with the adjacent trunnion 3a, 3c in the same speed change direction.

Description

DETAILED DESCRIPTION OF THE INVENTION

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to an improvement of a toroidal type continuously variable transmission, and more particularly to a double cavity type having a large number of power rollers.

[0002]

2. Description of the Related Art As shown in FIG. 5, a toroidal type continuously variable transmission used in a vehicle is provided with two sets of toroidal transmission units 10 and 11 so as to increase the transmission torque. 2. Description of the Related Art A continuously variable transmission is conventionally known, and a pair of power rollers 4 and a pair of power rollers 4,
4 and the power roller 4 and the input cone disk 1
The gear ratio is continuously changed by continuously changing the ratio of the contact radii of the output cone disks a and 1b and the output cone disks 2a and 2b.

[0005] In FIG. 5, two sets of toroidal transmission units 10 and 11 are provided with respective input cone disks 1.
a, 1b and the power rollers 4 held and pressed by the output cone disks 2a, 2b are supported by trunnions 3a to 3d which can be displaced around the axis and in the axial direction as shown in FIG. By synchronizing the rotation around the 3d axis, all the power rollers 4 transmit power at the same speed ratio. FIG. 6 shows a cross section of the trunnion 3a of the toroidal transmission unit 10, and the other trunnions 3b to 3c have the same configuration.

The trunnion 3a has a rotating shaft C at the upper and lower ends.
1, the rotary shaft portions 30, 30 are coaxial with each other, and between these rotary shaft portions 30, 30 there is formed an offset portion 31 projecting in the outer peripheral direction of the input / output cone disk to accommodate the power roller 4. Is done.

The power roller 4 is supported by a pivot shaft 5 eccentric by a predetermined amount. The pivot shaft 5 has its base end at the offset portion 3 of the trunnion 3a.
Supported by 1.

The trunnion 3a is supported so as to be displaceable in and around the rotation axis C1.
A rod 32 is connected to the rotation shaft 30 at the lower end of the a.
An actuator (not shown) connected to the rod 32 drives the trunnion 3a in the axial direction of the rotation axis C1, whereby the power roller 4 rotates around the rotation axis C1 (hereinafter, referred to as the rotation axis C1).
The contact radius between the input cone disk 1a and the output cone disk 2a changes to continuously change the gear ratio, and the driving force from the input shaft 20 changes the tilt angle of the power roller 4 (rotational shaft C1). Output gear 2 according to the rotation angle around
1 is transmitted.

Here, the toroidal transmission units 10, 1
1, the trunnions 3a and 3b opposed to each other with the input shaft 20 interposed therebetween are arranged so that the rotating shaft portions 30 on the upper end sides are spherical bearings as shown in FIG. 42 and upper link 4
3, the rotating shaft portions 30 on the lower end side are also connected to each other via the spherical bearing 42 and the lower link 44, and the thrust force applied to the power rollers 4, 4 (to the left in FIG. 6). Force), the distance between the rotation axes C1, C1 of the trunnions 3a, 3b is kept constant.

A large number of power rollers 4 need to make the tilt angles of the power rollers 4 coincide with each other, and each of the trunnions 3a to 3d rotates as disclosed in Japanese Utility Model Publication No. 4-52512. Trunnions 3a to 3d via wires or the like so that the displacement amount around the axis C1 = the tilt angle matches.
Are connected to each other in the direction of rotation of.

As shown in FIG. 6, a pulley 9 provided on a rotating shaft 30 below each of the trunnions 3a to 3d in FIG.
0, the wires 91 to 93 are wound around as shown in FIG. 7 to synchronize the rotation angles of all the trunnions 3a to 3d. In each of the toroidal transmission portions 10, 11, the opposing trunnions 3a, 3b, and 3c are respectively provided. 3d are connected to each other by wires 91, 93, and opposing power rollers 4, 4
In order to match the gear ratios set in the above, the opposing trunnions are connected so as to rotate in opposite directions (the same gear direction).

Then, two sets of toroidal transmission units 1
0 and 11 are connected via a wire 92 so that the trunnions 3a and 3c rotate in opposite directions to each other.

Each of the trunnions 3a is connected with the wires 91 to 93.
3d are connected in the rotational direction, and the tilt angles of the many power rollers 4 are matched.

Although not shown, the wires 91 to 91 are not shown.
Instead of the above-described conventional example, the above-described conventional example also discloses a configuration in which opposing trunnions are meshed with gears and the trunnions of the toroidal transmission units are synchronized with each other via rods.

[0013]

However, in the above-mentioned conventional toroidal-type continuously variable transmission, the tilt angles of the power rollers 4 of the plurality of toroidal transmission units 10 and 11 are synchronized by wires 91 to 93. Therefore, if the wires 91 to 93 are loosened due to aging or the like, the tilt angles of the power rollers 4 may not match, and there is a problem that the shifting operation cannot be performed smoothly. When the power roller is connected by a gear and a rod, the outer diameter of the gear meshing the opposing trunnions needs to be set according to the interval between the trunnions, and the opposing trunnions 3a, 3
Since the axial displacements of b, 3c and 3d are in the axial direction of the rotation axis C1 and in mutually opposite directions, the rod connecting the adjacent toroidal transmission units also responds to the axial displacement of the connecting trunnion. Since space is required, a space for securing the displacement of the rod and a space for accommodating a gear with a large outer diameter that connects the opposing trunnions are required inside the continuously variable transmission. However, there is a problem that the size and weight of the camera are hindered.

SUMMARY OF THE INVENTION The present invention has been made in view of the above-mentioned problems, and it is possible to reduce the space in a continuously variable transmission while ensuring that the tilt angles of the power rollers of a plurality of toroidal transmission units are matched. The purpose is to promote miniaturization and weight reduction.

[0015]

According to a first aspect of the present invention, there is provided a pair of power rollers which are disposed oppositely between a plurality of input / output cone disks arranged coaxially and which are held between the input / output cone disks. And a trunnion that can be displaced around the axis and in the axial direction while rotatably supporting each of the power rollers, and a synchronization unit that connects the trunnions in the rotation direction and matches the tilt angle of each power roller. In the toroidal-type continuously variable transmission, the synchronizing means includes a pinion formed in each trunnion, a first rod having a rack meshing with the pinion of the opposing trunnion in the same speed change direction, and an adjacent input / output cone. A second rod having a rack meshing with the trunnion of the disk in the same speed change direction.

In a second aspect based on the first aspect, the pinion is spline-coupled to the trunnion.

In a third aspect based on the first aspect, the first and second rods have an axial length adjusting member interposed therebetween.

[0018]

Accordingly, the first aspect of the present invention provides a transmission in which a trunnion opposed to a pinion provided on a trunnion supporting a power roller sandwiched between a plurality of input / output cone disks by a first rod provided with a rack has the same speed. By connecting the pinions of the trunnions of adjacent input / output cone disks in the same speed change direction with the second rod equipped with a rack, even if disturbance is applied to each power roller, Always match the turning angles,
It is possible to perform a stable shift operation, prevent deterioration of shift performance (misalignment of tilt angle) due to loosening of the wire as in the above-described conventional example, and have the first and the first in the casing of the continuously variable transmission. Only the space in which the second rod is displaced in the axial direction is sufficient, and the space formed in the casing is smaller than in the case where the trunnions are connected in the rotating direction by the rod and the gear as in the conventional example. Thus, the size and weight of the double-cavity toroidal type continuously variable transmission can be reduced.

In the second invention, the pinion and the trunnion are spline-coupled, so that when the trunnion is displaced in the axial direction at the time of shifting, the pinion is displaced relative to the trunnion to prevent slippage with the rack. It is possible to improve the durability by reducing the wear of the rack and the pinion.

According to the third aspect of the present invention, since the first and second rods are provided with the shaft length adjusting members, by adjusting the lengths of the rods, the play between the rack and the pinion can be reliably suppressed. This makes it possible to synchronize the tilt angles of the power rollers with high accuracy.

[0021]

Embodiments of the present invention will be described below with reference to the accompanying drawings.

FIG. 1 shows an example in which the present invention is applied to a double-cavity type toroidal type continuously variable transmission similar to that of FIGS. 5 to 7 of the prior art, and shows two sets of four toroidal transmission units 10 and 11. The two power rollers 4 are connected by a rack and pinion, and the same components as those in the conventional example are denoted by the same reference numerals, and redundant description is omitted.

In FIG. 1, the trunnions 3a, 3b and 3c and 3d have the power rollers 4 held and pressed between the input and output cone disks 1a, 2a and 1b and 2b, respectively, as in FIG. The trunnions 3a and 3b constitute a toroidal transmission unit 10, and the trunnions 3c and 3d constitute a toroidal transmission unit 11. Note that the axis C0 in FIG.
Are input / output axes, that is, input / output cone disks 1a to 2
4B shows the rotation axis.

The opposing trunnions 3a and 3b of the toroidal transmission unit 10 are connected to a rod 7a as a first rod.
Racks 8, 8 formed at both ends of the trunnion 3a,
The pinions 6, 6 formed in 3b are connected by meshing with each other, and the trunnions 3a, 3b rotate in opposite directions around the rotation axis C1 to synchronize the power rollers 4, 4 in the same speed change direction.

Here, the rod 7a is supported at its center by a supporting member 9a so as to be displaceable in the axial direction, and racks 8 formed at both ends are provided with trunnions 3a, 3b as shown in FIG. The teeth engage with the pinions 6 provided on the rotating shaft portion 30 in the lower part of the figure. Although only the trunnions 3a are shown in FIG. 2, the other trunnions 3b to 3d
Is similarly configured, and the pinion 6 is
The supporting member 9a is formed in a tubular shape, and supports the rod 7a slidably on its inner periphery, and is fixed to a casing (not shown) or the like.

Similarly, the opposing trunnions 3c and 3d of the toroidal transmission unit 11 are composed of racks 8 and 8 formed on both ends of a rod 7c as a first rod and pinions 6 and 6 formed on the trunnions 3c and 3d. The trunnions 3c, 3d rotate in opposite directions around the rotation axis C1, and synchronize the power rollers 4, 4 in the same speed change direction.

The rod 7c is supported at its center by a support member 9c so as to be freely displaceable in the axial direction. The racks 8 formed at both ends are connected to the trunnions 3c, 3c in the same manner as described above.
It meshes with the pinions 6, 6 provided on the lower rotating shaft portion 30 in FIG. The support member 9c is also formed in a tubular shape in the same manner as described above, supports the rod 7c slidably on the inner periphery, and is fixed to a casing (not shown) or the like.

The toroidal transmission units 10, 1
1 is synchronized with the trunnion 3
a, 3c are performed by a rod 7b.

The adjacent toroidal transmission units 10, 1
The first trunnions 3a, 3c are connected to the racks 8, 8 formed at both ends of a rod 7b as a second rod by engaging the pinions 6, 6 formed in the trunnions 3a, 3c with each other. 3c rotates in opposite directions about the rotation axis C1, and synchronizes the power rollers 4, 4 of the adjacent toroidal transmission units 10, 11 in the same speed change direction.

The rod 7b is supported at a substantially center of the trunnions 3a, 3c by a support member 9b so as to be freely displaceable in the axial direction. The racks 8 formed at both ends are formed with the trunnions 3a, 3c in the same manner as described above. It meshes with the pinions 6 and 6 provided on the lower rotating shaft portion 30. The support member 9b is also formed in a cylindrical shape in the same manner as described above, supports the rod 7b slidably on the inner periphery, and is fixed to a casing (not shown) or the like.

The thickness of the pinion 6 formed on each of the trunnions 3a to 3d is such that each of the rods 7a to 7d always remains in place even when each of the trunnions 3a to 3d is displaced in the direction of the rotation axis C1 during shifting.
The thickness is such that it can mesh with the rack 8 formed in FIG.

The configuration is as described above. Next, the operation will be described.

The power rollers 4 of the toroidal transmission units 10 and 11 rotate with the rotation of the input cone disks 1a and 1b, and power is transmitted to the output cone disks 2a and 2b. The output cone discs 2a and 2b rotate at a speed ratio according to.

In FIG. 2, when the opposing trunnions 3a, 3b and 3c, 3d are driven in opposite axial directions by an actuator (not shown), the power rollers 4, 4 are driven by the trunnions 3a, 3b, 3
The gear ratio is continuously changed by tilting around the rotation axis C1 of c and 3d.

When the gear ratio reaches a predetermined value, the actuator (not shown) drives the rotation axis C2 of the power rollers 4, 4 by feedback control similar to that of the conventional example.
Each of the trunnions 3a to 3d is driven in the axial direction again so that (see FIG. 2) coincides with the rotation axis C0 of the input / output cone disk, thereby maintaining the gear ratio.

In this shifting operation, the trunnions 3a to 3d rotate around the rotation axis C1 with the tilting of the power roller 4, for example, shifting to a higher gear ratio (Hi). Is performed, the trunnions 3a to 3d rotate as indicated by arrows in FIG.

That is, while the trunnions 3a and 3d rotate counterclockwise, the trunnions 3b and 3c rotate clockwise, and in each of the toroidal transmission units 10, 11, the opposing trunnions rotate in opposite directions. Move.

Here, the rod 7a of the toroidal transmission unit 10 is guided by the support member 9a and strokes obliquely upward in FIG. 1 to connect the racks 8, 8 formed at both ends and the pinions 6, 6 of the trunnions 3a, 3b. Thus, the turning angles of the trunnions 3a, 3b, that is, the tilting angles of the power rollers 4, 4, can be matched.

Similarly, the rod 7c of the toroidal transmission unit 11 is guided by the support member 9c and strokes obliquely upward in FIG. 1, thereby connecting the racks 8, 8 formed at both ends and the pinions 6, 6 of the trunnions 3c, 3d. Through this, the turning angles of the trunnions 3c and 3d, that is, the tilting angles of the power rollers 4 and 4 can be matched.

Further, the synchronization of the tilting angles of the power rollers 4 of the adjacent toroidal transmission units 10 and 11 is controlled by the racks 8 and 8 formed at both ends of the rod 7b and the trunnions 3a and 3b.
3c, performed by pinions 6, 6 and H
When shifting to the i side, the rod 7b is
1 and strokes to the left in FIG. 1, and the racks 8, 8 formed at both ends and the pinions 6 of the trunnions 3 a, 3 c
6, adjacent toroidal transmission units 10, 1
The tilt angle of the first power roller 4 can be matched.

During the shifting operation, the trunnions 3a to 3d are displaced in the direction of the rotation axis C1, while the rods 7a to 7c are allowed only by the axial displacement of the rods by the support members 9a to 9c. ~ 3d
Is displaced in the direction of the rotation axis C1, the rack 8 and the pinion 6 slide in the direction of the rotation axis C1, so that the rod 7a
7c can match the tilt angles of all the power rollers 4, 4 while displacing in the axial direction.

As described above, the trunnions 3a to 3d of the plurality of toroidal transmission units 10 and 11 are attached to the pinion 6 provided on the rotary shaft 30 by the rod 7 which can be displaced only in the axial direction.
By meshing with the racks 8 formed at both ends of the power rollers 4a to 7c, even when a disturbance is applied to each of the power rollers 4, the tilt angles are always made to coincide with each other, and a stable shift operation can be performed. As a result, it is possible to prevent deterioration of the shift performance (misalignment of the tilt angle) due to the slackness of the wire as in the conventional example. It is sufficient to secure only the space, and the space formed in the casing can be reduced as compared with the case where each trunnion is connected in the rotating direction by the rod and the gear as in the conventional example, and the double cavity type It is possible to promote reduction in size and weight of the toroidal type continuously variable transmission.

FIG. 3 shows a second embodiment in which the pinions 6 of the first embodiment are spline-coupled, and the other structure is the same as that of the first embodiment.

As shown in FIG. 2 of the first embodiment, the pinions 6 meshing with the rack 8 are trunnions 3a to 3a.
3d is attached to the lower rotating shaft portion 30 in the drawing. As shown in FIG. 3, the pinion 6 and the rotating shaft portion 30 are connected via the spline portion 33, and further, the lower surface of the pinion 6 (the lower portion in FIG. ) Is supported by a casing or the like (not shown), so that when the trunnions 3 a to 3 d are displaced in the direction of the rotation axis C <b> 1 at the time of gear shifting, the pinion 6 is splined 33 on the inner periphery.
While being relatively displaced in the direction of the rotation axis C1 via the rack 8.
With the rack 8 and the pinion 6
This makes it possible to reduce wear and improve durability.

FIG. 4 shows a third embodiment in which an axial length adjusting member 75 is interposed in the middle of the rods 7a to 7c of the first embodiment, and the rods 7a to 7c are supported by the axial length adjusting member. This is performed before and after the member 75, and the other configuration is the same as that of the first embodiment.

In FIG. 4, the rod 7a is composed of a rod 70 and a rod 7 each having a rack 8 formed at one end.
The female screw 72 is formed at the other end of the rod 70, while a rotatable screw 73 is formed at the other end of the rod 71.
Is attached, and by screwing the screw 73 to the female screw 72, the pair of rods 70, 71 are connected to form one rod 7a. The screw 73 is attached to the end of the rod 71 via a collar 74 which is rotatable relative to the rod 71 and is connected in the axial direction.
2, a screw 73 and a collar 74 constitute an axial length adjusting member 75.

The rod 7a is connected to the shaft length adjusting member 75.
Are supported by the cylindrical support members 9a, 9a before and after, and only axial displacement is allowed.

At the time of assembling the continuously variable transmission or the like, by adjusting the length of the rod 7a by turning the screw 73, the play between the rack 8 and the pinion 6 can be reliably suppressed. 4 can be synchronized with high accuracy.

[Brief description of the drawings]

FIG. 1 is a schematic plan view showing an arrangement of trunnions of a toroidal type continuously variable transmission showing an embodiment of the present invention.

FIG. 2 is a longitudinal sectional view of a trunnion.

FIG. 3 is a cross-sectional view showing a second embodiment and showing a coupling portion between a trunnion and a pinion.

FIG. 4 shows a third embodiment, and is a partial cross-sectional view of a rod.

FIG. 5 is a conceptual diagram of a toroidal type continuously variable transmission, showing a conventional example.

FIG. 6 is a longitudinal sectional view of a trunnion.

FIG. 7 is a schematic plan view showing the arrangement of trunnions.

[Explanation of symbols]

 1a, 1b Input cone disk 2a, 2b Output cone disk 3a to 3d Trunnion 4 Power roller 5 Pivot shaft 6 Pinion 7a to 7c Rod 8 Rack 9a to 9c Support member 10, 11 Toroidal transmission unit 20 Input shaft 21 Output gear 30 Rotary shaft Part 31 Offset part 32 Rod 33 Spline 70, 71 Rod 72 Female screw 73 Screw 74 Collar 75 Shaft length adjusting member

Claims (3)

[Claims] 1. A pair of power rollers which are respectively opposed to a plurality of input / output cone disks arranged coaxially and are held between the input / output cone disks.
A trunnion that can be displaced around the axis and in the axial direction while rotatably supporting each of the power rollers, and a synchronization unit that connects the trunnions in the rotation direction to match the tilt angle of each power roller. In the toroidal-type continuously variable transmission, the synchronizing means includes a pinion formed in each trunnion, a first rod having a rack meshing with the pinion of the opposing trunnion in the same speed change direction, and an input / output cone disk of an adjacent input / output cone disk. A toroidal-type continuously variable transmission, comprising: a trunnion; and a second rod having a rack that meshes in the same transmission direction. 2. The toroidal-type continuously variable transmission according to claim 1, wherein the pinion is spline-coupled to the trunnion. 3. The toroidal-type continuously variable transmission according to claim 1, wherein the first and second rods have a shaft length adjusting member interposed therebetween.