JPH03223555A - Toroidal continuously variable transmission - Google Patents

Abstract

PURPOSE:To continuously rotate an output shaft from a suspended position between normal and reverse rotations by fixing a sun gear and a ring gear onto the end section of an input shaft and the outside surface of an output side disc respectively, and pivotally supporting a planetary gear meshed with the sun gear and the ring gear onto a support arm fixed to the output shaft. CONSTITUTION:A sun gear 21 and a ring gear 18 are fixed onto the end section of an input shaft 1 and the outside surface 4b of an output side disc 4 respectively, and planetary gears 19 meshed with the sun gear 21 and the ring 18 are pivotally supported onto support arms 22 fixed onto the end section of an output shaft 3. In this constitution, when a reduction ratio between an input side and an output side disc 2 and 4 is matched to a reduction ratio between the sun gear 21 and the ring gear 18 with the tilt angle of a displacement shaft 5 regulated, it is possible to suspend the rotation of the output shaft 3 regardless of the rotation of an input shaft 1. It is also possible to continuously convert the rotation direction of the output shaft 3 by way of a suspended position between normal are reverse rotations with the input shaft 1 kept rotated to one direction by regulating the tilt angle of the displacement shaft 5.

Description

[Detailed Description of the Invention] (Industrial Application Field) The toroidal continuously variable transmission according to the present invention can be used, for example, as an automobile transmission, a riding lawn mower, a 3° snow remover, an electric vehicle, a forklift, etc. It can be used as a transmission for a light vehicle, and furthermore as a transmission for rotating an auxiliary machine for an automobile engine at an appropriate rotational speed regardless of fluctuations in the engine rotational speed.

(Prior art) As a transmission for automobiles with relatively low engine output (for example, 100 horsepower or less) such as motorcycles, and for light vehicles that run at low speeds such as riding lawn mowers, snow blowers, electric vehicles, and forklifts. Furthermore, a toroidal continuously variable transmission as schematically shown in Figures 9 and 10 is used as a transmission to rotate auxiliary equipment such as a compressor and generator at an optimal speed regardless of fluctuations in engine speed. The use of is being studied.

This toroidal type continuously variable transmission is, for example,
As disclosed in Japanese Patent No. 1465, the input side disk 2 is supported at the end of the input shaft 1, and the output side disk 4 is supported at the end of the output shaft 3, and the inclination angle is freely adjustable. A power roller 6.6 rotatably supported by a displacement shaft 5.5 is connected to both the input side and output side disks 2.
It is constructed by sandwiching it between 4.

The mutually opposing inner surfaces 2a and 4a of both the input and output disks 2.4 are each concave with an arcuate cross section, and the circumferential surface 6a of each power roller 6.6.

6a is a spherical convex surface that brings the peripheral surfaces 6a, 6a of each power roller 6.6 into contact with the inner surfaces 2a, 4a.

A pressure device 7 such as a loading cam is provided between the input shaft 1 and the input disk 2, and the pressure device 7 elastically presses the input disk 2 toward the output disk 4. are doing.

In the case of a toroidal continuously variable transmission configured in this way, as shown in FIG. 9, the outer circumferential surface 6a of each power roller 6.6,
When each displacement shaft 5 .
Deceleration is performed between the output shaft 3 and the output shaft 3.

On the other hand, as shown in FIG. 10, the outer peripheral surfaces 6a, 6a of each power roller 6.6 are located at the outer peripheral portion of the inner surface 2a of the input side disk 2 and the center portion of the output side disk 4. When the respective displacement shafts 5.5 are tilted so that they abut, a speed increase occurs between the input shaft 1 and the output @3.

If the inclination angle of each displacement shaft 5.5 is set to be intermediate between that in FIG. 9 and FIG. 10, an intermediate speed ratio can be obtained between the input shaft 1 and the output shaft 3.

FIG. 11 shows a state in which a toroidal continuously variable transmission configured and operated as described above is incorporated into an actual transmission such as a transmission for a light vehicle. 12
(See No. 0430).

The power is transmitted to the gear 8 through a power transmission mechanism (not shown), and is further transmitted to the power transmission shaft 1 through the gear 9 that meshes with the gear 8.
The rotational driving force transmitted to the toroidal continuously variable transmission 12 is transmitted via the clutch device 11 to the input shaft l of the toroidal continuously variable transmission 12.

Therefore, when the clutch device 11 is connected, the rotational driving force of the power transmission shaft 10 is transmitted to the loading cam type pressure device 7, which is composed of the input shaft 1, the rollers 13, 13, and the cam plate 17, and the input side disk. 2. It is transmitted to the output side disk 4 via a power roller 6.6 that rotates around a displacement axis 5.5. Further, this rotational driving force is transmitted through a gear 15 fixed to the outer circumferential surface of the cylindrical portion 14 that functions as an output shaft, and a gear 16 meshed with this gear 15. taken out.

(Problem to be Solved by the Invention) By the way, in the case of a toroidal continuously variable transmission that is configured and operates as described above and is used by being incorporated into an actual transmission, the displacement axis 5.5 can be tilted. Although it is possible to obtain any gear ratio within the range, the rotation of the output shaft 3 cannot be changed by itself (with the toroidal continuously variable transmission alone) when the input shaft 1 is rotating only in one direction. It is not possible to stop the motor or to continuously switch between normal rotation and reverse rotation after the stopped state.

Therefore, when it is necessary to stop the rotation of the output shaft 3 (cylindrical portion 14) even though the input shaft 1 is rotating in one direction, or when it is necessary to reverse the normal rotation from the stopped state, the above-mentioned As shown in FIG. 11, a toroidal continuously variable transmission 12
It is necessary to connect the clutch device 11 and the clutch device 11 in series and disconnect the clutch device 11, or to connect a fluid coupling in the middle of the output shaft 3, or to incorporate a reversing device for changing the direction of rotation. As a result, the transmission becomes more complex and larger, which inevitably increases costs.

The toroidal continuously variable transmission of the present invention was invented in view of the above circumstances.

(Means for Solving the Problems) The toroidal continuously variable transmission of the present invention includes an input side disk supported around an input shaft and to which rotational driving force is transmitted from the input shaft, and an input shaft An output side disk is rotatably supported around the input shaft, and an input side disk, an output side disk is rotatably supported around the input shaft, and a displacement shaft whose inclination angle can be adjusted freely. It consists of a power roller sandwiched between both disks.

Further, the inner surfaces of the input side and output side disks, which face each other, are each made into a concave surface having an arcuate cross section, and the circumferential surface of the power roller is made into a spherical convex surface, so that this circumferential surface and the inner surface are in contact with each other. I'm letting you touch me.

In the toroidal continuously variable transmission of the present invention as set forth in claim 1, a sun gear is provided at an end of the input shaft,
A ring gear concentric with the sun gear is fixed to the outer surface of the output disk, and the sun gear and the ring are fixed to a support arm fixed to the end of the output shaft provided concentrically with the input shaft. It pivotally supports a planetary gear that meshes with the gear.

Furthermore, in the toroidal continuously variable transmission of the present invention as set forth in claim 3, a ring gear is provided at an end of the input shaft,
A sun gear concentric with the ring gear is fixed to the outer surface of the output side disk, and the sun gear and the ring are fixed to a support arm fixed to the end of the output shaft provided concentrically with the input shaft. It pivotally supports a planetary gear that meshes with the gear.

(Function) In the case of the toroidal continuously variable transmission of the present invention configured as described above, the gear ratio between the input side disk and the output side disk can be adjusted by adjusting the inclination angle of the displacement axis. By matching the speed ratio between the sun gear and the ring gear, the rotation of the output shaft can be stopped even though the input shaft is rotating.

In addition, by adjusting the inclination angle of the displacement shaft, the rotation direction of the output shaft can be continuously changed between normal rotation and reverse rotation after the input shaft is rotated in one direction. I can do it.

(Example) Next, the present invention will be explained in more detail while explaining the illustrated embodiment.

FIG. 1 is a schematic sectional view showing a first embodiment of the present invention, which corresponds to the invention set forth in claim 1.

The main body of this toroidal type continuously variable transmission is the same as that shown in FIG. 11 above for basic fishing.

1 is an input shaft, and a cam plate 1 is provided on the intermediate outer peripheral surface of this input shaft 1.
7 is fixed, and this cam plate 17 is configured to rotate together with the input shaft 1. Further, a plurality of rollers 13.13 are provided between the outer surface of the input side disk 2 supported around the input shaft l and the cam plate 17, and as the cam plate 17 rotates, the input side disk 2 is elastically pressed in a direction away from the cam plate 17 (to the right in FIG. 1) and rotates together with the input shaft 1.

On the other hand, around the tip of the input shaft 1 (the right-hand side in FIG. 1), an output disk 4 is rotatably supported with respect to the input shaft 1 via a rolling bearing (not shown) or the like.

Around the input shaft 1, a plurality of displacement shafts 5.5 are provided between the input side disk 2 and the output side disk 4, the inclination angle of which can be adjusted freely, and a power roller is attached to each displacement shaft 5.5. 6
．． 6 rotatably supported, and each power roller 6.
6 is held between the input side and output side disks 2.4.

The mutually opposing inner surfaces 2a and 4a of both the input and output side disks 2.4 are concave surfaces with arcuate cross sections, and the peripheral surfaces 6a and 6a of each power roller 6.6 are spherical convex surfaces. , this peripheral surface 6a56a and the inner surfaces 2a, 4a are brought into contact.

Further, at the tip of the input shaft 1, a ring gear 18, which will be described below, is provided at a portion protruding from the outer surface 4b of the output side disk 4.
In combination with the planetary gears 19 and 19, a sun gear 21 constituting a planetary gear mechanism 20 is fixed.

On the other hand, a ring gear 18 concentric with the sun gear 21 is fixed to the outer surface 4b of the output side disk 4.

Further, a plurality of support arms 22, 22 are fixed to the end of the output shaft 3 provided concentrically with the input shaft 1, and each support arm 22.
．． 22, a planetary gear 19.19 which meshes with the sun gear 21 and the ring gear 18 is pivotally supported.

In the case of the toroidal type continuously variable transmission of the present invention configured as described above, as in the case of the conventional toroidal type continuously variable transmission described above, the outer circumferential surfaces 6a, 6a of each power roller 6.6
is a part near the center of the inner surface 2a of the input side disk 2,
When each displacement shaft 5.5 is tilted so that it comes into contact with the outer circumferential portion of the output side disk 4 (see Fig. 9)
, deceleration is performed between the input shaft l and the output shaft 3, and conversely, the outer peripheral surfaces 6a, 6a of each power roller 6.6 are connected to the outer peripheral portion of the inner surface 2a of the input side disk 2 and the output side When each displacement shaft 5.5 is tilted so that it comes into contact with the central portion of the disk 4 (see Fig. 10), speed increases between the input shaft 1 and the output shaft 3, and the displacement By adjusting the inclination angle of the shaft 5.5, the gear ratio between the input side disk 2 and the output side disk 4 can be freely adjusted.

Furthermore, in the case of the toroidal continuously variable transmission of the present invention, a planetary gear mechanism 20 consisting of a sun gear 21, a ring gear 18, and a planetary gear 19 is provided between the output side disk 4 and the output shaft 3. Therefore, the rotational driving force transmitted to the output side disk 4 as the power roller 6.6 rotates is further reduced in speed by the planetary gear mechanism 20, and then transmitted to the output shaft 3.

If you want to stop the rotation of the output shaft 3 even though the input shaft 1 is rotating, by appropriately changing the inclination angle of the displacement shaft 5.5, the input side disk 2 and the output side disk 4 can be stopped.
The speed ratio (reduction ratio) between the ring gear 18 and the sun gear 21 constituting the planetary gear mechanism 20 (when the revolution of the planetary gears 19 and 19 is stopped,
(reduction ratio between sun gear 21 and ring gear 18).

As a result, even though the input shaft 1 is rotating, the rotation of the output shaft 30 can be stopped.

That is, in this state, for example, when the input shaft 1 and the sun gear 21 rotate in the direction of the arrow a in FIG. Based on
The output side disk 4 and the ring gear 18 are connected to each other as shown by the arrow C in the figure.
Rotate in the direction.

In this state, the planetary gears 19 and 19 constituting the planetary gear mechanism 20 are engaged with the ring gear 18, and the arrow C
However, based on the meshing with the sun gear 21, the arrow C
Try to move in the direction.

Therefore, if the reduction ratio between the input side disk 2 and the output side disk 4 is adjusted to the reduction ratio between the ring gear 18 and the sun gear 21, the movement in the direction of the arrow C and the movement in the direction of the arrow C are canceled out, and each planetary gear 19.19 does not revolve around the sun gear 21, but only rotates at the end of the support arm 22.22.

As a result, the support arm 22 which pivotally supported each planetary gear 19.19
．． 22 does not move, and the output shaft 3 to which this support arm 22.22 is fixed does not rotate.

Therefore, even if a clutch mechanism or a fluid coupling is not incorporated into a transmission incorporating a toroidal type continuously variable transmission, it is possible to stabilize the state in which the rotation of the output shaft 3 is stopped even though the input shaft 1 is rotating. You can get it.

The transmission device is originally provided with a gear transmission mechanism for changing the rotational speed from a drive source such as an engine.
Although the planetary gear mechanism 2o is provided, a part of the gear transmission mechanism can be omitted. Therefore, by providing the planetary gear mechanism 20, the manufacturing cost of the transmission as a whole does not increase.

In the illustrated embodiment, a one-way clutch 23 and a torque limiter 24 are provided at the intermediate portion of the output shaft 3.

Therefore, if the torque limiter 24 slips at a torque higher than the set torque, the output shaft 3 side will suddenly stop, and excessive torque will pass through the sun gear 21 to the input side disk 2.
Even if the input side disk 2 and the power roller 6 are subjected to such force, the contact surface between the input side disk 2 and the power roller 6 will not be damaged. Furthermore, even when the output shaft 3 side is stopped by the one-way clutch 23,
A portion of the output shaft 3 located in front of the one-way clutch 23 (on the left side in FIG. 1) can rotate in one direction.

Therefore, if the output shaft 3 side is used only by rotating in one direction, even if the output shaft 3 side stops, the control of the displacement shaft 5 will not allow some error in the direction in which the one-way clutch 23 slips. , it is possible to stably stop the rear side of the output shaft 3 (the right side in FIG. 1).

In addition, such one-way clutch 23 and torque limiter 24
It is not necessarily necessary to provide both. For example, as shown in FIG. 2, only one-way clutch 23 may be provided, or a third
As shown in the figure, only the torque limiter 24 can be provided.

As shown in FIG. 2, the structure provided with only one-way clutch 23 is strong from the driven parts (auxiliary equipment), for example, like the drive mechanism of automobile auxiliary equipment. There is no risk of a-blow being transmitted, and it can be used in applications where there is no need to reverse the driven part.

Furthermore, as shown in Fig. 3, a structure in which only the torque limiter 24 is provided, such as a transmission for a tractor's traveling mechanism, has the risk of transmitting a strong impulse from the driven part (axle part).
Moreover, it can be used in applications where it is necessary to switch between forward and reverse rotation of the driven part.

That is, in the case of this embodiment, by appropriately changing the inclination angle of the displacement shaft 5, the gear ratio of the toroidal continuously variable transmission 12 is adjusted, and the ratio of the rotational speeds of the ring gear 18 and the sun gear 21 is adjusted to By changing the speed ratio at which the rotation of the output shaft 3 is stopped regardless of the rotation of the input shaft 1, the direction of rotation of the output shaft 3 can be changed between normal rotation and reverse rotation while the input shaft 1 is rotating in one direction. can be switched to For example, if the rotational speed of the ring gear 18 is made to increase, the output shaft 3 will rotate in the direction of arrow C in FIG. 3 rotates in the direction of arrow C in the figure.

Furthermore, the position where the torque limiter 24 is provided is the first position.
．． In addition to being located in the middle of the output shaft 3 as shown in FIG. 3, it can also be provided in the middle of the input shaft 1 and near the sun gear 21 as shown in FIG.

Next, FIG. 5 is a schematic sectional view showing a fifth embodiment of the present invention, which corresponds to the invention described in claim 3.

In the case of this embodiment, unlike the cases of the first to fourth embodiments described above, a ring gear 18 is provided at the end of the input shaft 1, and a sun concentric with the ring gear 18 is provided on the outer surface 4b of the output side disk 4. While fixing the gears 21, the input shaft 1
Support arm 2 fixed to the end of output shaft 3 provided concentrically with
2.22, a planetary gear 19.19 which meshes with the sun gear 21 and the ring gear 18 is pivotally supported.

Because of this configuration, in the case of this embodiment, a planetary gear mechanism 20 consisting of a sun gear 21, a ring gear 18, and a planetary gear 19 is provided between the output side disk 4 and the output shaft 3.
The transmission ratio pattern is different from that of the first to fourth embodiments.

In addition, even though the input shaft 1 is rotating, if the revolution of the planetary gears 19 and 19 is stopped in order to stop the rotation of the output shaft 3, the rotation speed on the output side is lower than the rotation speed of the input shaft 1. Since the rotational speed of the disk 4 increases, by appropriately changing the inclination angle of the displacement shaft 5.5, the speed ratio (speed increase ratio) between the input side disk 2 and the output side disk 4 can be changed to the planetary gear. The speed increasing ratio is adjusted to match the speed increasing ratio between the ring gear 18 and the sun gear 21 that constitute the mechanism 20.

The other configurations and operations are the same as those of the first embodiment described above, so the same parts are given the same reference numerals and redundant explanations will be omitted.

In addition, in the case of the invention stated in claim 3, the above-mentioned claim 1
As shown in FIG. 6, only the one-way clutch 23 is provided, or as shown in FIG.
It is also possible to provide only the torque limiter 24, or furthermore, as shown in FIG. 8, the torque limiter 24 may be provided at a position near the ring gear I8 in the middle of the input shaft 1.

(Effects of the Invention) Since the toroidal continuously variable transmission of the present invention is configured and operates as described above, it does not require the use of a clutch mechanism or fluid coupling, even though the input shaft is rotating. Not only is it possible to stably stop the rotation of the output shaft, but it is also possible to switch the rotation direction of the output shaft while keeping the input shaft rotating in one direction without using a separate reversing mechanism. of,
It is possible to perform the operation continuously after a stop state, and it is possible to downsize and lower the speed of a transmission incorporating a toroidal type continuously variable transmission.

[Brief explanation of drawings]

FIG. 1 is a schematic sectional view showing a first embodiment of the present invention corresponding to the invention described in claim 1, and FIGS. 2 to 4 are schematic sectional views showing second to fourth embodiments. , FIG. 5 is a schematic sectional view showing a fifth embodiment of the present invention corresponding to the invention described in claim 3, and FIGS. 6 to 8 are schematic sectional views similarly showing sixth to eighth embodiments. , Figures 9 and 10 show the basic configuration of the toroidal continuously variable transmission to which the present invention is applied, with Figure 9 being a side view showing the state at maximum deceleration, and Figure 10 showing the state at maximum speed increase. FIG. 11 is a partial cross-sectional view showing the toroidal continuously variable transmission installed in a vehicle transmission. 1: Input shaft, 2: Input side disk, 2a: Inner surface, 3:
Output shaft, 4; Output side disk, 4a: Inner surface, 4b: Outer surface, 5: Displacement shaft, 6: Power roller, 6a: Circumferential surface, 7
: Pressure device, 8.9: Gear, 10: Power transmission shaft, 11:
Clutch device, 12 Nidroidal continuously variable transmission, 13:
Roller, 14: Cylindrical part, 15.16: Gear, 17: Cam plate, 18: Ring gear, 19: Planetary gear, 20: Planetary gear mechanism, 21: Sun gear, 22: Support arm, 23: Directional clutch, 24 : Torque limiter.

Claims (7)

[Claims] (1) An input side disk supported around the input shaft and to which rotational driving force is transmitted from the input shaft, and an output side disk supported around the input shaft so as to be rotatable with respect to the input shaft, respectively. It consists of a power roller that is rotatably supported by a displacement shaft that is provided around the input shaft so as to be able to adjust its inclination angle, and that is sandwiched between both input and output side disks. The inner surfaces of both disks that face each other are concave surfaces with arc-shaped cross sections, and the circumferential surface of the power roller is a convex spherical surface, and this circumferential surface and the inner surface are in contact with each other. In the transmission, a sun gear is fixed to the end of the input shaft, and a ring gear concentric with the sun gear is fixed to the outer surface of the output side disk, and the ring gear is provided concentrically with the input shaft. A toroidal continuously variable transmission characterized in that a planetary gear meshing with the sun gear and the ring gear is pivotally supported on a support arm fixed to an end of an output shaft. (2) The toroidal continuously variable transmission according to claim 1, further comprising a torque limiter between the input shaft and the sun gear. (3) an input-side disk supported around the input shaft and to which rotational driving force is transmitted from the input shaft; and an output-side disk supported around the input shaft so as to be rotatable with respect to the input shaft, respectively. It consists of a power roller that is rotatably supported by a displacement shaft that is provided around the input shaft so as to be able to adjust its inclination angle, and that is sandwiched between both input and output side disks. The inner surfaces of both disks that face each other are concave surfaces with arc-shaped cross sections, and the circumferential surface of the power roller is a convex spherical surface, and this circumferential surface and the inner surface are in contact with each other. In the transmission, a ring gear is provided at the end of the input shaft, and a sun gear concentric with the ring gear is provided on the outer surface of the output side disk.
a toroidal type gear, wherein a planetary gear meshing with the sun gear and the ring gear is pivotally supported on a support arm fixed to an end of an output shaft provided concentrically with the input shaft; gearbox. (4) The toroidal continuously variable transmission according to claim 3, further comprising a torque limiter between the input shaft and the ring gear. (5) The toroidal continuously variable transmission according to any one of claims 1 to 4, wherein a one-way clutch is provided in the middle of the output shaft. (6) The toroidal continuously variable transmission according to any one of claims 1, 3, and 5, wherein a torque limiter is provided in the middle of the output shaft. (7) Any one of claims 1 to 6, wherein a pressure device is provided between the input shaft and the input side disk, and the pressure device elastically presses the input side disk toward the output side disk. The toroidal continuously variable transmission described in .