JP2682090B2 - Toroidal type continuously variable transmission - Google Patents

Description

Description: TECHNICAL FIELD The present invention relates to a toroidal type continuously variable transmission.

Conventional technology and its problems Conventionally, as a toroidal type continuously variable transmission, for example,
"SAE (Society of Automotive Engineers, Inc.) Pape
r, 751180, Fig.1 ", and this toroidal type continuously variable transmission is configured as a dual cavity type by arranging two sets of toroidal transmission parts called cavities in tandem. The torque transmission shaft provided with two sets of toroidal speed change units is arranged in parallel with the input shaft for engine rotation offset, and an output shaft is provided coaxially with the torque transmission shaft, and the rear shaft is provided on the output shaft. A propeller shaft for driving is connected.

Therefore, in the toroidal type continuously variable transmission, the rotating shaft of the engine coaxially arranged with the input shaft and the propeller shaft are offset from each other, and if the propeller shaft is mounted on an actual vehicle, the engine position may be high. Forced,
Inevitably, the bonnet becomes high, which causes deterioration of the forward visibility and increase of air resistance.

Therefore, it is desired that the rotary shaft of the engine and the propeller shaft are arranged substantially coaxially. Thus, in order to coaxially arrange the rotary shaft and the propeller shaft, the output shaft is coaxial with the input shaft. It is necessary to dispose it and to transmit the rotation of the torque transmission shaft to the output shaft via a transmission device such as a gear.

Further, in this case, in the above-described transmission device, the torque transmission shaft and the output shaft must rotate in the same direction, and it is necessary to temporarily reverse the rotation direction with the idler gear.

On the other hand, when the toroidal type continuously variable transmission is used for four-wheel drive, it is necessary to further branch the output shaft rotation and take it out to the side of the transmission, which makes the structure of this branching part extremely complicated. However, there was a problem that the transmission itself had to be remodeled significantly, resulting in a significant cost increase.

Therefore, in view of such conventional problems, the present invention arranges a rotary shaft of a power source such as an engine and an output shaft coaxially, and extracts power for four-wheel drive by using an idler gear provided at this time. Thus, it is an object of the present invention to provide a toroidal type continuously variable transmission whose structure can be remarkably simplified.

Means for Solving the Problems To achieve the above object, the present invention provides a first shaft coaxially arranged with an output rotation shaft of a power source, and a second shaft offset parallel to the first shaft. And a toroidal transmission unit disposed on one of the first shaft and the second shaft, and a first transmission device that transmits and receives torque between the toroidal transmission unit and the other of the first shaft and the second shaft is provided. At the same time, an output shaft is arranged substantially coaxially with the first shaft, a second transmission device having an idler gear is provided between the output shaft and the second shaft, and the idler gear is provided with the output shaft and the second shaft. The distribution gear is arranged to be offset with respect to the straight line connecting to, and the distribution gear is meshed in the offset direction of the idler gear, and the output shaft is connected to the first propeller shaft for driving one of the front wheel and the rear wheel, and the distribution gear is Drive the other of the front or rear wheels to It is configured by connecting the second propeller shaft.

In the toroidal type continuously variable transmission of the present invention having the above-described configuration, the second transmission is provided so that the output shaft can be arranged substantially coaxially with the first shaft, that is, the output rotation shaft of the power source. Become.

Further, since the idler gear provided in the second transmission device is arranged offset with respect to the straight line connecting the output shaft and the second shaft, the idler gear has a triangular point between the output shaft and the second shaft. Is arranged so as to form a structure that is provided so as to project laterally of the transmission.

Therefore, by engaging the distribution gear in the offset direction of the idler gear, the second propeller shaft connected to the distribution gear does not interfere with the transmission between the distribution gear and the output shaft. A sufficient offset amount can be provided.

Furthermore, when it is not used as a four-wheel drive, it can be used as a two-wheel drive by simply removing the distribution gear, and the two-wheel drive and the four-wheel drive are commonly used. The diversion between the two is greatly improved.

Embodiment Hereinafter, an embodiment of the present invention will be described in detail with reference to the drawings.

That is, FIG. 1 shows a toroidal type continuously variable transmission 10 according to an embodiment of the present invention, in which the rotation of an engine (not shown) as a power source provided on the left side of the figure is transmitted through a torque converter 12 to the toroidal type. Input to the continuously variable transmission 10.

As is well known, the torque converter 12 includes a pump impeller 12a, a turbine runner 12b and a stator 12c, and in particular, the torque converter 12 includes a lockup clutch 12d.

The output rotary shaft 14 of the torque converter 12 is arranged coaxially with the output rotary shaft of the engine (center line C).

Further, the toroidal type continuously variable transmission 10 is provided with a torque transmission shaft 16 as a first shaft arranged coaxially with the output rotation shaft 14, and the torque transmission shaft 16 is provided with a first toroidal transmission unit 18. The second toroidal transmission unit 20 is arranged in tandem.

The first and second toroidal speed change units 18, 20 have a pair of first input disks 18a, first output disks 18b, and second input disks 2 whose opposing surfaces are toroidal curved surfaces.
0a, the second output disk 20b, and the power rollers 18c, 18d and 20c, 20d frictionally contacted between the opposing surfaces of the first input and output disks 18a, 18b and the second input and output disks 20a, 20b. Composed by.

The power rollers 18c, 18d and 20c, 20d are arranged symmetrically with respect to the central axis C, and each power roller is, as disclosed in Japanese Utility Model Laid-Open No. 63-92859, a control valve and Via hydraulic actuator
The input disc is tilted according to the driving conditions of the vehicle
Output discs 18b, 20b by continuously changing the rotation of 18a, 20a
It is designed to be transmitted to.

The torque transmission shaft 16 is formed hollow and is attached to the housing 22 so as to be slightly movable in the axial direction.

The first toroidal transmission unit 18 is arranged on the left side of the torque transmission shaft 16 in the drawing, and the second toroidal transmission unit 20 is arranged on the right side of the torque transmission shaft 16 in the drawing, and
The respective first input disk 18a and second input disk 20a are arranged outside each other, and the first output disk 18b and second output disk 20b are arranged inside each other.

The first and second input disks 18a, 20a are fixed to the torque transmission shaft 16 via ball splines 24, 26 in the rotational direction, and are mounted so as to be able to move smoothly in the axial direction.

On the other hand, the first and second output disks 18b and 20b are spline-fitted to the output gear 28 which is relatively rotatably fitted to the torque transmission shaft 16, and the first and second output disks 18b and 20b.
The rotational force transmitted to the input gear 30a provided on the counter shaft 30 as the second shaft via the output gear 28.
The output gear 28 and the input gear 30a constitute a first transmission device 32.

By the way, a loading cam device 34 is provided outside the first input disk 18a (on the left side in the drawing), and the output rotation of the torque converter 12 is provided to the loading cam device 34 via a forward / reverse switching device 36. The loading cam device 34 receives an input and generates a pressing force corresponding to the input torque.

The loading cam of the loading cam device 34 is
34a is fitted to the torque transmission shaft 16 so as to be relatively rotatable, and is also locked to the torque transmission shaft 16 via a thrust bearing 38.

In addition, the second input disk 20a and the torque transmission shaft 1
The disc spring 40 is provided between the right end portion of FIG.

Therefore, the pressing force generated by the loading cam device 34 acts on the first input disc 18a and also on the second input disc 20a via the torque transmission shaft 16 and the disc spring 40, and The preload generated by the disc spring 40 acts on the second input disc 20a and also on the first input disc 18a via the torque transmission shaft 16 and the loading cam device 34. There is.

By the way, the forward / reverse switching device 36 includes a planetary gear mechanism 42 of a double planetary system, a forward clutch 44 capable of engaging the carrier 42a of the planetary gear mechanism 42 with the output rotary shaft 14, and a planetary gear mechanism 42. The ring gear 42b is constituted by a reverse brake 46 capable of being fastened to the housing 22.

Then, in the forward-reverse switching device 36, by engaging the forward clutch 44 and releasing the reverse brake 46, the rotation in the same direction as the engine rotation is input to the toroidal-type continuously variable transmission 10, and the forward clutch is used. By releasing 44 and engaging the reverse brake 46, rotation in the opposite direction is input.

In the planetary gear mechanism 42, 42c is a sun gear, 42d and 42e.
Is a planetary gear meshed with each other.

By the way, the rotation of the counter shaft 30 to which the output rotations of the first and second toroidal transmissions 18, 20 are input via the first transmission 32 is transmitted to the output shaft 50 via the second transmission 48. To be done.

Here, in the present embodiment, the output shaft 50 is arranged coaxially with the torque transmission shaft 16 (rotation center axis C).

In this case, the output shaft 50 and the rotation center shaft C do not have to be completely coaxial with each other, and the output shaft 50 may be arranged substantially in the vicinity of the rotation center shaft C in consideration of the mounting position of the engine, which will be described later.

In addition, the second transmission device 48 includes the counter shaft 30.
Drive gear 52 provided on the output shaft 50, a driven gear 54 provided on the output shaft 50, and an idler gear 56 meshed with the drive gear 52 and the driven gear 54, respectively. The counter shaft 30 rotates in the same direction. Is transmitted to the output shaft 50.

The drive gear 52, the driven gear 54 and the idler gear 5 are
Although 6 is schematically disclosed by the development method in FIG. 1, the respective gears are actually arranged in a positional relationship as shown in FIG.

That is, the driving gear 52 and the driven gear 54 are arranged at appropriate intervals in the vertical direction according to the positional relationship between the counter shaft 30 and the output shaft 50, and the idler gear 56
Is arranged offset (offset amount L) from a straight line P connecting the drive gear 52 and the driven gear 54.

A distribution gear 58 is meshed with the idler gear 56 in the direction offset from the straight line P (left side in FIG. 2).

A first propeller shaft 60 connected to a rear wheel side final reduction gear (not shown) is connected to the output shaft 50, and rear wheel drive is performed via the first propeller shaft 60 and the rear wheel side final reduction gear. A second propeller shaft connected to a front wheel-side final reduction gear (not shown)
62 are connected, and the front wheels are driven via the second propeller shaft 62 and the front wheel-side final reduction gear.

With the above configuration, the toroidal-type continuously variable transmission of the present embodiment
After the torque of the engine, which is input to the loading cam device 34 via the torque converter 12 and the forward / reverse switching device 36, is appropriately steplessly changed via the first and second toroidal speed change parts 18, 20. , Output gear 28 to counter shaft 30
Is transmitted to the input gear 30a, and the counter shaft 30 is rotated.

At this time, the forward-reverse switching device 36 is in the forward state, that is, the forward clutch 44 is engaged (the reverse brake 46
Is released), the first and second input disks 18a, 20
The rotation input to a is in the same direction as the rotation direction of the engine (this direction is the normal rotation), and the first and second output disks 18b and 20b and the output gear are transmitted through the power rollers 18c and 20c. The rotation input to 28 is in the reverse rotation direction, and the input gear 30a and the counter shaft 30 are again returned to the normal rotation.

The rotation of the counter shaft 30 is transmitted to the output shaft 50 via the second transmission device 48.
The transmission device 48 includes a drive gear 52, an idler gear 56, and a driven gear 54.By rotating the idler gear 56 in the reverse direction, the output shaft 50 is normally rotated in the same direction as the engine and is meshed with the idler gear 56. The distribution gear 58 is also rotated normally.

Therefore, the first propeller shaft 60 and the second propeller shaft 62 connected to the output shaft 50 are normally rotated in the same direction.

In this case, in order to equalize the rotational speeds of the first propeller shaft 60 and the second propeller shaft 62, it is desirable that the driven gear 54 and the distribution gear 58 have the same diameter.

Further, when the reverse brake 46 of the forward / reverse switching device 36 is engaged (the forward clutch 44 is disengaged) to set the vehicle in the reverse state, all the rotations of the loading cam device 34 and below are rotated in the reverse direction. .

By the way, in the present embodiment, the counter shaft
By providing the second transmission device 48 between the 30 and the output shaft 50, the output shaft 50 can be arranged coaxially with the torque transmission shaft 16, and the engine mounting position is set downward. The bonnet can be lowered.

Further, the second transmission device 48 is provided with an idler gear 56 so that the counter shaft 30 and the output shaft 50 are in the same rotational direction, and at this time, the idler gear 56 is a straight line connecting the drive gear 52 and the driven gear 54. Since they are offset with respect to each other, these drive gear 52, driven gear 54 and idler gear 5
6 are arranged so as to form a triangle, and the idler gear 5
6 is projected to the side of the output shaft 50.

Therefore, when the toroidal type continuously variable transmission 10 of this embodiment is used for four-wheel drive, it is connected to the distribution gear 58 by engaging the distribution gear 58 with the idler gear 56 protruding laterally. The second propeller shaft 62 can be sufficiently offset from the rotation center axis C so that it can be prevented from being interfered with by the housing 22 of the transmission 10.

Therefore, in the toroidal type continuously variable transmission 10 of the present embodiment, when performing four-wheel drive, simply add the distribution gear 58 and mesh the distribution gear 58 with the idler gear 56. On the other hand, when two-wheel drive is performed, the distribution gear 58 may be used in a detached state, and the common portion between the four-wheel drive and the two-wheel drive can be increased to greatly improve the diversion property.

Therefore, it is possible to significantly reduce the cost required for modifying the FR (front engine rear drive) -based four-wheel drive.

FIGS. 3 to 7 show schematic configurations showing other embodiments of the present invention, respectively, and the same components will be denoted by the same reference numerals, and duplicate description will be omitted.

That is, in the embodiment shown in FIG. 3, the forward / reverse switching device 36a is of a clutch switching type, and the forward / backward switching device 36a is arranged on the counter shaft 30.
By engaging (releasing the reverse clutch 72),
The rotation output via the first and second toroidal speed change units 18 and 20 is transmitted to the output shaft 50 via the counter shaft 30 and the second transmission device 48.

On the other hand, when the vehicle is moving backward, the reverse clutch 72 is engaged (the forward clutch 70 is disengaged) so that the torque transmission shaft
The rotation of 16 is directly transmitted to the second transmission device 48 via the gears 74, 76 without passing through the first and second toroidal transmission units 18, 20.

Next, in the embodiment shown in FIG. 4, the clutch switching type forward / reverse switching device 36b is used to connect the torque converter shaft 16 to the torque converter 12.
The toroidal speed change parts 18, 2 when the vehicle is moving forward.
Rotational force is transmitted via 0 and the gear 7
The rotation of the torque transmission shaft 16 is directly transmitted via the 4,76 second transmission device.
It is transmitted to 48.

In the embodiment shown in FIG. 5, the forward clutch 70 constituting the forward / reverse switching device 36c is arranged on the torque converter 12 side of the torque transmission shaft 16, and the reverse clutch 72 is provided on the counter shaft 30. Rotational force is transmitted through the first and second toroidal speed change units 18 and 20, and rotation of the torque transmission shaft 16 is directly transmitted to the second transmission device 48 via the gears 74 and 76 during reverse travel. There is.

In the embodiment shown in FIG. 6, the forward / reverse switching device 36d is formed of a dog clutch and is arranged on the counter shaft 30, and the starting clutch is arranged from the torque transmission shaft 16 to the torque converter 12 side.
78 is provided, and in this embodiment, the rotations output from the first and second toroidal speed change units 18 and 20 are transmitted to the second transmission device 48 during forward movement and reverse movement, respectively.

In the embodiment shown in FIG. 7, a forward / reverse switching device 36e constituted by a dog clutch is arranged on the output shaft 50, and a starting clutch 78 is provided on the torque converter 12 side of the torque transmission shaft 16. 1, 2nd toroidal transmission 1
The rotational force is transmitted to the second transmission device 48 via 8, 20 and the rotation of the torque transmission shaft 16 is reversely transmitted to the second transmission device 48 via the planetary gear set 80 during reverse travel.

In each of the embodiments shown in FIGS. 3 to 7 described above, the output shaft 50 is arranged coaxially with the torque transmission shaft 16, and
The second transmission device 48 between the counter shaft 30 and the output shaft 50 is composed of a drive gear 52, an idler gear 56 and a driven gear 54, respectively, and has the same function as that of the embodiment shown in FIG. You can

By the way, in each of the above embodiments, the case where the torque transmission shaft 16 is used as the first shaft and the counter shaft 30 is used as the second shaft has been disclosed, but the present invention is not limited to this. Torque transmission shaft 16 provided with 18, 20
Is arranged on the second shaft side, and the engine rotation input to the first shaft side is input to the first and second toroidal transmission units 18, 20 via the first transmission device 32. The rotation speed changed by 20 is transmitted to the torque transmission shaft 16 and the second transmission device 48.
It may be configured to be transmitted to the output shaft 50 via.

Of course, even in this case, it goes without saying that the output shaft 50 is arranged substantially coaxially with the first shaft.

As described above, in the toroidal type continuously variable transmission of the present invention, the output shaft is arranged substantially coaxially with the first shaft, that is, the output rotation shaft of the power source, by providing the second transmission. Therefore, the engine can be lowered while it is mounted on the vehicle.

Further, since the idler gear provided in the second transmission device is arranged offset with respect to the straight line connecting the output shaft and the second shaft, the idler gear has a triangular point between the output shaft and the second shaft. And is provided so as to project laterally of the transmission.

Therefore, by engaging the distribution gear in the offset direction of the idler gear, the second propeller shaft connected to the distribution gear does not interfere with the transmission between the distribution gear and the output shaft. A sufficient offset amount can be easily provided, the common part between two-wheel drive and four-wheel drive can be increased, and the diversion between them can be greatly improved, and the cost at the time of conversion of these drive systems can be improved. It has various excellent effects that can be significantly reduced.

[Brief description of the drawings]

FIG. 1 is a schematic configuration diagram showing an embodiment of the present invention, and FIG. 2 is a configuration diagram showing a gear arrangement relationship of an embodiment of a second transmission device used in the present invention, FIGS. 3, 4, and FIG. 5, FIG. 6 and FIG. 7 are schematic configuration diagrams respectively showing other embodiments of the present invention. 10 ... Toroidal type continuously variable transmission, 12 ... Torque converter, 16 ... Torque transmission shaft (first shaft), 18 ... First toroidal transmission section, 20 ... Second toroidal transmission section, 22 ... Housing , 30 …… Counter shaft (second axis), 32 ……
1st transmission, 36, 36a, 36b, 36c, 36d, 36e ... forward / reverse switching device, 48 ... second transmission, 56 ... idler gear, 58 ...
… Distribution gear, 60 …… first propeller shaft, 62 …… second
Propeller shaft.

Claims (1)

(57) [Claims] 1. A first device arranged coaxially with an output rotary shaft of a power source.
An axis and a second axis offset from and parallel to the first axis, the toroidal speed changer is disposed on one of the first axis and the second axis, and the toroidal speed changer and the first axis are provided. Alternatively, a first transmission device that transmits and receives torque to and from the other of the second shafts is provided, an output shaft is arranged substantially coaxially with the first shaft, and an idler gear is provided between the output shaft and the second shaft. And a second transmission device having, and the idler gear is arranged offset with respect to a straight line connecting the output shaft and the second shaft,
A first gear which meshes a distribution gear in an offset direction of the idler gear and drives one of a front wheel and a rear wheel on the output shaft.
A toroidal-type continuously variable transmission characterized in that a propeller shaft is connected and a second propeller shaft that drives the other one of the front wheel and the rear wheel is connected to the distribution gear.