JP2000266154A - Continuously variable transmission with infinite gear ratio - Google Patents

Abstract

PROBLEM TO BE SOLVED: To achieve improvement of durability of a transmission and miniaturization by reducing thrust force generated on a unit output shaft. SOLUTION: A transmission output gear 7 of a helical gear is provided on one end of a unit output shaft 6. The rotational direction of the unit output shaft 6, viewed from the transmission output gear 7 side is made into the counterclockwise direction in forward travel of a power circulation mode. The tooth traces of respective helical gears on the unit output shaft 6, viewed from the transmission output gear 7 side are set so that a sun gear 5a has a right helix, a ring gear 5c has a left helix, a constant transmission output gear 3b has a left helix, and a transmission output gear 7 has a left helix.

Description

DETAILED DESCRIPTION OF THE INVENTION

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to an infinitely variable transmission with an infinite transmission ratio used in vehicles and the like.

[0002]

2. Description of the Related Art A belt-type or toroidal-type continuously variable transmission is conventionally known as a vehicle transmission. In order to further expand the shift range of such a continuously variable transmission, a continuously variable transmission is known. A continuously variable transmission with an infinitely variable transmission ratio is known in which a constant transmission and a planetary gear mechanism are combined to control the transmission ratio to infinity. For example, Japanese Patent Application No. 8-15440 proposed by the present applicant has been known. And Japanese Patent Application No. 9-29080.

[0003] These are a planetary gear mechanism in which a continuously variable transmission and a constant transmission (reducer) are connected in parallel to a unit input shaft connected to an engine, and their outputs are arranged on a unit output shaft. The output side of the continuously variable transmission is connected to the sun gear of the planetary gear mechanism via the continuously variable transmission output gear train, and the output shaft of the constant transmission is connected to the carrier of the planetary gear mechanism via the power circulation mode clutch. Respectively.

The output shaft of the continuously variable transmission connected to the sun gear is connected to a unit output shaft, which is the output shaft of an infinitely variable speed ratio transmission, via a direct connection mode clutch.
The ring gear of the planetary gear mechanism is also coupled to the unit output shaft.

On the unit output shaft, a direct-coupled mode clutch, a planetary gear mechanism, a power circulation mode clutch, an output shaft of a constant transmission and a transmission output gear are coaxially arranged, and the transmission output gear is a differential gear. And the torque is transmitted to the drive shaft.

In such a continuously variable transmission with an infinite transmission ratio,
By connecting the power circulation mode clutch and disengaging the direct connection mode clutch, the unit speed ratio (unit input shaft speed / unit output shaft speed) is determined according to the speed ratio difference between the continuously variable transmission and the fixed transmission. ) From the negative value to the positive value, including the infinite (= geared neutral point) continuous gear shift control, and the power circulation mode clutch is disconnected, while the direct connection mode clutch is connected to It is possible to selectively use the direct connection mode in which the shift control is performed according to the speed ratio of the step transmission.

[0007]

By the way, in the above-mentioned conventional example, a helical gear is used for each gear of the planetary gear mechanism, the constant transmission and the transmission output gear, and the helical gear has a helical gear. It is known that a thrust force is generated according to a torsional direction and a torque transmitting direction.

For example, as shown in FIGS. 16 (A) and 16 (B), a case where torque is transmitted by meshing a left-handed helical gear 90 and a right-handed helical gear 91 is considered. Note that a right-handed helical gear rotates clockwise on the circumference when traveling beyond the tooth trace when viewed from the axial direction.A left-handed helical gear is viewed from the axial direction. When following the tip of the tooth, the advancing direction rotates counterclockwise on the circumference.

As shown in FIG. 16A, when the helical gear 90 is driven counterclockwise as viewed from the right side in FIG. 16 with the helical gear 90 as the driving side and the helical gear 91 as the driven side. 90 generates a thrust force toward the left side in the figure, while the driven helical gear 91 generates a thrust force toward the right side in the figure.

Conversely, as shown in FIG. 16B, when the helical gear 91 is driven clockwise as viewed from the right side in FIG. The helical gear 90 turns counterclockwise in the same manner as described above, but generates a thrust force toward the right side in the figure, while the helical gear 91 on the drive side also rotates clockwise in the same manner as described above. , And the thrust force is directed to the right in the figure, contrary to the above.

However, in the above-described conventional example, when helical gears are used for the respective gears, the thrust force generated by the respective gears due to the transmission of torque concentrates on one side depending on the combination of the torsional directions of the helical gears to be combined.
There is a problem that the load on the bearing that supports the unit output shaft becomes excessive and the durability is reduced, and that the friction increases due to the increase of the thrust force and the power transmission efficiency is reduced. There is a problem that increasing the size of the bearings hinders downsizing of the transmission.

SUMMARY OF THE INVENTION The present invention has been made in view of the above problems, and has as its object to reduce the thrust force generated on the unit output shaft to improve the durability of the transmission and promote downsizing. .

[0013]

According to a first aspect of the present invention, a continuously variable transmission and a constant transmission respectively connected to a unit input shaft and a unit output shaft arranged parallel to the unit input shaft are provided. A planetary gear mechanism comprising: a sun gear connected to the output shaft of the continuously variable transmission; a carrier formed of a single pinion and connected to the output shaft of the fixed transmission; and a ring gear connected to the unit output shaft. A power circulation mode clutch interposed in the transmission path from the unit input shaft to the output of the continuously variable transmission via the carrier, and two elements of the sun gear, carrier, and ring gear of the planetary gear mechanism. An interposed direct-coupled mode clutch, a continuously variable transmission output path for transmitting a driving force from the continuously variable transmission to the sun gear, and a communication with the unit output shaft via transmission means. The constant speed transmission, the planetary gear mechanism, and the transmission means are each constituted by a helical gear, and the power circulation mode clutch is engaged, while the direct connection mode clutch is provided. When the power circulation mode is released, the thrust force generated by the ring gear and the sun gear is set in the helix direction of the helical gear in a torsion direction that does not cancel each other, and
The teeth of the helical gear are set so that at least one of the constant transmission, the transmission means, and the thrust force generated by the ring gear on the unit output shaft is in a different direction.

According to a second aspect of the present invention, in the first aspect, a helical gear of transmission means is provided at one end of the unit output shaft, and the unit output as viewed from the transmission means side when the power circulation mode advances. When the rotation direction of the shaft is counterclockwise, the tooth trace of the helical gear on the unit output shaft viewed from the transmission means side, the sun gear is right-handed, the ring gear is left-handed, the fixed transmission is left-handed, and the transmission means is left-handed. Is set to

According to a third aspect of the present invention, in the first aspect, a helical gear of a transmission means is provided at one end of the unit output shaft, and the unit output viewed from the transmission means side when the power circulation mode advances. The rotation direction of the shaft is counterclockwise, and the tooth traces of the helical gear on the unit output shaft viewed from the transmission means side, the sun gear is right-handed, the ring gear is left-handed, the constant transmission is right-handed, and the transmission means is right-handed. Is set to

According to a fourth aspect of the present invention, in the first aspect, a helical gear of transmission means is provided at one end of the unit output shaft, and the unit output as viewed from the transmission means side when the power circulation mode is advanced. When the rotation direction of the shaft is counterclockwise, the tooth trace of the helical gear on the unit output shaft viewed from the transmission means side, the sun gear is right-handed, the ring gear is left-handed, the fixed transmission is right-handed, and the transmission means is left-handed. Is set to

According to a fifth aspect of the present invention, in the first aspect, a helical gear of transmission means is provided at one end of the unit output shaft, and the unit output viewed from the transmission means side when the power circulation mode advances. The rotation direction of the shaft is clockwise, and the teeth of the helical gear on the unit output shaft viewed from the transmission means side, the sun gear is left-handed, the ring gear is right-handed, the fixed transmission is right-handed, and the transmission means is right-handed. Is set.

According to a sixth aspect of the present invention, in the first aspect, a helical gear of transmission means is provided at one end of the unit output shaft, and the unit output as viewed from the transmission means side when the power circulation mode is advanced. The rotation direction of the shaft is clockwise, and the teeth of the helical gear on the unit output shaft as viewed from the transmission means side, the sun gear is left-handed, the ring gear is right-handed, the constant transmission is left-handed, and the transmission means is left-handed. Is set.

According to a seventh aspect of the present invention, in the first aspect, a helical gear of transmission means is provided at one end of the unit output shaft, and the unit output as viewed from the transmission means side when the power circulation mode is advanced. The rotation direction of the shaft is clockwise, and the teeth of the helical gear on the unit output shaft as viewed from the transmission means side, the sun gear is twisted left, the ring gear is twisted right, the fixed transmission is twisted left, and the transmission means is twisted right. Is set.

The eighth invention is characterized in that the second or fifth invention
In the invention, when the ratio of the number of teeth between the sun gear and the ring gear of the planetary gear mechanism is α, the pitch radius of the helical gear on the unit output shaft is R, and the torsion angle is β,

[0021]

(Equation 2)

Where βo: torsion angle of the transmission means βg: torsion angle of the constant transmission βr: torsion angle of the ring gear Ro: pitch radius of the transmission means Rg: pitch radius of the constant transmission Rr: pitch radius of the ring gear Or set so that it is almost satisfied.

In a ninth aspect of the present invention, a continuously variable transmission and a constant transmission respectively connected to a unit input shaft and a unit output shaft disposed in parallel with the unit input shaft are provided. A planetary gear mechanism comprising a sun gear connected to the output shaft of the transmission, a carrier formed of a single pinion and connected to the output shaft of the fixed transmission, and a ring gear connected to the unit output shaft; and A power circulation mode clutch interposed in the transmission path to the continuously variable transmission output portion via the carrier, and a power circulation mode clutch interposed between two elements of a sun gear, a carrier, and a ring gear of the planetary gear mechanism. With a direct connection mode clutch,
A continuously variable transmission having an infinitely variable transmission ratio, comprising: a continuously variable transmission output path for transmitting a driving force from the continuously variable transmission to the sun gear; and a differential connected to the unit output shaft via a transmission means. The constant transmission, the planetary gear mechanism, and the transmission means are each formed of a helical gear. When the power circulation mode clutch is engaged and the direct connection mode clutch is released, the ring gear and the sun gear generate thrust. The helical gear tooth traces are set in a torsional direction in which the forces cancel each other out, and the helical gear tooth traces are set so that the constant transmission on the unit output shaft and the thrust force generated by the transmission means are in different directions. A continuously variable transmission with an infinitely variable transmission ratio characterized by setting.

According to a tenth aspect, in the ninth aspect, a helical gear of transmission means is provided at one end of the unit output shaft, and at the time of forward movement in the power circulation mode,
The rotation direction of the unit output shaft as viewed from the transmission means side is clockwise, and the tooth traces of the helical gear on the unit output shaft as viewed from the transmission means side, the sun gear is right-hand twisted, the ring gear is left-hand twisted, and the constant transmission is The left twist and the transmission means are set to the left twist.

According to an eleventh aspect, in the ninth aspect, a helical gear of transmission means is provided at one end of the unit output shaft, and when the power circulation mode is advanced,
The rotation direction of the unit output shaft as viewed from the transmission means side is clockwise, and the tooth traces of the helical gear on the unit output shaft as viewed from the transmission means side, the sun gear is right-hand twisted, the ring gear is left-hand twisted, and the constant transmission is Right twist, the transmission means is set to right twist.

According to a twelfth aspect, in the ninth aspect, a helical gear of transmission means is provided at one end of the unit output shaft, and at the time of forward movement in the power circulation mode,
The rotation direction of the unit output shaft as viewed from the transmission means side is counterclockwise, and the teeth of the helical gear on the unit output shaft as viewed from the transmission means side, the sun gear is left-hand twisted, the ring gear is right-hand twisted, and a constant transmission. Is set to the right twist, and the transmission means is set to the right twist.

According to a thirteenth aspect, in the ninth aspect, a helical gear of transmission means is provided at one end of the unit output shaft, and at the time of forward movement in the power circulation mode,
The rotation direction of the unit output shaft as viewed from the transmission means side is counterclockwise, and the teeth of the helical gear on the unit output shaft as viewed from the transmission means side, the sun gear is left-hand twisted, the ring gear is right-hand twisted, and a constant transmission. Is set to the left twist, and the transmission means is set to the left twist.

[0028]

According to the first invention, in the power circulation mode of the infinitely variable speed ratio continuously variable transmission, the difference between the speed ratio of the continuously variable transmission and the constant transmission, that is, the rotation of the sun gear and the carrier of the planetary gear mechanism. The unit output shaft is driven in accordance with the difference in the number (number of revolutions), and continuously shifts from forward to reverse including the neutral position, and transmission of torque from the engine is performed from the unit input shaft side in a constant transmission. To the gear of the unit output shaft, in the planetary gear mechanism, from the carrier to the sun gear and the ring gear, and in the transmission means, from the gear of the unit output shaft to the differential.

The unit output shaft is provided with a planetary gear mechanism, an output side gear of a fixed transmission, and a drive side gear of a transmission means. Since each of these gears is constituted by a helical gear, torque is transmitted. Along with the thrust force generated, the thrust force generated by the ring gear and the sun gear of the planetary gear mechanism is set mutually in the torsion direction in which the thrust force is not canceled out, and a constant transmission on the unit output shaft,
Of the thrust force generated by the transmission means and the ring gear,
By setting the tooth traces of the helical gear so that at least one of the helical gears is in a different direction, the direction of the thrust force generated by the helical gears of the constant transmission, the ring gear and the transmission means is not all in the same direction, so that the unit output The total amount of thrust force applied to the shaft can be reduced, and durability can be ensured while reducing the capacity of the bearing that supports the unit output shaft. , And friction due to thrust force can be reduced to improve power transmission efficiency.

Further, in the second invention, when the power circulation mode advances, the rotation direction of the unit output shaft as viewed from the helical gear side of the transmission means is set to be counterclockwise, and the rotation direction of the unit output shaft as viewed from the transmission means side is changed. Thrust of the helical gear teeth, the sun gear is twisted to the right, the ring gear is twisted to the left, the constant transmission is set to the left, the transmission means is set to the left twist, and the helical gears of the constant transmission, the ring gear and the transmission are generated. Since the directions of the forces are not all in the same direction, reducing the total thrust force applied to the unit output shaft reduces the capacity of the bearing that supports the unit output shaft while ensuring durability and infinite speed ratio. It is possible to improve the durability and reduce the size of the continuously variable transmission, and reduce the friction caused by the thrust force to improve the power transmission efficiency.

Further, the third invention sets the helical gear of the constant transmission on the unit output shaft to the right and sets the helical gear of the transmission means to the right. Since the directions of the thrust forces generated by the helical gears are not all in the same direction, the total sum of the thrust forces applied to the unit output shaft can be reduced.

Further, the fourth invention sets the helical gear of the constant transmission on the unit output shaft to the right and sets the helical gear of the transmission means to the left. Since the directions of the thrust forces generated by the helical gears are not all in the same direction, the total sum of the thrust forces applied to the unit output shaft can be reduced.

Further, in the fifth invention, when the power circulation mode advances, the rotation direction of the unit output shaft as viewed from the helical gear side of the transmission means is clockwise, and the boss on the unit output shaft as viewed from the transmission means side. The thrust force generated by the helical gears of the fixed transmission, ring gear, and transmission means, with the tooth traces of the gears set such that the sun gear is twisted left, the ring gear is twisted right, the constant transmission is twisted right, and the transmission is set to right twist. Are not all in the same direction, reducing the total thrust force applied to the unit output shaft reduces the capacity of the bearings that support the unit output shaft, while ensuring durability and ensuring an infinite speed ratio. It is possible to improve the durability and reduce the size of the step transmission, and reduce the friction caused by the thrust force to improve the power transmission efficiency.

According to a sixth aspect of the present invention, the helical gear of the constant transmission on the unit output shaft is set to the left-hand twist, and the helical gear of the transmission means is set to the left-hand twist. Since the directions of the thrust forces generated by the helical gears are not all in the same direction, the total sum of the thrust forces applied to the unit output shaft can be reduced.

In the seventh invention, the helical gear of the constant transmission on the unit output shaft is set to the left-hand twist, and the helical gear of the transmission means is set to the right-hand twist. Since the directions of the thrust forces generated by the helical gears are not all in the same direction, the total sum of the thrust forces applied to the unit output shaft can be reduced.

An eighth aspect of the present invention is directed to the second or fifth aspect.
In the invention, when the ratio of the number of teeth between the sun gear and the ring gear of the planetary gear mechanism is α, the pitch radius of the helical gear on the unit output shaft is R, and the torsion angle is β,

[0037]

(Equation 3)

Where βo: the torsion angle of the transmission means βg: the torsion angle of the constant transmission βr: the torsion angle of the ring gear Ro: the pitch radius of the transmission means Rg: the pitch radius of the constant transmission Rr: the pitch radius of the ring gear Or, by setting it to be substantially established, the thrust force generated on the unit output shaft is reduced to 0 or almost 0, and the friction due to the thrust force is further reduced to improve the power transmission efficiency of the continuously variable transmission with an infinite transmission ratio. At the same time, the bearing capacity can be reduced, and the transmission can be downsized.

According to a ninth aspect of the present invention, a planetary gear mechanism, an output side gear of a fixed transmission, and a drive side gear of a transmission means are arranged on a unit output shaft, and each of these gears is constituted by a helical gear. Therefore, a thrust force is generated along with the transmission of torque, but the thrust force generated by the ring gear and the sun gear of the planetary gear mechanism is set in the helix direction of the torsion in which the thrust force is mutually canceled, and on the unit output shaft. By setting the tooth traces of the helical gear so that the thrust forces generated by the constant transmission and the transmission means are in different directions, the direction of the thrust force generated by each helical gear of the constant transmission and the transmission means is the same. Direction, so the total amount of thrust force applied to the unit output shaft can be reduced, ensuring durability while reducing the capacity of the bearing that supports the unit output shaft. , Strive to promote improvement and miniaturization of the durability of the IVT, it is possible to reduce the friction caused by the thrust force to improve the power transmission efficiency.

According to a tenth aspect of the present invention, a helical gear of transmission means is provided at one end of the unit output shaft, and the rotation direction of the unit output shaft as viewed from the transmission means is clockwise when the power circulation mode is advanced. The teeth of the helical gear on the output shaft of the unit as viewed from the transmission means side are twisted to the right, the ring gear to the left, the transmission to the left, the transmission to the left, the transmission and the transmission Since the directions of the thrust forces generated by the helical gears of the transmission means are different, the total sum of the thrust forces applied to the unit output shaft can be reduced.

According to an eleventh aspect of the present invention, the helical gear of the helical gear on the unit output shaft is set to a right-hand twist for the constant transmission and the right-hand twist for the transmission means. Since the directions of the thrust forces generated are different, they can be set to cancel each other, and the total sum of the thrust forces applied to the unit output shaft can be reduced.

According to a twelfth aspect of the present invention, a helical gear of transmission means is provided at one end of the unit output shaft, and when the power circulation mode is advanced, the rotation direction of the unit output shaft viewed from the transmission means side is counterclockwise. The tooth trace of the helical gear on the unit output shaft viewed from the transmission means side, the sun gear is twisted left, the ring gear is twisted right, the fixed transmission is twisted right, the transmission means is set to right twist, the fixed transmission and Since the directions of the thrust forces generated by the helical gears of the variable transmission means are different, the sum of the thrust forces applied to the unit output shaft can be reduced.

According to a thirteenth aspect of the present invention, the helical gear of the helical gear on the unit output shaft is set to the left-hand twist for the constant transmission and the left-hand twist for the transmission means. Since the directions of the thrust forces generated are different, they can be set to cancel each other, and the total sum of the thrust forces applied to the unit output shaft can be reduced.

[0044]

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

FIGS. 1 to 3 show an example in which the present invention is applied to an infinitely variable speed ratio continuously variable transmission using a toroidal type continuously variable transmission.

1 to 3, a continuously variable transmission having an infinitely variable transmission ratio is provided on a unit input shaft 1a, 1b connected to a crankshaft 13 of an engine with a continuously variable toroidal type continuously variable transmission. The transmission 2 is connected in parallel with a constant transmission 3 (reduction gear) composed of a gear 3a and a constant transmission output gear 3b, and these output shafts 4 and 3c are coaxially arranged on a unit output shaft 6. The output shaft 4 of the continuously variable transmission 2 is connected to a sun gear 5a of the planetary gear mechanism 5, and the output shaft 3c of the constant transmission 3 is connected to a planetary gear via a power circulation mode clutch 9. It is connected to the carrier 5b of the gear mechanism 5.

The continuously variable transmission output shaft 4 connected to the sun gear 5a receives the torque of the continuously variable transmission 2 from the sprocket 4a and the chain 40 (the continuously variable transmission output path), and receives the gear ratio via the direct connection mode clutch 10. The ring gear 5c is also connected to the unit output shaft 6, while being connected to the unit output shaft 6, which is the output shaft of the infinitely variable transmission.

A transmission output gear 7 is provided on the right side of the unit output shaft 6 in the figure, and the transmission output gear 7 (transmission means) is a final gear 12 of a differential gear 8.
The drive shafts 11a and 11b coupled to the differential gear 8 transmit torque at a predetermined total reduction ratio.

The unit output shaft 6 has a direct connection mode clutch 10, a continuously variable transmission output shaft 4, a planetary gear mechanism 5, a power circulation mode clutch 9, a constant transmission output gear 3b of the constant transmission 3, and an output shaft. 3c and the transmission output gear 7
Are arranged coaxially.

As shown in FIG. 1, the continuously variable transmission 2 is a double-cavity half-toroidal type that sandwiches and presses the power rollers 20, 20 with two sets of input disks 21 and output disks 22, respectively. The output sprocket 2a interposed between the pair of output discs 22 is formed on the continuously variable transmission output shaft 4 of the unit output shaft 6 arranged in parallel with the unit input shafts 1a and 1b via the chain 40. Connects to sprocket 4a.

The unit input shafts 1a and 1b are arranged coaxially and connected in the rotational direction via a loading cam device 23. The unit input shaft 1a is connected to the crankshaft 13 of the engine. In addition, a gear 3a of the fixed transmission 3 is provided, and the unit input shaft 1b is connected to two sets of input disks 21 and 21, and the loading cam device 23 is generated according to the input torque from the unit input shaft 1a. The power rollers 20, 20 are pinched and pressed between the input and output disks by the applied axial pressing force.

In the continuously variable transmission with an infinite speed ratio, a direct connection mode in which the power circulation mode clutch 9 is released and a direct connection mode clutch 10 is engaged to transmit torque in accordance with the speed ratio of the continuously variable transmission 2. By disengaging the direct-coupled mode clutch 10 while engaging the power circulation mode clutch 9, the entirety of the continuously variable transmission with an infinite transmission ratio according to the difference in the transmission ratio between the continuously variable transmission 2 and the constant transmission 3. It is possible to selectively use the power circulation mode in which the unit speed ratio (the speed ratio between the unit input shaft 1a and the unit output shaft 6) is controlled almost continuously from a negative value to a positive value including infinity. it can.

The unit input shafts 1a, 1b, the unit output shaft 6, and the drive shafts 11a, 11b are arranged in parallel on the inner periphery of the casing 14, and as shown in FIGS. Output gear 7, Final gear 1
2 and the gear 3a of the constant transmission 3 and the constant transmission output gear 3
b are displaced in the axial direction.

The constant transmission output gear 3b of the constant transmission 3 is formed in an annular shape, and the inner periphery of the constant transmission output gear 3b has an inner diameter through which the unit output shaft 6 and the transmission output gear 7 can be inserted. This constant transmission output gear 3b is fastened to the end face of the flange 3d of the output shaft 3c via a bolt.

As shown in FIG. 2, the unit output shaft 6 has a bearing unit 15 composed of a pair of tapered roller bearings 15a and 15b, an oil retainer 60, and a direct connection mode clutch 1 from the left end 6A in the figure.
0, a sprocket 4a, a planetary gear mechanism 5, a power circulation mode clutch 9, an output shaft 3c of the fixed transmission 3, a fixed transmission output gear 3b, and a transmission output gear 7 are sequentially arranged. 14.

The unit output shaft 6 is rotatably supported by the casing 14 via both ends on the left end 6A side and the right end 6B side shown in FIG. 2, and supports a radial load on the end 6B side. A roller unit 16 is provided on the end 6A side, while a bearing unit 15 including tapered roller bearings 15a and 15b for supporting a radial load and a thrust load is provided.

The tapered roller bearing 15a is
While supporting the thrust load toward the end 6A, the tapered roller bearing 15b supports the thrust load toward the end 6B. Hereinafter, in FIGS.
The sign of the thrust load toward the side is “+”, and the sign of the thrust load toward the end 6B is “−”.

Here, the gear 3 constituting the constant transmission 3
a, the constant transmission output gear 3b, each gear of the planetary gear mechanism 5, the transmission output gear 7, and the final gear 12 are composed of helical gears. In order to support the thrust force generated by these helical gears, The following bearings are provided between the components assembled on the unit output shaft 6.

As shown in FIG. 2, the oil retainer 60 is connected to the inner periphery of the casing 14, and the oil retainer 6
A needle bearing 30 for supporting a thrust load in the + direction is interposed between an end surface on the right side in FIG. 0 and an inner peripheral side surface of the clutch drum 10 a of the direct connection mode clutch 10. The clutch drum 10 a is spline-coupled to the unit output shaft 6 on the inner peripheral side, and rotates relatively to the oil retainer 60.

The hub 10b engaged with the clutch drum 10a is supported by a sprocket 4a coupled to the continuously variable transmission output shaft 4, and the left end face of the continuously variable transmission output shaft 4 in the figure and the clutch drum A needle bearing 31 that supports a thrust load in the + direction is interposed between the inner peripheral surface of the needle 10a and the inner peripheral surface 10a via a collar 100. A sun gear 5a of a planetary gear mechanism 5 is formed on the right side of the continuously variable transmission output shaft 4 in the drawing, and the continuously variable transmission output shaft 4 is connected to a unit output shaft via a bearing provided on the inner periphery. 6 is supported so as to be freely rotatable relative to 6.

Further, a needle bearing 32 for supporting a positive or negative thrust force is provided between the side surface of the sprocket 4 a connected to the continuously variable transmission output shaft 4 and the carrier support member 51 of the planetary gear mechanism 5. Is established.

A needle for supporting a positive or negative thrust force is also provided between the shaft end on the right side of the carrier 5b in the drawing and the ring support wall 50 connecting the ring gear 5c of the planetary gear mechanism 5 and the unit output shaft 6. A bearing 33 is provided.

The carrier support member 51 is connected to the hub 9b of the power circulation mode clutch 9 and supported so as to be rotatable relative to the unit output shaft 6, and connects the ring gear 5c of the planetary gear mechanism 5 to the unit output shaft 6. A needle bearing 34 that supports a positive or negative thrust force is disposed between the ring support wall 50 and the wall 9c extending from the hub 9b toward the inner periphery.

In FIG. 2, the collar 1 is also provided between the right side surface of the wall 9c and the end surface of the constant transmission output shaft 3c.
A needle bearing 35 that supports a positive or negative thrust force via the first and second thrusts 01 is provided.

A flange 3d is formed at the right end of the output shaft 3c of the fixed transmission 3 in the figure, and is connected to the clutch drum 9a of the power circulation mode clutch 9 via the flange 3d. At the same time, a fixed transmission output gear 3b is fastened, and a bearing 17 is interposed between the unit output shaft 6 and the inner periphery of the flange 3d so as to be rotatably supported relative to the unit output shaft 6.

The bearing 17 is composed of, for example, a deep groove ball bearing and is capable of supporting a thrust load, and supports a thrust load applied to the constant transmission output gear 3b and the output shaft 3c.

Accordingly, the negative thrust load generated on the output shaft 3c is transmitted from the bearing 17 to the unit output shaft 6 via the flange 3d, and is supported by the bearing unit 15 provided at the end 6A. When a negative thrust force is generated in 5a, the needle bearing 32, the carrier support member 51, the needle bearing 33, the ring support wall 50, the needle bearing 34, the wall 9c, the needle bearing 35, which contact the side surface of the sprocket 4a, The power is transmitted to the unit output shaft 6 via the collar 101, the output shaft 3c, and the bearing 17, and is supported by the tapered roller bearing 15b of the bearing unit 15.

On the other hand, those generated by the planetary gear mechanism 5 due to the thrust load in the + direction are supported by the casing 14 from the respective needle bearings and the like via the oil retainer 60.

For example, the thrust force in the + direction generated in the ring gear 5c is generated by the needle bearing 33, the carrier support member 51, the needle bearing 32, the sprocket 4a, the continuously variable transmission output shaft 4, and the needle bearing 33 provided at the shaft end of the carrier 5b.
It is supported by the casing 14 via the collar 100, the needle bearing 31, the clutch drum 10a, the needle bearing 30, the collar 102, and the oil retainer 60.

The thrust force in the + direction generated in the sun gear 5a is applied to the continuously variable transmission output shaft 4, the collar 100, the needle bearing 31, the clutch drum 10a, the needle bearing 30, the collar 102, and the oil retainer 60.
And is supported by the casing 14 via.

Similarly, of the thrust force in the + direction, the one generated in the constant transmission output gear 3b or the transmission output gear 7 is directly supported by the tapered roller bearing 15a of the bearing unit 15 via the unit output shaft 6. Is done.

Next, when moving forward in the power circulation mode,
The setting of the rotation direction of each shaft and the twist direction of each helical gear will be described in detail with reference to FIG.

First, in FIG. 3, the unit input shaft 1 when the continuously variable transmission 2 is viewed from the gear 3a side of the constant transmission 3
Assuming that the rotation directions of a and 1b are clockwise, the constant transmission output gear 3b reverses and turns counterclockwise to rotate the carrier 5b.
Orbit. Hereinafter, the rotation direction of each axis is the rotation direction viewed from the right side of FIG.

In the toroidal type continuously variable transmission 2 having the unit input shaft 1b, the input disk 21 and the output disk 2
2, the output sprocket 2a rotates counterclockwise, and the sprocket 4a connected via the chain 40 also rotates counterclockwise to rotate the sun gear 5a.
a also rotates counterclockwise.

Here, assuming that the forward direction of the vehicle is clockwise of the final gear 12, the rotation directions of the unit output shaft 6 and the ring gear 5c are counterclockwise.

When the rotation directions of the respective shafts are set as described above, the torsional directions of the teeth of the constant transmission 3, the planetary gear mechanism 5, and the transmission output gear 7 constituted by the helical gear are determined by the constant transmission output. When the gear 3b is set to the left-hand twist, the sun gear 5a is set to the right-hand twist, the ring gear 5c is set to the left-hand twist, and the transmission output gear 7 is set to the left-hand twist, the gear 3a of the unit input shaft 1a is set.
Is twisted right, and the final gear 12 is also twisted right.

The direction of transmission of torque from the engine is from the gear 3a to the output gear 3b in the constant transmission 3, and from the carrier 5b to the sun gear 5a in the planetary gear mechanism 5.
To the ring gear 5c and from the transmission output gear 7 to the final gear 12.

Therefore, the thrust force generated on the helical gear on the unit output shaft 6 is reduced by the constant transmission output gear 3b.
Assuming that the thrust force of the transmission output gear 7 is Fg and the thrust force of the transmission output gear 7 is Fg, as shown in FIG. In the negative direction toward the middle right, the thrust force Fo is in the positive direction toward the left in the figure.

In the planetary gear mechanism 5 composed of helical gears, assuming that the thrust force of the sun gear 5a is Fs and the thrust force of the ring gear 5c is Fr, as shown in FIGS. 5b connected to
Is transmitted from the pinion to the ring gear 5c and the sun gear 5a. Therefore, when the twist direction of the tooth trace is set as described above, the thrust force Fs of the sun gear 5a
Acts in the + direction on the left side in the figure and is supported on the casing 14 side, while the thrust force Fr of the ring gear 5c acts in the-direction on the right side in the figure and acts on the unit output shaft 6 so that the thrust force Fr does not cancel each other out. Is set.

The thrust force acting on the pinion of the carrier 5b is, as shown by the arrow in FIG.
The thrust force generated on the side and the thrust force generated on the sun gear 5a side cancel each other.

Therefore, the thrust force acting on the unit output shaft 6 is as follows.

[0082]

[Table 1]

In Table 1, the arrows indicating the direction of the thrust force correspond to FIG. 2 or FIG.

Since the thrust force Fs in the + direction generated in the sun gear 5a is supported by the casing 14 as described above, the thrust forces Fg, Fr of the constant transmission output gear 3b, the ring gear 5c and the transmission output gear 7 are generated. , Fo are not set in the same direction, the thrust force applied to the unit output shaft 6 can be reduced.

Therefore, as shown in Table 1 above, the constant transmission output gear 3b, the ring gear 5c, and the transmission output gear 7 have a left-handed twist, while only the sun gear 5a has a right-handed helical gear, so that the thrust force is increased. The directions of Fg, Fr, and Fo are not all in the same direction.
The total sum of the thrust forces (Fr + Fg + Fo) generated in the transmission can be reduced, the size of the bearing unit 15 that supports the thrust load can be suppressed, and the increase in friction can be suppressed. It is possible to improve the power transmission and reduce the size, and also to improve the power transmission efficiency.

Further, the total sum of the thrust forces (Fr + Fg) generated on the unit output shaft 6 even in the engine braking state.
+ Fo), thereby suppressing an increase in the size of the bearing unit 15 supporting the thrust load and suppressing an increase in friction, thereby improving the durability and miniaturizing the continuously variable transmission with an infinite transmission ratio. And the power transmission efficiency can be improved.

Further, the torsion angle of the constant transmission output gear 3b is βg, the gear pitch radius is Rg, the torsion angle of the transmission output gear 7 is βo, the gear pitch radius is Ro, the torsion angle of the ring gear 5c is βr, and the gear pitch radius is Rr,
If the ratio of the number of teeth between the sun gear 5a and the ring gear 5c of the planetary gear mechanism 5 is α (the number of sun gear teeth / the number of ring gear teeth),

[0088]

(Equation 4)

The torsion angle β of each gear is set so as to satisfy the relationship
g, βo, and βr may be obtained. Alternatively, the above (1)
The torsion angles βg, βo, βr of each gear to approximate
May be set.

For example, the helix angle of the constant transmission output gear 3b is set equal to βg and the helix angle of the ring gear 5c is set equal to βr, and the gear pitch radii Rg, Rg are set as follows.
o, Rr, the transmission output gear 7
The case where the torsion angle βo is obtained will be described.

Rg = 85 mm Rr = 55 mm Ro = 30 mm α = 0.5 βg = βr = 21 °

From the above equation (1),

[0093]

(Equation 5)

It is sufficient to set βo = tan ⁻¹ 0.413 ≒ 22.4 °.

In this way, the thrust force generated on the unit output shaft 6 is reduced to zero or almost zero, the friction due to the thrust force is further reduced to improve the power transmission efficiency of the continuously variable transmission with infinite transmission ratio, and the bearing unit 15 Can be further downsized.

In the direct connection mode, the power circulation mode clutch 9 is released, while the direct connection mode clutch 1 is released.
0 is engaged and the torque from the continuously variable transmission 2 is only input to the unit output shaft 6 via the direct connection mode clutch 10 and the constant transmission 3 and the planetary gear mechanism 5 only rotate together. The thrust force applied to the output shaft 6 is
It can be treated as being substantially equal to the thrust force Fo of the transmission output gear 7.

FIG. 4 shows a second embodiment, in which the teeth of the constant transmission output gear 3b and the transmission output gear 7 of the first embodiment are replaced with right-handed twists. This is the same as in the first embodiment.

The rotation directions of the respective shafts are the same as in the first embodiment. The thrust force Fg generated by the constant transmission output gear 3b becomes positive, while the thrust force Fo generated by the transmission output gear 7 decreases. -Direction, and each thrust force is as shown in the following table.

[0099]

[Table 2]

In the above Table 2, the thrust force Fs generated in the sun gear 5a is supported by the casing 14 as described above, so that the directions of the other thrust forces Fg, Fr, Fo are not in the same direction. The constant transmission output gear 3b, the sun gear 5a, and the transmission output gear 7 are right-handed torsion, while only the ring gear 5c is a left-handed helical gear, so that the total thrust force generated on the unit output shaft 6 (Fr + Fg + Fo). Can be reduced, the size of the bearing unit 15 supporting the thrust load can be suppressed, and the increase in friction can be suppressed, thereby improving the durability and miniaturizing the continuously variable transmission with an infinite speed ratio. Thus, the power transmission efficiency can be improved.

In addition, the total sum of the thrust forces (Fr + Fg) generated on the unit output shaft 6 even in the engine braking state.
+ Fo), thereby suppressing an increase in the size of the bearing unit 15 supporting the thrust load and suppressing an increase in friction, thereby improving the durability and miniaturizing the continuously variable transmission with an infinite transmission ratio. And the power transmission efficiency can be improved.

FIG. 5 shows a third embodiment, in which the constant runout output gear 3b of the first embodiment is replaced with right-handed teeth, and other configurations are the same as those of the first embodiment. is there.

The rotation direction of each shaft is the same as that of the first embodiment, and the sun gear 5a is the same as that of the first embodiment except that the thrust force Fg generated by the constant transmission output gear 3b is changed to the + direction. And the thrust force Fo of the transmission output gear 7 is positive, while only the thrust force Fr of the ring gear 5c is in the negative direction, and each thrust force is as shown in the following table.

[0104]

[Table 3]

In Table 3 above, the thrust forces Fs and Fr of the sun gear 5a and the ring gear 5c are not canceled out and the constant transmission output gear 3b and the transmission are shifted so that the directions of the thrust forces Fg, Fr and Fo are not all in the same direction. Machine output gear 7
Of the thrust forces Fg and Fo of the sun gear 5a and the direction of the thrust force Fr of the ring gear 5c are set opposite to the direction of the thrust force Fr of the ring gear 5c, and the total (Fr + Fg + Fo) of the thrust forces generated in the unit output shaft 6 can be reduced. By suppressing the increase in the size of the bearing unit 15 that supports the thrust load and suppressing the increase in the friction, the durability of the continuously variable transmission with infinite transmission ratio and the miniaturization are promoted, and the power transmission efficiency is improved. You can do it.

FIG. 6 shows a fourth embodiment in which the rotation directions of the respective shafts of the first embodiment are reversed and the teeth of the helical gears are reversed. This is the same as in the first embodiment.

In FIG. 6, when the continuously variable transmission 2 is viewed from the gear 3a side of the constant transmission 3, the unit input shafts 1a, 1
b is a counterclockwise rotation direction, and a constant transmission output gear 3
b reverses and turns clockwise to revolve the carrier 5b. Hereinafter, the rotation direction of each axis is the rotation direction viewed from the right side of FIG.

In the toroidal type continuously variable transmission 2 having the unit input shaft 1b, the input disk 21 and the output disk 2
2, the output sprocket 2a rotates clockwise, the sprocket 4a connected via the chain 40 also rotates clockwise, and the sun gear 5a also rotates clockwise.

Here, assuming that the forward direction of the vehicle is counterclockwise of the final gear 12, the rotation directions of the unit output shaft 6 and the ring gear 5c are clockwise.

The torsional directions of the constant speed transmission 3, the planetary gear mechanism 5, and the transmission output gear 7 constituted by the helical gear are such that the constant transmission output gear 3b is twisted rightward and the sun gear 5
When a is set to a left-hand twist, the ring gear 5c is set to a right-hand twist, and the transmission output gear 7 is set to a right-hand twist, the gear 3a of the unit input shaft 1a is left-handed and the final gear 12 is also left-handed.

FIG. 16 of the conventional example and FIG.
As shown in FIG. 7, the thrust force generated on the helical gear on the unit output shaft 6 is negative when the thrust force Fg of the constant transmission output gear 3b is negative, because of the relationship between the torsion direction of the tooth traces and the relationship between driving and following. The following table shows that the thrust force Fs of the sun gear 5a is in the + direction, the thrust force Fr of the ring gear 5c is in the-direction, and the thrust force Fo of the transmission output gear 7 is in the + direction.

[0112]

[Table 4]

Since the + thrust force Fs generated in the sun gear 5a is supported by the casing 14 as described above, the thrust forces Fg, Fr of the constant transmission output gear 3b, the ring gear 5c and the transmission output gear 7 are generated. , Fo are not set in the same direction, the thrust force applied to the unit output shaft 6 can be reduced.

Therefore, as shown in Table 4 above, the constant transmission output gear 3b, ring gear 5c, and transmission output gear 7 are made to be right-hand twisted, while only the sun gear 5a is made to be left-handed helical gear, so that the thrust force is increased. The directions of Fg, Fr, and Fo are not all in the same direction.
The total sum of the thrust forces (Fr + Fg + Fo) generated in the transmission can be reduced, the size of the bearing unit 15 that supports the thrust load can be suppressed, and the increase in friction can be suppressed. The power transmission efficiency can be improved while improving the size and promoting the miniaturization.

In the engine braking state, as in the first embodiment, the total sum of the thrust forces (Fr + Fg + Fo) generated on the unit output shaft 6 can be reduced, and the size of the bearing unit 15 for supporting the thrust load increases. And the increase in friction are suppressed, the durability of the continuously variable transmission with infinite speed ratio is improved, the size of the continuously variable transmission is promoted, and the power transmission efficiency can be improved.

FIG. 7 shows a fifth embodiment, in which the teeth of the constant transmission output gear 3b and the transmission output gear 7 of the fourth embodiment are replaced with left-handed twists. This is the same as the fourth embodiment.

The rotation directions of the respective shafts are the same as in the fourth embodiment. The thrust force Fg generated by the constant transmission output gear 3b is in the positive direction, while the thrust force Fo generated by the transmission output gear 7 is in the positive direction. -Direction, and each thrust force is as shown in the following table.

[0118]

[Table 5]

In Table 5, the positive thrust force Fs generated in the sun gear 5a is supported on the casing 14 side as described above, so that the other thrust forces Fg, Fr, F
The unit output is made by setting the constant transmission output gear 3b, the sun gear 5a, and the transmission output gear 7 to the right-hand twist while setting only the ring gear 5c to the left-hand twist helical gear so that the directions of o are not all in the same direction. The total sum of the thrust forces generated on the shaft 6 can be reduced, the increase in the size of the bearing unit 15 that supports the thrust load and the increase in friction are suppressed, and the durability of the continuously variable transmission with an infinite transmission ratio is improved. In addition to promoting the miniaturization, the power transmission efficiency can be improved.

As in the first embodiment, the total (Fr + Fg + Fo) of the thrust forces generated on the unit output shaft 6 can be reduced even in the engine braking state, and the bearing unit 1 supporting the thrust load can be reduced.
5 and the increase in friction
It is possible to improve the durability and promote the miniaturization of the infinitely variable transmission, and to improve the power transmission efficiency.

FIG. 8 shows a sixth embodiment, in which the constant runout output gear 3b of the fourth embodiment is replaced with a left-handed spiral, and other configurations are the same as those of the fourth embodiment. is there.

The rotation direction of each shaft is the same as that of the fourth embodiment, except that the thrust force Fg generated by the constant transmission output gear 3b is changed to the + direction, and the sun gear 5a is similar to the fourth embodiment. The thrust force Fs of the transmission gear 7 and the thrust force Fo of the transmission output gear 7 are in the positive direction, while the ring gear 5
Only the thrust force Fr of c is in the negative direction, and each thrust force is as shown in the following table.

[0123]

[Table 6]

In the above Table 6, the positive thrust force Fs generated in the sun gear 5a is supported by the casing 14 as described above, so that the other thrust forces Fg, Fr, F
The thrust force Fg of the constant transmission output gear 3b and the transmission output gear 7 so that the directions of o are not all in the same direction,
The direction of the thrust force Fs of the Fo and the sun gear 5a is set opposite to the thrust force Fr of the ring gear 5c, so that the total thrust force generated on the unit output shaft 6 can be reduced, and the bearing unit 1 supporting the thrust load
5, the increase in friction and the increase in friction can be suppressed, the durability of the continuously variable transmission with infinite transmission ratio can be improved, the miniaturization can be promoted, and the power transmission efficiency can be improved.

FIG. 9 shows a seventh embodiment in which the thrust force Fs generated by the sun gear 5a of the planetary gear mechanism 5 and the thrust force Fr generated by the ring gear 5c cancel each other, that is, the case where Fs + Fr = 0 holds. It is shown.

The rotation directions of the respective shafts are the same as in the fourth embodiment.
, The rotation directions of the unit input shafts 1a and 1b are set counterclockwise, and the sun gear 5a rotates clockwise.

If the forward direction of the vehicle is counterclockwise of the final gear 12, the rotation directions of the unit output shaft 6 and the ring gear 5c are clockwise.

The torsional directions of the teeth of the constant transmission 3, the planetary gear mechanism 5, and the transmission output gear 7 constituted by the helical gears are such that the constant transmission output gear 3b is left-hand twisted and the sun gear 5
When a is set to right-hand twist, the ring gear 5c is set to left-hand twist, and the transmission output gear 7 is set to left-hand twist, the gear 3a of the unit input shaft 1a is right-hand twisted, and the final gear 12 is also right-hand twisted.

FIG. 16 of the conventional example and FIG.
As shown in FIG. 7, the thrust force generated on the helical gear on the unit output shaft 6 depends on the relationship between the torsional direction of the tooth traces and the relationship between driving and following. The thrust force Fs of the sun gear 5a is in the minus direction, the thrust force Fr of the ring gear 5c is in the plus direction, the thrust force Fo of the transmission output gear 7 is in the minus direction, and |
Fs | = | Fr | is set as shown in the following table.

[0130]

[Table 7]

Since the thrust force Fs of the sun gear 5a generated inside the planetary gear mechanism 5 and the thrust force Fr of the ring gear 5c cancel each other, the thrust forces of the constant transmission output gear 3b, the ring gear 5c and the transmission output gear 7 are cancelled. Fg, F
If the directions of “o” are set so as not to be the same, the total sum of the thrust forces applied to the unit output shaft 6 can be reduced.

Therefore, in Table 7 above, the constant transmission output gear 3b and the transmission output gear 7 are counterclockwise twisted so that the directions of the thrust forces Fg and Fo do not become the same direction but cancel each other. Direction, the total sum of thrust forces (Fg + Fo) generated on the unit output shaft 6 can be reduced, and the bearing unit 15 that supports the thrust load can be suppressed from increasing in size, and the increase in friction can be suppressed, and the gear ratio can be reduced. It is possible to improve the durability and reduce the size of the infinitely continuously variable transmission, and further improve the power transmission efficiency.

FIG. 10 shows an eighth embodiment.
Constant transmission output gear 3b and transmission output gear 7 of the embodiment
Are replaced with right-handed twists, respectively, and other configurations are the same as those of the seventh embodiment.

The rotation direction of each shaft is the same as that of the seventh embodiment, and the thrust force Fg generated by the constant transmission output gear 3b is negative, while the thrust force Fo generated by the transmission output gear 7 is negative. In the + direction, each thrust force is as shown in the following table.

[0135]

[Table 8]

Since the thrust force Fs of the sun gear 5a generated inside the planetary gear mechanism 5 and the thrust force Fr of the ring gear 5c cancel each other, the constant transmission output gear 3b and the transmission output gear 7 are right-handed. And the thrust force F
g and Fo are not in the same direction but in directions that cancel each other, so that the total (Fg + Fo) of the thrust force generated in the unit output shaft 6 can be reduced, and the bearing unit supports the thrust load. 15, the increase in friction and the increase in friction can be suppressed, the durability of the infinitely variable transmission with infinite transmission ratio and the miniaturization can be promoted, and the power transmission efficiency can be further improved.

FIG. 11 shows a ninth embodiment.
The rotation direction of each shaft of the embodiment is reversed, and the planetary gear mechanism 5
This shows a case where the thrust force Fs generated by the sun gear 5a is offset by the thrust force Fr generated by the ring gear 5c.

The rotation direction of each shaft is the same as that of the first embodiment, and the rotation direction of the unit input shafts 1a and 1b when the continuously variable transmission 2 is viewed from the gear a side of the fixed transmission 3 is clockwise. And the sun gear 5a rotates counterclockwise.

Assuming that the forward direction of the vehicle is clockwise of the final gear 12, the rotation directions of the unit output shaft 6 and the ring gear 5c are counterclockwise.

The torsional direction of the tooth of the constant transmission 3, the planetary gear mechanism 5, and the transmission output gear 7 constituted by the helical gear is such that the constant transmission output gear 3b is twisted rightward and the sun gear 5
When a is set to a left-hand twist, the ring gear 5c is set to a right-hand twist, and the transmission output gear 7 is set to a right-hand twist, the gear 3a of the unit input shaft 1a is left-handed and the final gear 12 is also left-handed.

FIG. 16 of the conventional example and FIG.
As shown in FIG. 7, the thrust force generated on the helical gear on the unit output shaft 6 depends on the relationship between the torsional direction of the tooth traces and the relationship between driving and following. The thrust force Fs of the sun gear 5a is in the minus direction, the thrust force Fr of the ring gear 5c is in the plus direction, the thrust force Fo of the transmission output gear 7 is in the minus direction, and |
Fs | = | Fr | is set as shown in the following table.

[0142]

[Table 9]

Since the thrust force Fs of the sun gear 5a generated inside the planetary gear mechanism 5 and the thrust force Fr of the ring gear 5c cancel each other, the constant transmission output gear 3b and the transmission output gear 7 must be right-hand twisted. And the thrust force F
g and Fo are not in the same direction but in directions that cancel each other, so that the total (Fg + Fo) of the thrust force generated in the unit output shaft 6 can be reduced, and the bearing unit supports the thrust load. 15, the increase in friction and the increase in friction can be suppressed, the durability of the infinitely variable transmission with infinite transmission ratio and the miniaturization can be promoted, and the power transmission efficiency can be further improved.

FIG. 12 shows a tenth embodiment, in which the torsional directions of the teeth of the constant transmission output gear 3b and the transmission output gear 7 shown in the ninth embodiment are left-handed. The configuration is the same as in the ninth embodiment.

In this case, the thrust force generated on the helical gear on the unit output shaft 6 is fixed to the constant transmission output gear 3.
b, the thrust force Fg of the sun gear 5a is in the minus direction, and the thrust force Fr of the ring gear 5c is in the minus direction.
Direction, the thrust force Fo of the transmission output gear 7 is set in the + direction, and | Fs | = | Fr | is set as shown in the following table.

[0146]

[Table 10]

Therefore, the thrust force Fs of the sun gear 5a generated inside the planetary gear mechanism 5 and the ring gear 5c
The thrust forces Fr are canceled out by setting the constant transmission output gear 3b and the transmission output gear 7 to left-handed twist, so that the directions of the thrust forces Fg and Fo are not in the same direction but are mutually offset. Direction, the total sum of thrust forces (Fg + Fo) generated on the unit output shaft 6 can be reduced, and the bearing unit 15 that supports the thrust load can be suppressed from increasing in size, and the increase in friction can be suppressed, and the gear ratio can be reduced. It is possible to improve the durability and reduce the size of the infinitely continuously variable transmission, and further improve the power transmission efficiency.

In the above embodiment, an example was shown in which the position of the power circulation mode clutch 9 was disposed between the counter gear 3b and the carrier 5b. Output shaft 6
13 can be arranged at any position between the transmission gear 7 and the transmission gear 7, for example, as shown in FIG.
c and the unit output shaft 6 or, as shown in FIG.
Or, or as shown in FIG.
It may be interposed in the middle of the continuously variable transmission output shaft 4 connected to the sun gear 5a, and these arrangement positions are equivalent to the above embodiment.

[Brief description of the drawings]

FIG. 1 is a schematic configuration diagram of an infinitely variable speed ratio continuously variable transmission showing one embodiment of the present invention.

FIG. 2 is a sectional view of an essential part of the continuously variable transmission with an infinite speed ratio.

FIG. 3 is a schematic configuration diagram of a continuously variable transmission with an infinite gear ratio showing tooth traces of a helical gear.

FIG. 4 is a schematic configuration diagram of a continuously variable transmission with an infinite gear ratio, showing a second embodiment, showing teeth of a helical gear;

FIG. 5 is a schematic configuration diagram of a continuously variable transmission with an infinite gear ratio, showing a third embodiment of the present invention and showing tooth traces of a helical gear;

FIG. 6 is a schematic configuration diagram of a continuously variable transmission with an infinite gear ratio, showing a fourth embodiment, showing tooth traces of a helical gear;

FIG. 7 is a schematic configuration diagram of a continuously variable transmission with an infinite gear ratio, showing a fifth embodiment, and showing tooth traces of a helical gear.

FIG. 8 is a schematic configuration diagram of a continuously variable transmission with an infinite gear ratio, showing a sixth embodiment, showing tooth traces of a helical gear.

FIG. 9 is a schematic configuration diagram of a continuously variable transmission with an infinite gear ratio, showing a seventh embodiment, and showing tooth traces of a helical gear.

FIG. 10 is a schematic configuration diagram of a continuously variable transmission with an infinite gear ratio, showing an eighth embodiment and showing tooth traces of a helical gear;

FIG. 11 is a schematic configuration diagram of a continuously variable transmission with an infinite gear ratio, showing a ninth embodiment and showing tooth traces of a helical gear;

FIG. 12 shows the tenth embodiment, and is a schematic configuration diagram of an infinitely variable speed ratio continuously variable transmission showing tooth traces of a helical gear.

FIG. 13 is a schematic configuration diagram of a continuously variable transmission with an infinite speed ratio according to another embodiment.

FIG. 14 is a schematic configuration diagram of a continuously variable transmission with an infinite speed ratio according to another embodiment.

FIG. 15 is a schematic configuration diagram of a continuously variable transmission with an infinite speed ratio according to another embodiment.

16A and 16B are explanatory diagrams showing tooth traces of a helical gear and generation of a thrust force in accordance with a driving and driven relationship. FIG. 16A shows a case where a left-handed helical gear is used as a driving side, and FIG. The case where the helical gear is on the drive side is shown.

FIG. 17 is an explanatory diagram showing tooth traces of a planetary gear mechanism constituted by a helical gear, and generation of a thrust force according to a driving and driven relationship.

[Explanation of symbols]

 1a, 1b Unit input shaft 2 Continuously variable transmission 3 Constant transmission 3a Gear 3b Constant transmission output gear 5 Planetary gear mechanism 6 Unit output shaft 7 Transmission output gear 8 Differential gear 9 Power circulation mode clutch 10 Direct connection mode clutch 14 Casing 15 Bearing unit 16 Roller bearing 17 Ball bearing 30-35 Needle bearing 50 Ring support wall 51 Support member

Claims (13)

[Claims] 1. A continuously variable transmission and a constant transmission respectively connected to a unit input shaft, and a unit output shaft arranged in parallel with the unit input shaft and connected to an output shaft of the continuously variable transmission. A planetary gear mechanism comprising a connected sun gear, a carrier formed of a single pinion and connected to an output shaft of a fixed transmission, and a ring gear connected to a unit output shaft; and a continuously variable carrier via the carrier from the unit input shaft. A power circulation mode clutch interposed in the middle of a transmission path leading to a transmission output unit; a direct coupling mode clutch interposed between two elements of a sun gear, a carrier, and a ring gear of the planetary gear mechanism; A variable transmission including an output path for transmitting a driving force from the continuously variable transmission to the sun gear, and a differential device connected to the unit output shaft via transmission means; In the infinitely variable infinitely variable transmission, the constant transmission, the planetary gear mechanism and the transmission means are each formed of a helical gear, and when the power circulation mode clutch is engaged, while in the power circulation mode in which the direct connection mode clutch is released, The thrust force generated by the ring gear and the sun gear is set in the helix direction of the helical gear in a torsion direction in which the thrust forces generated by the ring gear and the sun gear are not mutually cancelled. A continuously variable transmission with an infinitely variable gear ratio, wherein at least one of the helical gear teeth is set so as to be in a different direction. 2. A helical gear of transmission means is provided at one end of the unit output shaft, and at the time of forward movement in the power circulation mode, the rotation direction of the unit output shaft as viewed from the transmission means side is counterclockwise, and 2. The toothed line of the helical gear on the unit output shaft as viewed from the above, wherein the sun gear is set to the right twist, the ring gear is set to the left twist, the constant transmission is set to the left twist, and the transmission means is set to the left twist. The infinitely variable transmission according to the above description. 3. A helical gear of transmission means is provided at one end of the unit output shaft, and at the time of forward movement in the power circulation mode, the rotation direction of the unit output shaft viewed from the transmission means side is counterclockwise, and 2. The tooth trace of the helical gear on the unit output shaft as viewed from above, wherein the sun gear is set to the right twist, the ring gear is set to the left twist, the constant transmission is set to the right twist, and the transmission means is set to the right twist. The infinitely variable transmission according to the above description. 4. A helical gear of transmission means is provided at one end of the unit output shaft, and at the time of forward movement in the power circulation mode, the rotation direction of the unit output shaft viewed from the transmission means side is counterclockwise, and 2. The helical gear of the helical gear on the unit output shaft as viewed from above, wherein the sun gear is set to the right twist, the ring gear is set to the left twist, the fixed transmission is set to the right twist, and the transmission means is set to the left twist. The infinitely variable transmission according to the above description. 5. A helical gear of transmission means is provided at one end of the unit output shaft, and at the time of forward movement of the power circulation mode, the rotation direction of the unit output shaft as viewed from the transmission means side is clockwise, and from the transmission means side. 2. The tooth race of the helical gear on the unit output shaft as viewed, wherein the sun gear is set to the left, the ring gear is set to the right, the constant transmission is set to the right, and the transmission means is set to the right. Speed ratio infinitely variable transmission. 6. A helical gear of transmission means is provided at one end of the unit output shaft, and at the time of forward movement in the power circulation mode, the rotation direction of the unit output shaft viewed from the transmission means side is clockwise, and 2. The toothed streak of the helical gear on the unit output shaft as viewed, wherein the sun gear is set to the left twist, the ring gear is set to the right twist, the fixed transmission is set to the left twist, and the transmission means is set to the left twist. Speed ratio infinitely variable transmission. 7. A helical gear of transmission means is provided at one end of the unit output shaft, and at the time of forward movement in the power circulation mode, the rotation direction of the unit output shaft as viewed from the transmission means side is clockwise, and from the transmission means side. 2. The tooth trace of the helical gear on the unit output shaft as viewed, wherein the sun gear is set to the left-hand twist, the ring gear is set to the right-hand twist, the constant transmission is set to the left-hand twist, and the transmission means is set to the right-hand twist. Speed ratio infinitely variable transmission. 8. When the gear ratio between the sun gear and the ring gear of the planetary gear mechanism is α, the pitch radius of the helical gear on the unit output shaft is R, and the torsion angle is β, Where βo: the torsion angle of the transmission means βg: the torsion angle of the constant transmission βr: the torsion angle of the ring gear Ro: the pitch radius of the transmission means Rg: the pitch radius of the constant transmission Rr: the pitch radius of the ring gear is established or almost established The infinitely variable speed ratio transmission according to claim 2 or 5, wherein the transmission is set so as to perform the following. 9. A continuously variable transmission and a fixed transmission respectively connected to the unit input shaft, and a unit output shaft arranged in parallel with the unit input shaft and connected to an output shaft of the continuously variable transmission. A planetary gear mechanism comprising a connected sun gear, a carrier formed of a single pinion and connected to an output shaft of a fixed transmission, and a ring gear connected to a unit output shaft; and a continuously variable gear from the unit input shaft via the carrier. A power circulation mode clutch interposed in the middle of a transmission path leading to a transmission output unit; a direct coupling mode clutch interposed between two elements of a sun gear, a carrier, and a ring gear of the planetary gear mechanism; A variable transmission including an output path for transmitting a driving force from the continuously variable transmission to the sun gear, and a differential device connected to the unit output shaft via transmission means; In the infinitely variable infinitely variable transmission, the constant transmission, the planetary gear mechanism, and the transmission unit are each configured by a helical gear, and when the power circulation mode clutch is engaged, while in the power circulation mode in which the direct connection mode clutch is released, The helical gear teeth are set in the torsion direction in which the thrust forces generated by the ring gear and the sun gear cancel each other, and the thrust forces generated by the constant transmission and the transmission means on the unit output shaft are in different directions. A continuously variable transmission with an infinite gear ratio, wherein the toothed lines of the helical gears are set respectively. 10. A helical gear of transmission means is provided at one end of the unit output shaft, and at the time of forward movement in the power circulation mode, the rotation direction of the unit output shaft as viewed from the transmission means side is clockwise, and 10. The tooth profile of the helical gear on the unit output shaft as viewed, wherein the sun gear is set to a right-hand twist, the ring gear is set to a left-hand twist, the constant transmission is set to a left-hand twist, and the transmission means is set to a left-hand twist. Speed ratio infinitely variable transmission. 11. A helical gear of transmission means is provided at one end of the unit output shaft, and at the time of forward movement of the power circulation mode, the rotation direction of the unit output shaft viewed from the transmission means side is clockwise, and 10. The tooth of the helical gear on the unit output shaft as viewed, wherein the sun gear is set to the right, the ring gear is set to the left, the transmission is set to the right, and the transmission means is set to the right. Speed ratio infinitely variable transmission. 12. A helical gear of transmission means is provided at one end of the unit output shaft, and at the time of forward movement in the power circulation mode, the rotation direction of the unit output shaft viewed from the transmission means side is counterclockwise, and When the sun gear twists left, the tooth of the helical gear on the unit output shaft seen from
The infinitely variable transmission ratio transmission according to claim 9, wherein the ring gear is set to the right, the fixed transmission is set to the right, and the transmission means is set to the right. 13. A helical gear of a transmission means is provided at one end of the unit output shaft, and at the time of forward movement of the power circulation mode, the rotation direction of the unit output shaft as viewed from the transmission means side is counterclockwise, and When the sun gear twists left, the tooth of the helical gear on the unit output shaft seen from
The infinitely variable transmission ratio transmission according to claim 9, wherein the ring gear is set to right-hand twist, the constant transmission is set to left-hand twist, and the transmission means is set to left-hand twist.